Spring-coiling machine, its mechanisms cuttings, education site, transportation of workpieces (options), their devices seizures, movement, orientation, clip, cam means

 

(57) Abstract:

The device relates to the production of springs. The machine is equipped with a mechanism of formation of the node to the reference coil springs with knotting gears made with the capture device, the spring device with progress springs with device orientation support coil springs, with clamping springs, heat treatment device, mechanism for stacking plates of packaging, as well as mechanisms for moving workpieces springs from the cutting zone in the formation area of the site and area education site in the area of heat treatment of each capture device, and means for opening and closing mechanism of formation of the node, device, heat treatment and cutting mechanism each have their own Cam means, while the Cam means of the mechanisms of forming and cutting rigidly installed on the same working shaft, which is associated with the levers rotation movement mechanisms, the Cam means of the mechanisms of formation of the host and of the heat treatment is rigidly installed on another operating shaft, the operating shaft mounted for synchronous rotation, the Cam cuttings equipped with lifting a work area of its lateral surface, the working surface is cool is I spring workpiece from the cutting zone in the formation area of the node associated with the kinematic chain mechanism cuttings tool to open is associated with the kinematic chain of the closing of the gripper mechanism of formation of the site, the means of closing the opening of the gripper mechanism for moving the spring from the formation zones of the site to the zone of heat treatment kinematically associated with the kinematic chain of the swing. This machine allows you to perform a full cycle of the technological process of manufacture of the spring. 12 s and 12 C.p. f-crystals, 8 ill.

The invention relates to the production of cylindrical, curly, in particular, biconical springs and can be used in the design and manufacture of spring-coiling machines, producing finished products without additional processing.

Known machines for coiling springs, which include the basic mechanisms mounted on one frame and kinematically associated with each other. Thus, in the invention of SU 1570826, B 21 F 35/02, bull. 22, 1990 [1] the machine contains a wire feeder, the mechanism for winding the spring, a cutting mechanism, a mechanism for processing the ends of the springs, the mechanism of removal of the spring from the mandrel, kinematically connected by means of a Cam shaft and having a common drive. In SU 1052304, B 21 F 35/02, bull. 41, 1983 [2] the machine is equipped with a manipulator for p is 2, [3] machine provided with a device for removal of the finished spring. In SU 1234018, B 21 F 35/00, publ. 30.05.86. [4] the machine is equipped with a device for heat treatment of coiled springs. However, these machines, which includes several functionally complete mechanisms, each working on the programme, on its operation of the process of obtaining a fairly complex product, such as a spring, in particular double-cone spring, require tight synchronization of coordinated movements of all mechanisms. Defects in this part of the cause frequent failures of the machine, thereby reduce its performance. High-performance machines require a reconciliation of the beginning of a single operation with the end of the previous and subsequent training operations with the utmost precision, which is not provided by the specified solutions.

For synchronization of the individual nodes use different technical solutions. In SU 776725, B 21 F 35/00, publ. 07.11.80. [5], SU 1268260, B 21 F 35/00, publ. 7.11.86. [6] each mechanism operates from its electric motor, and coordinates the work of the whole machine software device and unit program that can be executed in the form of digital presetting of parameters nalivaeva spring or in the form of, unreliable, expensive, and large power consumption. Other solutions involve synchronization of machinery by means of kinematic connection of their working shafts with one control (input) shaft. So, in SU 1657263, B 21 F 35/02, bull. 21, 1991 [7] kinematically connected by means of shaft feeder wire, the winding mechanism and the means for bending the ends of the spring. Manipulator transfer of the workpiece in [2] is connected by means of levers with the camshaft of the machine. In SU 1194549, B 21 F 35/00, publ. 30.11.85 [8] kinematically connected by means of a drive shaft mechanisms windings segments and reset ready for the spring.

The greatest development as received reliable machines, in which the synchronization is performed by the communication mechanisms with one shaft; for example, in SU 996011, B 21 F 35/00, publ. 15.02.83. [9], Cam shoobridge mechanism and cutting cutter located on the same shaft mounted with the possibility of continuous rotation and kinematically associated with the shafts of the feed rolls wire feeder.

Kinematic relationship of individual arrangements with their workers shafts is effected by means of Cams with shaped side surface. So with the possibility to interact with the bending drive mechanism for winding the spring; in SU 506460, B 21 F 35/00, publ. 15.03.76. [11] the drive of the knife is made in the form attached to the shaft associated with the camshaft of the reduction gear of the Cam.

Synchronize the operation of the individual components of the mechanisms of high-performance machine is not sufficient for reliable, uninterrupted operation of it in General. The necessary synchronization of all the constituent mechanisms of the machine.

The closest analogue of the proposed machine according to the ideology of a kinematic scheme means the same destination that operates from a single motor, and the presence of solutions for the synchronization of component parts is an invention.with. 599896, M. CL.2B 21 F 35/00, published 30.03.78. , bull. 12, the Automatic spring coiling [12], containing the wire feeder, mechanism of formation, the cutting mechanism mounted on the frame, kinematically associated with a single motor via a drive shaft, which serves as a common drive for the transmission of motion for all mechanisms of the machine. The wire feeder is running on the drive shaft, the rotation of which is attached to the pinch rollers. The mechanism of forming includes the winding mechanism and the mechanism saloobrazovanie. The mechanism Navi is rnost which defines the shape and dimensions nalivaeva spring; copier rigidly attached to the tracing shaft. The mechanism saloobrazovanie works through the Cams on the Cam shaft associated with the tracing shaft. Cutting mechanism kinematically connected with the winding mechanism via an additional shaft. Knives, winding stops, stepping stops each work on its operating shaft; working shafts are synchronized via a kinematic connection with a common drive shaft.

The disadvantage of this analogue are insufficient functionality of the machine, because it does not contain many of the mechanisms needed for the final production of the spring as the finished product, such as: handling mechanism ends of the springs, the heat treatment device, pagetutor ready springs, which would be consistent with the work of other constituent mechanisms of the machine, as well as insufficient hard synchronization mechanisms involved, the complexity of the kinematic scheme of the machine, containing a lot of work, clock and gear shafts.

The objective of the invention is the creation of a logically complete machine for the winding of the spring, making the entire manufacturing process from wire feeder to receive the spring as the finished product, and takiko scheme, more reliable and trouble-free operation.

This problem is solved by the design of the spring-coiling machine for the production of springs including wire feeder, mechanism of formation, the cutting mechanism mounted on the frame, kinematically connected with the motor via a drive shaft, Cam means rigidly mounted on the working shaft of the machine, with the cutting mechanism kinematically connected with the shaft of the Cam formation, and the feeder wire drive (Central) shaft side working surface of the Cam formation is made curved, the law of removal of each point from the axis of rotation of the working shaft of the mechanism of formation corresponds to the law of change of the diameter of the spring, which is further provided with a mechanism for the formation of the node to the reference coil springs with knotting gears made with the capture device, the spring device with progress springs with device orientation support coil springs, with clamping springs, heat treatment device, mechanism for stacking plates of packaging, as well as mechanisms for moving workpieces springs from the zone of cutting in the area of education is relevant to their opening and closing, the mechanism of formation of the node to the reference circuit, the heat treatment device and the cutting mechanism each have their own Cam means when the Cam means of the mechanisms of forming and cutting rigidly installed on the same working shaft, which is associated with the levers rotation movement mechanisms, the Cam means of the mechanisms of formation of the host and of the heat treatment is rigidly installed on another working shaft, which is kinematically connected knotting gear mechanism of formation of the node through the mechanism of intermittent rotation, for example a toothed sector plate packaging. Working shafts mounted for synchronous rotation, for example with the same angular speed in the same direction. Cam cuttings equipped with lifting a work area of its lateral surface, the beginning of which corresponds to the beginning of the formation of the spring, i.e. the beginning of his lifting of the plot lies in the contact zone obratnogo roller Cam forming area with the beginning of the forming of the spring Cam formation (up to its middle line); in the case of winding cone spring start lifting the work area of the Cam cuttings matches the end of the transition zone nalivaeva springs with large diameter its rotation, coincides with the lever rotation grip mechanism for moving the workpiece springs from the zone of the cutting zone uzlovataya, i.e., the connection point of the lever rotation and the first link of the kinematic chain (e.g., pull) the mechanism for moving the workpiece from the cutting zone uzlovataya lies on the line connecting the start point of the cutting zone of the Cam cutting with the axis of rotation of the shaft, on one side with the beginning of the cutting zone from the axis of rotation of the shaft, the mechanism for moving the spring blanks from uzlovataya in the area of heat treatment designed to match its extreme upper and lower positions with the extreme lower and upper positions of the mechanism for moving the workpiece from the cutting zone uzlovataya respectively, namely provisions of their seizures, the working surface of the Cam heat treatment is made symmetric and represents an arc of a semicircle, with the line connecting the center of the working surface with the axis of rotation, which axis of symmetry of the Cam track heat treatment, coincides with the line connecting the beginning of the work area of the Cam felling with its axis of rotation is in one direction, i.e. is it an angle in the 0othe Cam mechanism of formation of the node violnet the contact zone tying gear with spring-loaded Cam mechanism of formation of the node coincides with the starting point of the cutting zone of the Cam cuttings subsequent spring, plate batching mechanism kinematically connected with the second working shaft through the lever rotation, and their extreme position in the area of packaging (extreme right position of the plates in Fig.1 shows the relative axis) corresponds to the beginning of uzlovataya, i.e. the beginning of the contact tying gear with a spring, means closing the gripping mechanism to move the spring of the workpiece from the cutting zone uzlovataya associated with the kinematic chain cutting tool to open is associated with the kinematic chain close grip springs in the mechanism of formation of the site, the means of closing the opening of the gripper mechanism for moving the spring from the zone of uzlovataya in the area of heat treatment kinematically connected with its kinematic chain swing grip.

The proposed solution allows you to create a logically complete machine for coiling springs, including all manufacturing operations for its manufacture, does not require the use of other devices and mechanisms outside of the machine, which leads to high performance spring production, high quality, and reduce the cost of their production, can simplify the design of the machine and to achieve a high degree of synchronization of the work of all mechanisms of AV is ukcia machine as a whole is illustrated in Fig.1. Description spring-coiling machine in statics and his work is shown below.

The mechanism cuttings

Known spring-coiling machines, in which the wire feed stops for cutting coiled springs [9]. Such machines have insufficient performance and quite complex, as they involve a special device turn off wire feeder. Periodic on/off mechanism causes transient acceleration and deceleration of pulling rollers, shafts, on which fixed these rollers, which affects the accuracy of wire of the desired length for harvesting and as a consequence leads to defective products; besides, the mode of acceleration/deceleration causes large vibration, noise of operation of the machine, the wear of its parts.

There are also known machines, in which a segment of coiled springs is carried out without stopping the wire feed through "quick cuts", for example, due to the speed of rotation of the shaft the Cam cuttings significantly greater speed of shaft associated with the wire feed [11]. Increasing the speed of the cutting knife can be achieved by message him for more energy, for example, by a spring, the La spring making SU 471941, M. CL. B 21 F 35/00, published 30.05.75. , bull. 20 [13]. This design allows before driving the knife pre-compress the power spring for a message later her energy rolling knife that due to this quickly cuts a wound spring. However, the high speed movement of the knife to the cutting in the described structure creates a strong shock, which may cause violation of the form of springs and unpredictable destruction of the cutting mechanism, its individual elements and/or details of the mating structures that will affect the reliability of the machine and the fragility of his service.

To resolve the problem of reducing the speed of cutting and the associated problems of reducing the distance of the stroke of the rolling knife the location of the knife in the standby mode constantly change synchronously with the winding process. Thus, in [5] stove with knives using a separate motor for winding the spring can synchronously with the winding stops to move, then leaving, then coming back to the starting point of bending of the wire.

The closest analogue mechanism felling is cutting mechanism according to the invention.with. 599896, M. CL.2 B 21 F 35/00, published 30.03.78., bull. 12, the Automatic spring coiling [12], which cinematic the first in the movable plate, and external knife mounted on a movable Polushka. Polushka one end adjustably mounted on the axis and at the other end to the eccentric end of the shaft that is installed in the movable plate. Shaft with an eccentric connected with the clutch, comprising a cutting mechanism at the time segments of coiled springs, and to the drive shaft. On the inner plate knife fixed toothed rack which engages with a pinion which is connected with the gear shaft of the winding mechanism. In the kinematic connection of the winding mechanism with the mechanism of cutting knife are in constant motion, moving away from the springs, then approaching her; the movement of the knives of the cutting device is carried out synchronously with the winding mechanism on the proportional length and is made from the tracing of the drive mechanism of the winding. This mode of operation of the cutting mechanism allows you to track the location nalivaeva springs, reducing to a minimum the length of the stroke of cutting knives, however, requires more complex kinematics of the machine, reduce reliability, and reduce the service life of moving parts, more frequent readjustment of the machine. In addition, the knives in [12] perform the reciprocating movement along the long kinematically, great efforts movable knives at the time of cutting, which slow down the cutting process and can lead to desync operation of the machine. Another drawback is the complexity of the cutting mechanism, its kinematic scheme and as a consequence reducing the reliability of the machine. Another unsolved problem is the closest analogue is the withdrawal of rolling knife from the zone of cutting after cutting without deformation of the end of the subsequent spring.

The objective of this invention is to improve the synchronization mechanism cuttings with other mechanisms of the machine, simplifying the design, improving the reliability of a cutting mechanism and machine as a whole while maintaining the continuity of the wire and the small stroke of the knife when cutting, the removal of the deformation subsequent spring with a knife at his return to the starting position.

The problem is solved by the design of the mechanism cuttings containing the movable knife with the ability to interact with others with a knife during cutting, with the possibility of shifts in the winding and cutting the springs associated with the Cam cutting and kinematically associated with the Cam shifts, in which the movable knife is installed with the possibility of rotation in the plane perpendicular to the coil pruinosa with the Cam movement and the Cam cuttings made by one kinematic chain through obecnie rollers advances and cutting, respectively, located coaxially on one shoulder rocker kinematic chains, each in front of his Cam, Cam cutting is equipped with a lifting straight or curved work area of its lateral surface, the Cam advances provided with a first working lifting area of the side surface, straight or curved, which is located before the start of the working section of the Cam cutting, and the second (last) work lifting section, straight or curved, the beginning of which coincides with the end of the working section of the Cam cuttings and the second work area of the Cam advances made with elevation (tilt) of the same sign as his first work area, and the Cam mechanism cuttings made with the possibility of different times of their interaction with their subcatname rollers.

This design of the cutting mechanism allows to synchronize the operation of the cutting mechanism due to the relative position of both Cams, to eliminate the constant movement of the knife and replace them on the progress of the knife prior to the direct process of cutting, to exclude the reciprocating motion of the knife, inertia and bending loads, to provide a smooth preparatory machining in the plane perpendicular to the coil spring, after selecting all the backlash kinematic chain before felling, reducing working stroke of the knife to the point of felling to a minimum, excluding large shock load on the spring procurement and construction details cutting and reducing bending effort on his spring preparation; execution of the working-side surface of the Cam shifts the gap makes the possibility of multi-temporal contact Cams shifts and cutting with their rollers, i.e., the possibility of multi-temporal operation of the cutting mechanism in different modes: movement of the knife and cutting the spring blanks, switching the knife when cutting with the Cam shifts the Cam cutting is more massive and shockproof, not loading the Cam shifts, thereby ensuring the durability of the mechanism and eliminating malfunctions of the machine. The shape of the Cam shifts allows you to continue the rotary speed of the knife after cutting in the same direction as before felling, quickly bringing the knife from the cutting zone and preventing distortion of the shape of the end of the new nalivaeva in this time of spring. This will reduced the effort of rolling knife when cutting and ensured the performance of the cutting process. All this allows cutting the springs without stopping the feed Provo operation of the machine as a whole.

The design of the cutting mechanism is illustrated in Fig.1, 2B, 4. Describe the construction and operation of the mechanism described below.

The Cam mechanism cuttings

Known Cams cuttings designed to control the operation of the cutting mechanism in machines for winding spring having a core side surface, a pivotal movement of the knife cutting. Thus, in [13] the cutting mechanism includes a movable knife with the possibility of reciprocating motion from the drive Cam having a steeply sloping site, which determines the movement of the blade when cutting. The presence of the spring stroke of the knife restricts the ability of the cutting mechanism.

In [11] described the Cam means of the cutting mechanism, in which the actuator is movable knife spring-coiling machine is equipped with levers, one of which is in constant contact with the Cam profile, equipped with a lifting section and rigidly mounted on the shaft kinematically connected reduction gear with the camshaft. Cam through the said lever passes constant vibrational motion of the slave coupling associated with the knife kinematically, resulting in the team from the other of the Cam through the microswitch closes the I without stopping the wire feed speed of the knife at the time of felling, significantly higher wire feed speed. Reverse knife immediately after logging provides the Cam 42.

Such a device, first, causes a large displacement of the knife when cutting at high speed, which causes a significant shock load on the spring mechanisms of the machine and the deformation of the spring during cutting, secondly, the return springs back immediately after logging also leads to deformation following nalivaeva springs, thirdly, the device comprising in addition to kinematic chains and electric, is complex and unreliable. Installing Cams on different shafts affects synchronization mechanism cuttings. Described Cam means is the closest analogue of the proposed resolution.

The objectives of this invention are the reduction of shock loads from the knife to nalivaeva spring and mechanisms of the machine, improving the quality nauywaima springs, simplification of the mechanism of cutting, increase the degree of synchronization of the cutting process.

Problems are solved by the design of the Cam means of the cutting mechanism, containing a Cam cutting, Cam motions knife fitted with a lifting section and is made possible with the creation of the cutting mechanism is a dual Cam, consisting of rigidly interconnected and installed coaxially of the Cam movement and the Cam cuttings, each of which with its contact element in the form of a roller, Cam cuttings are equipped with a work area lift his side surface, straight or curved, the size (linear dimension of its projection on the arc of a circle with radius equal to the distance of the initial point of the side surface to the axis of Cam rotation) is determined by the diameter of the wire used for winding the spring, and the angle of the hoist is determined by the speed of cutting; the working section of the Cam cuttings can be a continuation of lifting it outside of the site, as shown in Fig.2B, the beginning of the work area of the Cam cuttings in one embodiment, the design may be the value at which the difference of the distances from the points of the side surfaces of the Cam movement and the Cam cuttings lying on one axial straight line to the axis of rotation of the Cams will be less than the radial difference of the sizes (radii) of their obecnych rollers; beginning of the work area of the Cam cuttings can be an arc, the concave side of which faces interacting with him obratnogo roller, and the radius of which is equal to the radius of this obratnogo roller; culutures Cam progress made with four parts; the first section shifts to the felling is located before the start of the working section of the Cam cuttings and is a branch of rise, straight or curved, linear size of the projection of which on the arc of a circle with radius equal to the distance of the initial point of this site to the axis of rotation of the Cam is determined empirically depending on the distance from the location of the knife (the blade) in the standby mode to the point of cutting, and the angle (tilt angle) is defined by the speed that you want to inform the knife to his progress in the areas of cuttings prior to cutting; this rate in turn depends on early shifts (beginning of the first section of the Cam shifts) and the distance of the knife blade from the cutting zone; the second segment is performed with a constant radius, and its beginning is also to the working area of the cutting Cam cuttings, and the end coincides with the beginning of the wheelhouse or other nonleaf point cutting Cam cuttings; the second condition is preferable from the viewpoint of assurance of the beginning of the operation of the Cam cutting, in order to secure the achievement of the Cam surface felling the above values; the third phase of lifting, the end of which coincides with the end of the section cutting the Cam cuttings and is set to upturn is on one axial straight line to the axis of rotation will be greater the difference between the radial sizes (radii) of their obecnych rollers; the length of this section depends on the angle of ascent; the greater the angle of inclination of this section, the shorter; the fourth (last) part of the Cam track progress made lifting, straight or curved, with elevation (tilt) of the same sign as the first work area of the Cam movement. The magnitude of these values is formulated for the case when the radius obratnogo roller Cam felling more radius obratnogo roller Cam motions, and distances from point-side surface of the Cam shifts to the axis of rotation of the Cams is greater distances from the points on the side surface of the Cam cuttings to the axis of rotation of the Cams. At the other (opposite) conditions everything will be different. The length of the fourth, the last of the work area of the Cam movement is defined as the distance from the site of felling to the progress of a knife at its exit from the zone of cutting, and the angle of this area are defined by required rate of release of their knife cutting zone. Working surfaces obecnych rollers located opposite surfaces of their Cams, performed with a common axis of rotation and with different diameters. It is possible to ensure that once the Cams I, with this and will contact one or the other roller, but in this case, possible failures, as the end of each working Cams site should have a sharp decline, and its beginning to the sharp rise, and the normal operation can be affected by inaccuracies of manufacturing. Therefore, it is preferable described the design of a Cam means.

This design of the Cam cutting allows smooth preparatory support rolling knife to the logging site by early (before the cut), it shifts to the place of cutting, thereby to reduce the stroke of the knife to the point of felling to a minimum, excluding large shock load on the spring procurement and construction details cutting and reducing bending effort on his spring preparation; provides the difference of the contact Cams shifts and cutting with their rollers, i.e., the difference in operation of the cutting mechanism in different modes: advances knife and cutting spring workpiece, switching the knife when cutting with the Cam shifts the Cam cutting is more massive and impact resistant, not loading the Cam shifts, eliminating failures of the machine and ensuring the durability of the mechanism. The shape of the Cam shifts cont allows the e assuming the curvature form of the end of the new nalivaeva in this time of spring. This will reduced the effort of rolling knife when cutting and ensured the performance of the cutting process. All this allows cutting the springs without stopping the wire feed at the simplicity and reliability of the cutting mechanism, providing vysokozhirnuyu smooth operation of the machine as a whole. The advanced design allows the initial contact of the working surface of the Cam felling with his obytnym roller is not in point, and along the arc, reducing the contact stresses on the Cam at the beginning of his contact with his video.

In Fig.2B shows the structure of the composite Cam felling.

Description Cam means of the cutting mechanism in statics and his work is shown below.

The capture device supporting coil springs of the mechanism of formation of the node on the reference orbit

The known device orientation, fixing and clamping spring at the time of processing it all, and capture the ends of the spring. So, in A. with. The USSR 1405938, INC4 B 21 F 35/00, publ. 30.08.88., bull. 24 [14] the winding of the spring is carried on a cylindrical mandrel, so the orientation and fixation of the spring in the desired position carries out the mandrel and clamp the last coil of the spring is made using podzemnih the grip.

The closest analogue capture device supporting a coil spring mechanism for the formation of a node on the reference orbit is the device described in and. C. the USSR 996012, M CL 3 B 21 F 35/02, publ. 15.02.83., bull. 6 [15], the Unit of education site on the supporting coil springs. The specified device contains a drive gear with a radial groove and bending strap on the end face of the gear, the inner surface of which is provided with a cone, located coaxially with the gear, with a groove for guiding the reference coil springs, and the conductor bar for fixing the supporting coil springs; on the working surface bending of the strap in place pairing it with an end surface of the gear made the groove is folded around the end of spring. Thus the axis of the cone is perpendicular to the axis of the spring. For education site on the supporting coil spring installed on the conductor in the groove planks, and places the part of the loop. When you push the conductor with a spring on tying gear is capture, orientation and clamp supporting coil springs: spring base coil gets into the groove of the gear and the groove of the cone on the pinion gear; the reference coil spring is located in the cone so that the axis of the cone is tangent to pornoterapia reference coil; when turning the gear its bending strap provides the flanging of the mesh end of the spring beyond its control coil, forming therein a node.

The drawback capture device supporting a coil spring mechanism for the formation of a node on the reference orbit is that the coil spring is caught limited in size by the groove of the cone; the cone holds round only at the apex of the cone and supports it at the base of the cone, so the hold coil is unreliable, and its spatial orientation and the orientation of the end of the spring uncertain; performing cone capture in the pinion housing creates the problem of getting the reference loop in the body of the gears at the push of a conductor to a gear, which leads to a crash of the machine as a whole. In addition, the complex design of the gear and its large dimensions determined by the size of the reference coil, which leads to high power consumption during the rotation of the large gear.

The objective of this invention is to provide a secure grip of the spring with the mutual movement of the spring and cone capture, elimination of malfunctions of the machine by eliminating mistakes when getting spring in conical seizure mechanism for the formation of the site, simplifying the design itself Chester the/P> The problem is solved in the capture device of the spring mechanism for the formation of a node on the reference orbit containing cone capture each core with a coil cone with cone movement capture and springs relative to each other, in which the tapered grips for two reference coils each made in the form of a pair of cones - internal and external, installed one in another coaxially and oppositely, i.e., the larger base of the inner cone lies in the plane of the smaller base of the outer cone, with the base radius of the outer cone of greater radius at the base of the inner cone by an amount equal to the diameter used for the spring wire, with the formation of the socket between the cones facing the spring, i.e., the tapered grips are facing each other with socket ends, with the formation of the annular area between the cones at the base of the conical engagement with a mounting seat for the reference coil spring in the form of a chute square or tapered cross-section side cross-section (height) equal to the diameter of the wire used (taking into account the technological gap), with the diameter of the platform equal to the diameter of the supporting coil rigidly fixed to each other. When this cone grippers for supporting coils set the military mode uzlovataya, at a distance of not less than the axial dimension of the spring, with the possibility of rapprochement. When installing the clamps at an angle to each other they are made to rotate relative to each other to the position in alignment with the spring, when installed parallel to each other facing each other - with the possibility of reciprocating motion.

This embodiment of the tapered grip for the spring makes it easy to catch the spring in cone space (socket) with a wide aperture in the direction of the reference coil springs at their mutual push each other to capture a spring between the two tapered grips with a subsequent decrease in the distance between the grips holding the spring in a tapered grip into the groove of the two reference points round and around its perimeter, securely locking this reference stage in the mechanism of formation of the node. While tying gear, you can run smaller, more simple in construction.

Design capture device of the spring mechanism for the formation of the node illustrated in Fig.6A,b,C. a description of the construction and operation of the device is shown below.

The device shifts the spring mechanism for the formation of the node on the reference orbit

Known in the nl. 30.08.88., bull. 24 [14] slip springs to handle end of the spring is accomplished by movement of the cylindrical mandrel on which the coils of the spring, with the help of Reiki with the gear installed on the shaft splines of the spindle and arbor.

The closest analogue device to move the spring mechanism for the formation of the node on the reference orbit is.with. The USSR 996012, M CL.. 3 B 21 F 35/02, publ. 15.02.83., bull. 6 [15]. The device comprises a drive gear with a radial groove and bending strap on the end face of the gear, the inner surface of which is provided with a cone, located coaxially with the gear, with a groove for guiding the reference coil springs, and the conductor bar for fixing the supporting coil springs; on the working surface bending of the strap in place pairing it with an end surface of the gear made the groove is folded around the end of spring. Thus the axis of the cone is perpendicular to the axis of the spring. For education site on the supporting coil spring installed on the conductor in the groove planks, and places the part of the loop. When you push the conductor with a spring on tying gear is capture, orientation and clamp supporting coil springs: spring anchor round popadae the result orientation and clamp reference coil; when turning the gear its bending strap provides the flanging of the mesh end of the spring beyond its control coil, forming therein a node.

The disadvantage of this device is that it does not provide a progress springs immediately before the clamp to install it in such position that the end of the spring, spinning in the node on the reference orbit, would be strictly defined. Problematic installation of the spring in the conductor to the free end of the support loop for the formation of a node on a supporting turn in the automatic mode. The end of the reference coil springs for a node from the workpiece to the workpiece may have a different length, variable within wide limits. Typically, a machine for coiling springs configured for a certain number of nodes on the base turn, depends on their number, the number of turns of the tying gear, the parameters of the kinematic scheme tying gear; if the length of the end supporting a coil of going to Uzlovaya will vary from spring to spring, as the site is bad. If the length of the end will be too big, then the end when uzlovataya may affect adjacent coils of the spring, which can cause deformation of the spring, the end of the reference coil, it can Orivesi to malfunction of the machine; too short end of the spring is insufficient to winding the required number of rings in the site, the whole site is unreliable and of poor quality.

Object of the invention is the precise definition of the required length of the end of the reference coil that goes to education site on the reference orbit in automatic capture mode of the spring, thereby improving the quality of the springs, the exception malfunction in the operation of the machine as a whole.

This problem is solved by the design of the device to move the spring mechanism for the formation of the node to the reference circuit, comprising a tapered grip the spring with the groove, together with the progress cone capture and springs relative to each other, in which the tapered grip for each reference coil is made in the form of a pair of inner and outer cones installed one another coaxially and oppositely, i.e., the larger base of the inner cone is located in the plane of the smaller base of the outer cone, with the radii of the bases, the difference between which is equal to the diameter used for the spring wire located socket to the spring, with the formation of the seats between the cones at the base of the cone capture under the reference coil springs with a diameter equal to the diameter of anchor withslovakia, at the base of the cone capture (at the base of the inner cone), is oriented in a plane perpendicular to the axis of the spring installed in the mode uzlovataya, geometrical dimensions of the groove (width and length) cone capture is determined from the inequality:

ND + h < l < step spring,

where l is the geometrical dimensions of the groove (width and length), equal to the required length of the end of the reference coil spring, going to Uzlovaya;

N = an integer equal to the number of complete rings in the node; typically N=2 or 3, but may be to others;

D is the circumference of one ring from the end of the reference coil;

D - ring diameter from the end of the reference coil;

h is the distance between the support and the inner coil in the area of location of the site,

the tool advances further provided with a plate rigidly mounted on the tapered grip the wall of the groove opposite the end point of the contact supporting turn in the tapered grip, the working surface is facing the groove

made serving outside the cone of capture and is oriented parallel to the longitudinal axis (length) of the groove or at an acute angle thereto, and orientation of the working surface of the plate at an acute angle preferred. The length of extension of the hours is the more, but for greater reliability of the contact end of the spring the first option is preferable.

The device specified structure with the mutual movement of the spring and grips will allow the spring at the end of the installation the tapered grips, stumbled on the plate with its end, to make an additional rotary motion (in the plane of the drawing counterclockwise), which resulted in the unnecessary part of the end of the reference coil, larger than the transverse size of the groove, will go into the tapered engagement, and in the groove will only strictly fixed length determined by the dimensions of the groove according to the formula specified above. The design of the device illustrated in Fig.6V.

Description of the design of the device in statics and his work is shown below.

The orientation device supporting a coil spring mechanism for the formation of a node on the reference orbit

The known device orientation, fixing and clamping spring at the time of processing it all. So, in A. C. the USSR 1405938, INC4 B 21 F 35/00, publ. 30.08.88. , bull. 24 [14] the winding of the spring is carried on a cylindrical mandrel, so the orientation and fixation of the spring in the desired position carries out the mandrel and clamp the last coil of the spring is made through the gland, role education site on the reference orbit is.with. The USSR 996012, M CL 3 B 21 F 35/02, publ. 15.02.83., bull. 6 [15]. The device comprises a drive gear with a radial groove and bending strap on the end face of the gear, the inner surface of which is provided with a cone, located coaxially with the gear, with a groove for guiding the reference coil springs, and the conductor bar for fixing the supporting coil springs; on the working surface bending of the strap in place pairing it with an end surface of the gear made the groove is folded around the end of spring. Thus the axis of the cone is perpendicular to the axis of the spring. For education site on the supporting coil spring installed on the conductor in the groove planks, and places the part of the loop. When you push the conductor with a spring on tying gear is capture, orientation and clamp supporting coil springs: spring base coil gets into the groove of the gear and the groove of the cone on the pinion gear through the strap and rotating the gear relative to the cone orientation and clamp reference coil; rotating the gear its bending strap provides the flanging of the mesh end of the spring beyond its control coil, forming therein a node.

The disadvantage of this device orientation support coil springs, milling the look on part of its length, in fact, the short arc orbits, determined by the width of the conductor, and two points: the points of contact of the spring with the top of the cone and the base of the cone; large (bottom) part of the loop hanging in the air, which does not provide the required reliability orientation and clamping the reference coil; this in turn leads to the fact that the reference coil can be bent, "walking" its free end in a large unrestricted space; diameter round from spring to spring in the formation of the site and large operating the bending stress varies within wide limits, the reference coil is deformed, that leads to the custom of the final product, i.e. the quality of the finished spring.

The invention is more clear and Narusawa orientation of the reference coil spring under the influence of large deforming stresses in uzlovataya and thereby providing the required diameter of the supporting coil springs, the shape retention of the reference spiral wound springs in the formation of the node on the reference orbit at the time of uzlovataya, due to this increase in the standard springs and their quality.

The problem is solved in the device orientation of the reference coil spring is STU traffic cone capture and springs relative to each other, in which the tapered grip is made with the possibility of installing it in alignment with the spring mode uzlovataya, tapered grip for each reference coil is made in the form of a pair of cones - internal and external, installed one in another coaxially and oppositely, i.e., the larger base of the inner cone lies in the plane of the smaller base of the outer cone and the radius of the smaller base of the outer cone more than the radius of the larger base of the inner cone to the diameter of the wire used for the spring cone are funnel-shaped opening towards each other, i.e. the spring, with the formation of the seats between the cones at the base of the grip under the reference coil spring in the form of a chute square, conic sections with a side sectional size equal to the diameter of the wire used (taking into account the technological gap), with the diameter of the area (the base of the gutter), equal to the diameter of the reference coil rigidly fixed between them, the device is equipped with a restrictive plate with the tabs, the destination site (the ends) are placed in an arc with a radius, not a large difference of the radius of the reference coil spring and the diameter of the wire used for the spring, and a length not less than half the length of the neighborhood what about the plate, thus the outer surface of the inner cone (i.e., the surface facing inwards to the inner surface of the outer cone and the inner surface of the outer cone is made with the sample surfaces opposite the respective inner (end) surfaces of the protrusions of the plate at the closed capture mode of education site (coaxially with the spring installed in the mode uzlovataya). The plate is located at a distance from the base of the cone grip in the closed position, is equal to the diameter of a wire or a few more on the size of the technological gap, which can be up to 0.5 mm

This solution will allow soft "boxed", the orientation of the reference coil spring into the groove between the two cones cone capture, limiting its spatial axis of the spring within the base of the cone capture (gutters)- plate", not letting go the anchor coil of this space; due to this limitation, the reference orbit will remain on its seat when tightening around him end it, its diameter will remain unchanged, will retain its shape and size, despite the large bending of the supporting coil efforts that will allow the reference coil springs VIERA reference coil, equal to the base diameter of the conical grip.

The device orientation support wrapping mechanism for the formation of the node on the reference orbit with the formation of the diameter of the supporting loop is illustrated in Fig.6A,b. Describe the construction and operation of the device is shown below.

The mechanism of formation of the node to the reference coil springs

In many cases, the use of coiled springs should have the ends, not siteplease with each other, not damaging contact with them surface. This is achieved by processing the ends of the springs, for example, by bending, twisting, etc.

Known technical solutions, which provide the fold ends of the coiled springs (see and.with. The USSR 1282948, INC4 B 21 F 35/00, publ. 15.01.87., bull. 2 [16] ); in the above-mentioned machine fold ends is through the mechanism of the fold, consisting of a housing and mounted on the slider. In the guide housing has thebody roller associated with the slider. Before submitting material to the winding mandrel his front end unbent when the movement of the slide in one direction, and after the winding of the spring rear end unbent the same slider in the other direction. For springs often insufficient simply fold the ends, e.g. the Finance site on the supporting coil spring and is.with. The USSR 996012. M CL 3 B 21 F 35/02, publ. 15.02.83., bull. 6 [15], a Device for education site on the supporting coil spring containing the drive gear with a radial groove and bending strap on the end face of the gear, the inner surface of which is provided with a cone, located coaxially with the gear, with a groove for guiding the reference coil springs, and the conductor bar for fixing the supporting coil springs; on the working surface bending of the strap in place pairing it with an end surface of the gear made the groove is folded around the end of spring. Thus the axis of the cone is perpendicular to the axis of the spring. For processing the ends of the springs installed on the conductor in the groove planks, and places the part of the loop. When you push the conductor with a spring on tying gear is capture, orientation and clamp supporting coil springs: spring base coil gets into the groove of the gear and the groove of the cone on the pinion gear through the strap and rotating the gear relative to the cone clamping and orientation of the reference coil; rotating the gear its bending strap provides the flanging of the mesh end of the spring beyond its control coil, forming therein a node. Tying gear contains a clip in the form of a groove and co tangent to the reference coil in the top of the cone, when this takes place the clamp and the orientation of the spring; gear cone combines the functions: capture, clip, retaining and uzlovataya.

Install the spring in the conductor bar in automatic mode the machine is problematic and is more in line with the manual installation.

Hitting conductor with spring on the gear is progressive, while the tapered grip is perpendicular to the spring axis. Capture the reference coil springs, its positioning and clamping are performed on only part of its length; in fact, the detent spring is short arc orbits, determined by the width of the conductor, and two points: the points of contact of the spring with the top of the cone and the base of the cone; large (bottom) part of the loop hanging in the air, which does not provide the required reliability nor capture or clamp and orientation is the lack of a mechanism, especially when having a large bending effort that occurs when you bend the small end of the spring. Unreliable grip and clamp springs lead to uncertainty of the spatial orientation of the spring to shift the spring relative to the gear change of the geometric dimensions of the support wrap in uzlovataya, sat the" spring, additionally confusing as its orientation, thus lowering the clamp. All this affects the quality of the spring. In addition, when "hard blow" is unpredictable wear and tear of the elements of the mechanism, which leads to a limited capacity machine for coiling springs as a whole. Additionally, large size gear determined by the size of the reference orbits, leading to high power consumption during the rotation of tying gear.

The objective of this invention is the provision of mechanism, in particular grip and clip in the automatic mode, improving the reliability of the capture, retention spring when uzlovataya, clamp and rigid orientation relative to the processing nodes all, and thus improving the quality of the springs, reducing shock loads when capturing springs, initial contact with the capture, tying, gear, reducing crashes the machine, increasing the service life of the mechanism and machine in General.

The problem is solved in the mechanism of formation of the node to the reference coil springs, containing for each end of the spring knotting pinion with a radial groove for supporting a coil and bending strap on the end of gear with the possibility of rotational movement of the grip support with a coil groove, with traffic cone capture and gears relative to each other and relative to the spring, in which the tapered grips are made with a conical socket toward each other (toward the spring), with a mounting seat for the reference coil in the base of the grip between the cones with diameter equal to the diameter of the reference coil, the tapered groove grip made in its base opposite tying gear, longitudinal and transverse size which is set to be at least the size of the end of the reference coil springs required for the formation of the node, the height of tying gear with bending bar is less than the transverse dimension (width) of the groove tapered grip, the grips are installed in their original position with their bases at an angle to each other or in parallel opposite each other at a distance less than the axial dimension of the spring, tapered grip for each reference coil is made with the possibility of installing a helical spring mounted on a support mechanism, with the possibility of convergence cone grips with each other with the rotation in case the hooks are angled to each other or progressive in parallel position in the initial state; the tapered grip and knotting each gear svjazanno capture, gear linked with the previous link and the tapered engagement, the gear axes of rotation are parallel to each other, with the possibility of installing axes of rotation in one line, i.e. with the possibility of moving average rotation axis to the line connecting the extreme rotation axis, and one of the links of the kinematic chain shifts capture gear provided with a limiter (focus) movement of the average axis of rotation. Structurally tying gear with the drive spline gear installed in tying the box, attached to the wafer with the possibility of movement relative to the axis of the cone gripping in its closed position, i.e., about the axis of the springs installed for uzlovataya, preferably rotary, and not translational motions, knotting box on the end with a groove located opposite the groove tapered grip and the inner coil spring, of a width larger than the diameter of the wire of the spring by an amount taking into account the rise of a coil spring. The connection tying gear with the Cam formation of the node performed via the fastening plate knotting boxes. The thickness of the boxes must be less than the groove tapered grip.

Presents the design and the o to secure it around the perimeter of the reference coil in position uzlovataya, the ends of the spring, except for the shift, shift spring, regardless attached thereto deforming forces that ensure the quality of the resulting node springs; knee when his "straightening" slows the movement that captures the springs at low speeds capture the spring immediately prior to contact her with tapered grips and knotting the box, and also to securely hold the spring in the mechanism of uzlovataya. While the capture of the spring is carried out without interruption in automatic mode.

The design of the mechanism illustrated in Fig.1, 6A,b. Description of the mechanism of formation of the node to the reference coil springs in statics and his work is shown below.

The device clamp spring mechanism education site on the supporting coil spring.

The known device orientation, fixation of the spring at the time of processing it all. So, in A. C. the USSR 1405938, IPC 4 B 21 F 35/00, publ. 30.08.88., bull. 24 [14] the winding of the spring is carried on a cylindrical mandrel, so the orientation and fixation of the spring in the desired position carries out the locking pin with clip last coil of the spring with the gland of the roller cylinder.

The closest analogue of the fixation device of the spring mechanism for ll 6 [15], the Unit of education site on the supporting coil springs. The specified device contains a drive gear with a radial groove and bending strap on the end face of the gear, the inner surface of which is provided with a cone, located coaxially with the gear, with a groove for guiding the reference coil springs, and the conductor bar fixing (fixing) of the reference coil spring; on the working surface bending of the strap in place pairing it with an end surface of the gear made the groove is folded around the end of spring. Thus the axis of the cone is perpendicular to the axis of the spring. For education site on the supporting coil spring installed on the conductor in the groove of the strap, which is placed and where the fixed (clamped) part of the loop. When you push the conductor with a spring on tying gear is capture, additional orientation and clamp supporting coil springs: spring base coil gets into the groove of the gear and the groove of the cone on the pinion gear through the strap and rotating the gear relative to the cone orientation and clamp reference coil; rotating the gear its bending strap provides the flanging of the mesh end of the spring beyond its control coil, forming therein a node.

is actually fixing the spring is short arc orbits, determined by the width of the conductor, and two points: the points of contact of the spring with the top of the cone and the base of the cone; the main (lower) part of the loop hanging in the air, which does not provide the required reliability orientation, fixation, clamps, especially when having a large bending effort that occurs when you bend the small end of the spring. Unreliable clamp spring leads to changes in the geometrical dimensions of the reference coil when uzlovataya and flawed site from the end of the spring.

The objective of this invention is to improve the reliability of the fixing clamp spring mode uzlovataya.

The problem is solved in a device of the clamping spring of the mechanism of formation of the node to the reference coil springs, containing for each end of the spring cone capture support with a coil groove, with the possibility of movement of the tapered grip on springs, with means for fixing (fuser) spring, in which the tapered grip for supporting coils made with a mounting seat for the reference orbit with the annular space at the base with a diameter equal to the diameter of the supporting coil spring, a groove is made at the end of the reference coil springs at the base of the cone capture perpendicular to the axis of the spring set is opposite and parallel to each other) is not less than the axial dimension of the spring, with the possibility of convergence and install each of them coaxially with the spring means for the fixation (fixation) of a spring is further provided with a liner with pin, protruding above the surface of the liner, one side surface of which, facing the spring, can be performed beveled at an acute angle to the axis of the spring is equal to the angle of the lifting loop, the insert is rigidly fixed to the tapered gripping his groove, the surface of the liner facing the spring installed in the mode uzlovataya, can also be carried out at an acute angle to the axis of the spring, i.e., to the axis of the cone gripping in its closed position, with platforms for part of the previous (internal) coil springs, the angle between the planes of which is equal to the angle of rise of the coil, and a stop fixed on the basis of the mechanism and located in the closed position, the taper of the grip opposite the liner; counter its surface is also provided with a pad portion of the abutment and the inner orbits parallel to the grounds of the liner; the emphasis is equipped with a plug having internal dimensions corresponding to the dimensions of the pin of the liner opposite the pin in the closed position of the grippers. The gap between the opposing areas of the liner and up the wire. The gap between the opposing pads liner and a stop for the inner loop at the position of the closed cone of capture is determined by the size, a bit larger (not smaller) diameter used for the spring wire. This value should be small and allow for some slight movement of the inner loop within 0.3 mm, which is determined empirically and depend on the parameters of the spring and other design features. The area under the reference coil springs on the liner can be made into the lateral surface of the liner side of the groove tapered grip.

This solution allows you to secure and fasten the support coil and lock without holding previous inner coil springs in the mechanism of processing ends, eliminating the distortions of the spring when large bending the forces acting on it in the process of formation of nodes, to improve the quality of the site of the spring and the spring itself. The design of the proposed solution is illustrated in Fig.6A,b,C,d,E. a description of the solutions in statics and his work is shown below.

The Cam mechanism education site on the supporting coil springs

The known device processing the ends of the springs, which are controlled by the Cam. That is semirings, made in the form of pivotally mounted on the frame levers pre flexible fixed on them rollers and slider connected through a thrust with the Cam shaft.

The disadvantage of this funds are insufficient functionality.

The closest analogue is selected Cam tool [1] and.with. 1570826, which has a handling mechanism ends and which is a dual Cam, both of which are fixed on one working shaft, one Cam associated with the punch and bending the finger, and the other interacts with two shoulders lever and two additional fingers. The shape of the first Cam with a lifting section allows you to lift the plunger from bending your finger pressed for clamping and removal of the wire end of its groove, forming the rear end of the spring, a few not duliba it, then take the punch down. The second Cam through interacting with him arm utaplivaet one finger, releasing the other, which pulls the end of the spring with sunken finger, and the latter under the action of forces, deformation and shock about the emphasis and released a second finger digibeta to the desired size.

The disadvantage of collective this, insufficient functionality of Cams, as they do not participate in the management of other nodes on the mechanism of formation of the node on the reference orbit.

The objective of the invention is to provide Cam means of the mechanism of formation of the node to the reference coil springs, allowing successively a number of steps required for processing ends of the two support coils of the spring in the automatic mode and without shock deformation.

The problem is solved by the design of the Cam means of the mechanism that constitutes a Cam mounted on the working shaft and interacting through their contact elements with devices in which the contact elements are in the form obecnych rollers, for example roller bearings, Cam made a composite of three parts: the middle part, power, and two lateral Cams: to control the slip knotting boxes (gear) (Cam tying gear) and to control the slip cone capture (Cam cone capture), lateral lobes each made with a lateral surface, consisting of four zones, one of which is for both Cams - waiting area - is on the Denmark tying boxes (gear), (about 1/4 part of the cycle, but the calculation can be done on another part of the cycle), and its radius is determined by the arrangement of the elements of the mechanism of processing ends (their location relative to the working shaft of the engine ends) in the standby mode. Opposite arc expectations Cam tying boxes (gear) is a zone of contact, representing an arc of a circle of larger radius, the length of which is determined by the time spent tying boxes (gear) in contact with a spring harvest - time contact boxes (tying gear) spring, and its radius is determined by the location of tying boxes (gear) relative to the working shaft in contact mode with a spring. The similar length of the arc of contact of the Cam cone grippers in front of their waiting area is determined by the time cone grippers in contact with the spring (the arc of contact of the conical gripper with spring), and the radius is determined by the location of the cone grippers relative to the working shaft in contact mode directly from the spring, both arc out and contact each of the Cams are located on opposite sides of the axis of rotation of its Cam and connected to each other by two rectilinear wet the AI, connecting the centers of the arcs out and contact, the average power part of the Cam is equipped with stoppers located opposite each of its opposite branches in parallel at a distance equal to the diameter of the corresponding obratnogo roller, at the end of the contact zone of his fist, and made at the ends with arc turned to my return leg, with the ability to interact with his obytnym roller, obecnie rollers are its side surface opposite the side surface of its Cam on the different axes of rotation. The rollers can be made of the same radii. The length of the arc of contact of the conical gripper with spring is greater than the length of the arc of contact knotting gears with a spring.

The implementation of the Cam of this design will allow you to consistently carry out the following operations in strict order: first, to inform the movement of the tapered grips, grab them spring with its ends for supporting the coils, bringing together the tapered grips up to a distance equal to the axial dimension of the spring, and make contact tapered grips with spring, then move the tying gear in tying the boxes, pulled down over his them in the groove of the grip, making contact tying gear walkie-talkie in the automatic mode, then after processing the ends of the spring in the reverse order, without failing to return the constituent elements of the mechanism of formation of the node in the original position. The ability to perform all of these operations extends the functionality of the Cam means in the automatic mode. Specified a strict sequence of operations eliminates undesired operation of the mechanism of formation of the host and the machine in General, improves the reliability of his work.

The design of the Cam means of the mechanism of formation of the node to the reference circuit, presented in figure 1, 2B, 3.

Design description in statics and operation of the Cam means shown below.

The transfer mechanism (and its variants)

Known spring-coiling machines, containing in its composition of different mechanisms for moving workpieces from one processing zone of the workpiece to another (see , for example, the patent of the Russian Federation 2147965, IPC 7 B 21 F 35/00, publ. 27.04.2000. , bull. 12 [18]). The specified mechanism for moving workpieces made in the form of an inclined gravity slid with pneumatic vibrator, conveyor and regulatory tray.

The closest analogue for both variants of the mechanism for moving the spring blanks is a manipulator for transferring the n on A. with. The USSR 1052304, IPC B 21 F 35/02, publ. 7.11.83. bull. 41 [2] , kinematically connected through a system of levers with the camshaft of the machine containing the lever grip consisting of two levers, one ends of which are connected to each other along the axis can be rotated around this axis of one of the levers relative to another, with means for closing and opening of the gripper. Means for opening the gripper of the manipulator consists of a mounted on the frame scenes with Cams, follower and attached to the levers capture pins, interacting with Cams scenes and follower.

The specified transfer mechanism has a limited scope and is not suitable for moving workpieces relatively large dimensions, made of thick wire, with a great weight. The clamping device is not reliable enough, moreover, applied the flow of unacceptable for the proposed design, and difficult to design solutions to achieve a large volume inside the machine, allowing the use of a rack and pinion system move. The time of the clamping spring in a known seizure associated with impact loads on the spring, which changes its form, and also reduces the service life of the parts: ishimi weight characteristics with reliable grip and reducing shock loads on the gripping elements and the spring at the moment of capture.

The problem is solved by the design of the mechanism for moving the spring workpiece, comprising a lever capture of two levers: movable and immovable, which are connected along the axis of rotation of the movement arm relative to the stationary in the plane perpendicular to the course of movement arm, and made with the possibility of contact of the ends of the levers to each other with a gap equal to the diameter of a wire spring of the workpiece, means for moving engagement with lever system kinematic connection with a working shaft of the machine, means for closing and opening the gripper, in which the lever grip is made with the possibility to perform swinging movements between their extreme positions, means for closing and opening the gripper contain cravings, one end fixed to the movable arm along the axis "a", parallel to the axis of rotation of the movement arm, with the possibility of rotation about this axis, the other end connected to the bracket on the middle axis of the strut "b" with the possibility of rotation about this axis parallel to the axis of rotation of the movement arm, a bracket attached to a fixed arm on an axis "b", with the possibility of rotation around this axis parallel to the axis of rotation of the movement arm, the sleeve opening, the imp is the NAP, the sleeve closing, made interoperable opposite directions (as shown by arrows in the figure), with the closing lever in the other extreme position capture (left), mounted on different shoulders of the rocker arm; sleeve opening and closing can be combined in one part or in two parts; designed as two parts of the sleeve may be located on opposite sides of the axis "b" connection cable with bracket horizontally and vertically, depending on the execution type of the sleeves (in the form of one-part or two) and their mutual location of their interaction with the levers for opening and closing will be different or the same direction; thus, the location of the two sleeves diagonally relative to the axis "b" should involve the application of force of opening and closing in the same direction, in other cases the opposite direction; an arm rigidly mounted on the bracket at a point preferably in the immediate vicinity of the axis "b" connection bracket with thrust, while the rod and the bracket with its axis of rotation "a", "b", "b" form a system of knee, made with the possibility of installation of the axes "a", "b", "b", "a", "in" or move this line on the opposite side (with the formation of the deflection of) and back. A means of opening and closing of the gripper is equipped with a restrictor middle axis of the strut (the axis "b" connection cable with bracket) mounted on the fixed lever grip under the middle axis line "a"-"b") at a distance of not more than 3 mm from the centre line a-b, i.e., to limit deflection of up to 3 mm For symmetry shock structurally, the rocker may be made double, between two planes of which is a bracket.

The task is also solved another design of the mechanism for moving the spring workpiece, comprising a lever capture of two levers: movable and immovable, which are connected along the axis of rotation of the movement arm relative to the stationary, and executed with a possibility of contact of the ends of the levers to each other with a gap between them equal to the diameter of a wire spring of the workpiece, means for moving engagement with lever system kinematic connection with a working shaft of the machine, means for closing and opening the gripper, in which the lever grip is made with the possibility to perform swinging movements between their extreme positions, means for th fixed fixed arm capture through a spline connection, means for closing and opening the gripper include traction strut, one end of which is mounted on a movable arm that can be rotated around the axis "a", parallel to the axis of rotation of the movement arm relative to the fixed arm, the other end to the bracket can be rotated relative to the Central axis of the strut "b" parallel to the axis of rotation of the movement arm relative to the fixed arm arm fixed arm can be rotated about an axis, parallel to the axis of rotation of the movement arm relative to the fixed lever, pull the opening-closing set on the bracket can be rotated around an axis, parallel to the axis of rotation of the movement arm relative to the fixed lever, located preferably in the vicinity of the axis "b" of the first connection rod with bracket, with the other end connected with one arm of the rocker axis of rotation perpendicular to the axis of rotation of the movement arm about a fixed axis of rotation of the rocker arm mounted on the lever associated splined connection with the other end of the torsion shaft, a stationary plate fixed on the frame of the machine, equipped with a pair of lugs, RA is deystviya with the second arm of the rocker, and the plate with the other pair of lugs on its sides, while the angular distance between the lugs of different pairs differ by the value of double the angle of twisting of the torsion shaft, the metal plate is a lever of the opening-closing with the possibility of the shock of contact interaction with them, is rigidly connected with the fixed lever grip, mounted on torsion shaft with splined connection. In this case the axis "a", "b", "C" constitute a system of the knee with the possibility of building axes in one line, i.e. with the possibility of moving average axis of the strut "b" to line "a"-"in" or move this line "a","b", with the formation of the cantilever deflection. The lever stops may optionally be equipped with limit switches made with the possibility of their adjustment, fixed to the lever-side stops interoperable lever stops through these stops. Additionally, the fixed lever is equipped with a limit switch axis "b" connection cable with bracket, the limiter is located below the axis away from the midline of not more than 3 mm, the Limiter provides a deflection of not more than 3 mm

The use of strut provides large Executive effort and speed reduction hotkey shock of capture on the spring and the details of the mechanism. The proposed solution extends the scope of the transfer mechanism, which can move the spring workpiece relatively large size and heavy weight, with reliable clamp of simple construction, to exclude the shock load at the moment of capture of the workpiece, thereby to increase the life of the mechanism and to provide high quality undistorted in the process of moving springs. The design of the mechanisms illustrated in Fig.1, 5A,b, 8A,b; a description of the construction and operation of transfer mechanisms is given below.

The capture device of the mechanism for moving the spring

Known capture device springs [15], containing gear, equipped with a cone groove. When getting spring in the groove of the cone by rotating the gear relative to the cone clamp coil springs. During rotation of the gear relative to the cone is also possible rotation, displacement of the spring inside the cone. Due to the location of a coil spring within the large cone of the space of the spring is fixed in space with a sufficient degree of uncertainty.

The closest analogue for the proposed solution is to capture manipulator for transferring the workpiece springs in the Machine for the manufacture of springs in and.slitely shaft of the machine, containing lever grip consisting of two levers, one ends of which are connected to each other along the axis can be rotated around this axis of one of the levers relative to another, which are made with the possibility of contact of the ends of the levers to each other with a gap equal to the wire diameter of the spring, with means for closing and opening of the gripper.

The specified capture when you open it has a large area of uncertainty of the position of the spring-definable presets from the end of the levers to the place of their connection with each other; capture spring billet levers takes place in a random orientation, which causes distortion in her space, harvesting in the fall in the next work cycle treatment area in an arbitrary orientation, may not zahvatchitsa or will not hold the grips in this zone that will lead to marriage and crash the entire machine. Especially important these problems are optionally capture and retention in automatic mode complex-shaped articles, such as cylindrical, conical and other springs.

The objective of this invention is to provide a secure grip coiled spring blanks with neobhodimosti spring billet ultimately smooth operation as capture, and the machine in General, reduction of defective products.

The problem is solved by the design of the capture mechanism for moving the coiled spring workpiece, comprising a lever grip with the possibility of opening and closing, consisting of two levers: movable and immovable, which are made with the possibility of contact of the ends of the levers to each other with a gap equal to the diameter of a wire spring, which free the same ends of the levers at the end of the grip is equipped with limiters spatial position of the spring at the time of its capture, mounted on the fixed arm and the movable arm. Limiters

made with the possibility of interaction between them with a minimum clearance equal to the diameter of the wire used for the spring. The limiter fixed arm is a plate rigidly mounted on the fixed lever, at one end provided with a wedge-shaped guide, and on each side two stoppers located symmetrically relative to the longitudinal axis of the plate along it, made with two beveled surfaces each. The height of the stops defined by the distance between the movable and stationary levers in the open position of engagement, not less. Stops vypolnenoe guide with the formation of the area under the portion of the coil spring shown in Fig.5B by a dotted line. One beveled surface of each extreme position (shown in Fig.5V rare hatching) inclined towards the wedge-shaped guide and relative to the plane of the plate; the plots of these beveled surfaces located at the same height from the plate, are piecewise approximated plots arcs, extending them to connect them with each other is formed plot arc with a radius equal to the radius of a coil spring. Each beveled surface of the other pair of beveled surfaces (Fig. 5B shown shaded) is located at an angle to the plane of the plate 90o. The angle chosen for reasons of greater technology, but may be of other than 90o. The line of intersection of the second beveled surfaces with the plane of the plate are piecewise approximated plots arcs, extending them to connect them with each other is formed plot arc with a radius equal to the radius of a coil spring. The height of the second pair of bevels on size not less than diameter of the wire from which the spring. The limiter rolling lever is a plate pulse is built parallel to the plate of the first stopper in the closed position of the gripper. The plate of the second limiter is equipped with two symmetrically arranged relative to the longitudinal axis of the plate lugs, arranged at an angle to each other at the end of the plate is equal to the angle of the wedge the wedge-shaped guide plate stopper fixed to the lever and at a distance from each other equal to the width of the wedge-shaped guide in the place of their interaction. The lugs are provided with two pairs of beveled surfaces, each of which is parallel to the corresponding beveled surface of the first extreme position (Fig.5g surface, opposite to the respective surfaces of the lugs of the other plate of the fixed lever shown similar shading). The distance between opposing parallel beveled surfaces at the closed capture is equal to the diameter used for the spring wire.

This design capture restricts the position of the springs in space, orients it in a certain position when closing grip and helps to ensure uninterrupted operation of the capture and the machine, eliminating the waste products and the failure of the machine due to the loss of the workpiece during capture and due to wrong orientation mechanisms for subsequent processing of the workpiece in auto the basic mechanism for moving the spring blanks.

The design of the grip shown in any of figures 5A,b, 8A,b, design constraints - Fig.5B,g

Description of the design capture and his work is shown below.

Description of work in statics

In Fig.1 shows a kinematic diagram of the machine; Fig.2A,b,in the form of Cams and their location, and the location of the levers rotation movement mechanisms in the working shafts of the machine; Fig.3A,b - design of Cam mechanism of formation of the node on the reference orbit at various angles; Fig.4 - cutting mechanism spring blanks; Fig.5A,b - device capture mechanism for moving the spring of the workpiece from the cutting zone uzlovataya in the open and closed position; Fig.5 b,g,d, e, f - structure constraints capture device separately from different angles (5B,d) and Assembly (5D) of Fig.6A - mechanism of formation of the node on the reference circuit of two identical component parts for right and left ends of the springs; Fig. 6b is an integral part of this mechanism to the right end of the spring in a different perspective, in Fig. 6V - design conical seizure mechanism for the formation of the node of Fig.6g is a cross - section tapered grip in the closed position; Fig.6D, e - design Korobochka at different angles; in Fig.7 - picture of spring with machined ends; Fig. 8A, b - capture mechanism for moving the spring blanks from uzlovataya in the area of heat treatment in the open and closed positions.

Spring-coiling machine includes a wire feeder 1, the mechanism of formation of the spring 2, the cutting mechanism 3 spring piece, the moving mechanism 4 spring workpiece from the cutting zone in the area of education site on the supporting coil springs (area uzlovataya), the mechanism of formation of the node on the supporting stage 5, the moving mechanism 6 spring harvesting area uzlovataya in the area of heat treatment, the heat treatment device 7, pagetutor 8, is placed in the frame 9 of the machine (on his bed) where you installed the motor 10, is fixed in its lower part.

The engine 10 is kinematically connected with the Central control shaft 11, which by means of gears connected with the two working cyclic walking shafts, the first 12 and second 13 and V-belt passing over the pulleys 14, 15 V-belt variator with a wire feeder 1. All the mechanisms of the machine, in addition to the wire feeder 1, get moving and work from the two business cycle shafts 12 and 13, rotating alternova shaft 11.

The wire feeder 1 includes two pairs of clamp 16 and pulling rollers 17; the latter, through its gear 18 connected to the shaft 19 of the broaching gear. The speed of rotation of the pulleys 14, 15, at least one of which consists of two disks, forming a V-shaped stream, installed with the possibility of their mutual adjustment relative to each other, can be adjusted by changing the spacing between the disks in order to obtain the necessary length of the wire piece for spring. The wire feeder is equipped with nozzles that are located after the rollers.

Mechanisms of morphogenesis 2, 3 cuttings, formation of node 5, the heat treatment device 7 associated with their software devices made in the form of Cams 20-25 profile with lateral surfaces through obecnie rollers 26-31, made for example in the form of rolling bearings (see Fig.1.2 a, 2B,2C).

On the first working shaft 12 coaxially with it installed and fixed Cams forming 20, shifts 21, 22 felling, on the second working shaft 13 coaxial Cams 23,24 mechanism for the formation of the node, the Cam 25 heat treatment.

The side working surface of the Cam formation 20 is made kivalina is of 2 corresponds to the law of change of diameter nalivaeva spring. If necessary, winding cone spring side working surface of the Cam formation 20 is made symmetrical, with an area of smooth removal of points lying on the surface, from the center of rotation of the shaft 12, the zone of maximum removal (with a certain size of the spring it may not be the area and point), a smooth approximation to the center of rotation of the shaft 12, and the beginning of the zone of removal coincides with the end zone approximation, and the axis of symmetry a-a* Cam formation 20 passes through the center of the zone of maximum removal And*, the center of rotation of the working shaft 12 about* and the beginning of zone delete/end zone approximation (Fig.2A). The side surface of the Cam 20 may be made and other forms for formation of a cylindrical, one-cone and other springs. The Cam formation 20 is associated with obytnym roller 26.

The Cam means of the cutting mechanism 3 is a dual Cam comprising a Cam shifts 21 and Cam 22 felling (Fig.2B). Cams made with the possibility of multi-temporal contact their working surfaces with their rollers 27,28. This can be achieved by the design of the Cams and rollers described below.

Working surfaces obecnych rollers 27, 28 ASS="ptx2">

The Cam 22 is equipped with cutting work area lift his side surface m*m**, straight or curved, located in relation to the fist 20 forming in the place corresponding to the beginning of the formation of the spring, i.e. the beginning of his lifting of the plot lies in the contact zone obratnogo roller 26 of the Cam forming area with the beginning of the forming of the spring Cam 20 forming (up to its middle line, the zone of maximum removal for biconical springs). The optimal location of the beginning of the working area cutting - beginning of formation, in the case of double conical springs at the beginning of his zone delete AA* corresponding second round nalivaeva springs at the steady state of the dynamic mode of the winding process, although not ruled out other options, determined by the layout of the machine. The size of the area of the lifting Cam 22 (linear size of its projection on the arc of a circle with radius beginning of the plot with the center of*) depends on the diameter of the wire used for winding the spring. Beginning of the work area of the Cam felling is the value at which the difference of the distances from the points of the side surfaces of the Cam movement and the Cam cuttings lying on one axial straight line to the axis of rotation kavadlo, if the radius obratnogo roller 28 of the Cam cuttings 22 more radius obratnogo roller 27 of the Cam shifts 21, and the side surface of the Cam shifts 21 is farther from the axis of rotation of the Cams in comparison with the axial distances of the points of the side surface of the Cam cuttings 22, as shown in Fig.2B. In other cases, the ratio of the radial (axial) dimensions of the rollers and the side surfaces of the Cams will be different, the opposite. Beginning of the work area of the Cam cuttings 22 can be provided with an arc mm*, the concave side of which faces interacting with him obratnogo roller 28 and the radius of which is equal to the radius of this obratnogo roller. This allows the initial contact of the working surface of the Cam cuttings 22 with its obytnym roller 28 is not in point, and along the arc, reducing the contact load on the Cam 22 and the wear and tear.

The side surface of the Cam shifts 21 has a working area nn****when the movement of the working shaft is reportedly rolling knife, and outside the zone n****n (obkatkoj roller 27 interacts with the Cam 21 without passing motion). Destination outside the zone to keep the knife in his waiting area to the working mode. Outside area n****n can be any shape with a gradual reduction of its happy and fulfilled with four sections; the first section advances nn* before felling is located before the beginning of the work area m*m** Cam cuttings. This is ahead of the curve associated with the need to progress the knife to the cutting zone outside his location in the zone of cutting. The first section nn* is a branch of rise, straight or curved, linear size of the projection of which on the arc of a circle with radius beginning of the plot with the center of* determined empirically depending on the distance from the location of the knife in the standby mode to the point of cutting, and the angle (tilt angle) is defined by the speed that you want to inform the knife to his progress in the area of logging to logging; this rate in turn depends on early shifts (beginning of the first section of the Cam shifts) and the distance of the knife (the blade) from the zone of cutting. The second section is made with a constant radius, and the beginning of the n* is also to the working area of the cutting Cam cuttings, and the end coincides with the beginning of the wheelhouse or other nonleaf point cutting m*m** Cam cuttings; for greater assurance that at the point of felling work Cam cutting and will not be the single point of failure, it is necessary to preserve the continuity of the radius of the side surface of the Cam shifts with increasing distance of the side surface is t, therefore, the second option is preferable, but working both options, and the choice may be determined by the accuracy of the dimensions of the Cams. The third section of the Cam shifts hoist, end coincides with the end of the segment cutting Cam cuttings and is set to rise, in which the difference of the distances from the points of the side surfaces of the Cam movement and the Cam cuttings lying on one axial straight line to the axis of rotation n**** and m*** there will be more difference between the radial sizes (radii) of their obecnych rollers. This should cause the switching roller 28 on the roller 27. This area is required to ensure a smooth switching of the working surface of the Cam 22 on the working surface of the Cam 21. Worded condition should be met with the same above reservations. The length of the third section depends on the angle of ascent; the greater the angle of inclination of this section, the faster the Cam shifts reaches the above value, so it is shorter. Fourth and last section of the Cam track progress made lifting, straight or curved, with elevation (tilt) of the same sign as the first work area of the Cam movement. The length of the fourth area defined rasoaniaina area defined by required rate of release of the knife from the cutting zone. As you can see, the mutual location of work sites Cams 21, 22, their design (size, dimensions) and the shape of these Cams and sizes interacting with them obecnych rollers 27, 28 predetermine time delay between the operation of these Cams and suggest several options for their execution. In Fig.2B larger in diameter roller is a roller Cam 28 felling 22, but may be another option. In the case illustrated in this Fig.2B, when (n**o*m*o*)<(R28-R27) contact will be made between the roller 28 with the Cam cuttings 22, when (n****-m**)>(R28-R27) will contact roller 27 with the Cam motions 21. Thus, the instantaneous ratio of the radii obecnych rollers and the axial distances of the points working the side surfaces of the Cam shifts and cuttings determine the instantaneous operating point of one or another of the Cam.

The Cam mechanism of formation of site 5 (Fig.2B, 3) rigidly mounted on the working shaft 13 and is made of a composite of three parts: the middle part, the power and the side Cams: 23 to control the slip knotting bolls mechanism 5 of the education site and 24 to control the slip cone gripper mechanism 5. These Cams 23, 24 each have a side surface that is divided into four zones. One area DL is waiting taper grips and knotting boxes; the length of the arc expectations defined by the timeout taper grips and knotting boxes (about 1/4 part of the cycle of operation of the machine). The lengths of these arcs of different Cams need not be equal. The radius of each arc expectations defined by the arrangement of the elements of node taper grips and knotting boxes (their location relative to the working shaft (13) in the standby mode. In particular, the radius of the arc expectations tying boxes Lo1 will be determined by the location of tying boxes in the standby mode. Opposite arc waiting Lo1 Cam 23 is the area L1 - arc of contact, representing an arc of a circle, the length of which is determined by the time spent tying boxes in contact with the spring-loaded workpiece - contact time approximately equal time uzlovataya (for reliability a little more time uzlovataya), and in one embodiment, the design may be approximately one third of the circumference and the radius is determined by the location of the knotting of the boxes relative to the shaft 13 in the mode uzlovataya directly from springs. The difference between the radii of the arc expectations and the arc of contact is determined by the lengths of shifts tying boxes from waiting area in m stay cone grippers in contact with the spring (the arc of contact of the conical gripper with spring); as can be seen from Fig.3, L1 < L2. Radius L2 determined by the location of the taper grips. Both arc Lo, LK of each of the Cams are located on opposite sides of the axis of rotation of the Cam shaft 13 and are connected to each other by two rectilinear branches on each side. These branches determine the slip knotting boxes (Cam 23 and tapered grips (Cam 24) mechanism 5 education site from the standby position of the contact spring (straight line) and back (backward branch). The Cams 23, 24 can be made symmetric, and the axis of symmetry of each of the Cam passes through the centers of the arcs expectations and arcs of contact. Average power part of the Cam provided with lugs 32. Stops the power section are intended to bring in forced contact obecnych rollers 29 and 30 with opposite branches Cams 23,24. Stops are located opposite each of its opposite branches in parallel at a distance equal to the diameter of the corresponding obratnogo roller 29, 30, at the end of the contact zone of his fist, and made at the ends with arc turned to my branch with the opportunity to interact with their obytnym roller. The forced contact of the rollers 29, 30 with opposite branches of the Cams 23, 24 can be osushestvlyaem with the same geometric dimensions, mounted on the same shoulders double rocker, have a different axis of rotation and located its side surface opposite the side surface of its Cam 23 and 24, respectively. The location of the composite Cam mechanism 5 on the axis of rotation of the shaft 13 depends on the location of the Cam cuttings 22 and from the location obecnych rollers 29, 30 with respect to the axis of rotation of the shaft 13. The time of cutting the spring time coincides with the end of uzlovataya the previous spring. Meanwhile, the composite Cam mechanism 5 is located on the axis of the working shaft 13 so that the cutting zone m*m** Cam cuttings 22 coincides with the beginning of the transition mechanism for the formation of the node of the mode of contact tying boxes to the standby mode, i.e. with the beginning of the exhaust tying boxes, the end of the arc of contact tying boxes L1.

Cam heat treatment 25 (Fig.2B) is made symmetrical; lateral surface of which consists of two arcs of a semicircle with smaller and larger diameters with transition areas in the form of smooth steps, performed by the arc, and the axis of symmetry of the Cam heat treatment coincides with the beginning of felling, namely the line connecting the midpoint of the working surface of the Cam tarmoola the cuttings with the axis of rotation. The dimensions of the Cam 25 is determined by the arrangement of the elements of the heat treatment. The Cam 25 is supplied obytnym roller 31.

The mechanism of morphogenesis

The Cam 20 forming kinematically connected through obkatkoj roller 26, such as a rolling bearing, with the mechanism of formation of the spring 2, comprising forming roller 33 and Agazade emphasis 34; kinematic relationship of the roller 26 and running a forming roller 33 carried out consistently through the rocker 35, rod 36, the rocker 37, rod 38, the lever 39.

The cutting mechanism generally depicted in Fig.4.

In addition to the above Cams progress 21 and 22 felling with their subcatname rollers 27, 28 of the cutting mechanism includes a movable knife 40 and rigidly mounted on the frame 9 fixed blade 41. For more accurate adjustment of the knives can be made with the possibility of adjusting their position (not shown). Kinematic relationship of the Cam 21 through obkatkoj roller (bearing) 27 with a movable knife 40 is accomplished through the rocker 42, rod 43 on the axis 44 of rotation of the rolling knife 40; cutting plane (the plane of rotation of the knife blade) is perpendicular to the coil. Cam cuttings 22 is arranged to communicate with its obytnym roller 28, mounted coaxially with the role of the knife 40. This allows to increase the degree of synchronization process advances knife and cutting process and to simplify the kinematic scheme of the machine as a whole. The movable knife 40 is also connected with the return spring from the endpoint of the movement of the knife to its original position (not shown).

Mechanism 4 to move the spring of the workpiece from the cutting zone uzlovataya includes a capture device with means for closing and opening (Fig.5) and means for moving the gripper (Fig.1). Means for moving mechanism 4 is connected with the working shaft 12 draft 45 (Fig.1, 2A) fixed to the Cam cuttings 22 via a shackle 46 (see Fig.2A), forming a lever rotation; a mounting for this earring on the Cam 22 is located on the line connecting the starting point of its working surface m*with the axis of rotation of the working shaft 12 with eccentricity, which is determined by the layout of the machine, and made with the possibility of angular adjustment within narrow limits; rod 45 is oriented along the line of connection of the working surface of the Cam 22 with the axis of the shaft 12 and is located on one side with the specified line from the axis of rotation. This allows for tight synchronization of the processes of cutting and moving the workpiece. Rod 45 passes motion relative to the axis of rotation 51. Capture 50 in Fig.1 shows a conventionally. The grip 50 is fixed on the rotation axis 51 and can take two extreme positions: in the area of felling spring harvest (extreme bottom position) and in the area of uzlovataya end of the spring (extreme top position). The grip 50 has two States: open (Fig.5A) and closed (5B), which holds the workpiece wound springs for its transfer. The grip 50 includes a movable lever 52, the stationary arm 53, which are connected along the axis of rotation of the movement arm relative to the stationary in the plane perpendicular to this axis, rod 54, one end fixed to the movable arm 52 along the axis "a", parallel to the axis of rotation of the movement arm 52, with the possibility of rotation relative to it, the bracket 55, associated with the other end of the thrust 54 along the axis b, parallel to the axis of rotation of the movement arm 52, with the possibility of rotation relative to it, and fixed the lever 53 can be rotated around the axis "b", parallel to the axis of rotation of the movement arm 52, the sleeve closing 56, sleeve opening 57, mounted on different shoulders of the rocker arm 58. Structurally, the rocker arm 58 may be made double, between two planes which are rigidly linked, mounted on the bracket 55; place connect the Yaga 54, as near the axis "b" contact voltage at the connection details from the impact will be minimal. If you do not follow these considerations, the connection of the bracket 55 and the rocker arm 58 may be further from the axis "b". The axis of rotation of the bracket 55 "b" parallel to the axis of rotation of the movement arm 52 and the fixed lever 53. Rod 54, the bracket 55 with their axes of rotation "a", "b", "b" form a system of the knee, which made the capture kinematics; brace provides large Executive efforts and reducing the speed at the end of the movement the Executive details of the capture: bracket 55, rod 54, the movable arm 52. Rod 54, the bracket 55, the arm 58, the sleeve 56 and closing the opening 57 constitute the means for opening and closing the gripper 50. For reliable jamming gripper axis "b" should fall below the line "a","b", forming a deflection. To reduce the deflection of the system of the knee to a value of not more than 3 mm in the system of the knee on the fixed lever 53 has a limiter 59 stroke axis "b" bracket 55 under the bracket 55. In the absence of the limiter 59 when further lowering the midpoint of the knee below 3 mm (technological dimension), the movable arm 52, turning on around the axis of Sidency levers 52, 53 at the end of the grip 50 is equipped with a limiter position of the spring at the time of its capture: 60 fixed on the lever 53 and 61 on the movable arm 52. These limiters 60 and 61 shown in Fig. 5V. and 5g, respectively, in its various angles, and at the time of their contact with each other and with squeezed between the coil spring harvest (Fig. 5D). Limiters made with the possibility of interaction between them with a minimum clearance equal to the diameter of the wire used for the spring. The limiter 60 (Fig.5B) is a plate 62 rigidly mounted on the fixed lever 53, at one end provided with a wedge-shaped guide 63, and the sides - two stops (actually limiters) 64, arranged symmetrically relative to the longitudinal axis of the plate 62 along it, made with two beveled surfaces each. The height of the lugs 64 are defined by the distance (not less than) between the movable 52 and 53 fixed levers in the open position of the gripper 50 (Fig. 5A). The lugs 64 are made on the end plate 62 along it, with some shift from its front edge, namely near the base of the wedge-shaped guide 63, with the formation of the area under the portion of the coil spring shown in Fig. 5B,g dashed line. One skolen tivemos springs) and are tilted with respect to the Central plane of the plate 62 (Fig.5B shows a rare hatching); plots of these beveled surfaces of the lugs 64, located at the same height from the plate 62, are piecewise approximated plots arcs, extending them to connect them with each other is formed plot arc with a radius equal to the radius of a coil spring. Each beveled surface of the other pair of beveled surfaces is at an angle equal to 90oto the plane of the plate 62 (for reasons of manufacturability) (Fig.5B,g shaded). The line of intersection of the second beveled surfaces with the plane of the plate 62 are piecewise approximated plots arcs, extending them to connect them with each other is formed plot arc with a radius equal to the radius of a coil spring. The height of the second pair of bevels on the value selected is not less than the diameter of the wire from which the spring of the reasons exceptions slipping coil springs. Both the stop 64 with their beveled surfaces are designed to limit movement round caught the spring with one hand (in the plane of the figure to the right). The limiter 61 (Fig. 5g) is also a plate 65 of a width not larger than the distance between the lugs 64 rigidly mounted on a movable arm 52, located parallelogram relative to the longitudinal axis of the plate 65 supports 66 opposite the lugs 64. Stops 66 are arranged at an angle to each other equal to the angle of the wedge the wedge-shaped guide 63, and at a distance from each other equal to the width of the wedge-shaped guide 63 in place of their interaction. Stops 66 are provided with two pairs of beveled surfaces, each of which is parallel to the respective opposite the beveled surface of the stop 64 (Fig.5B,g counter surfaces are made with the same shading).

The distance between opposing parallel beveled surfaces at the closed gripper 50 is equal to the diameter used for the spring wire.

The transfer mechanism 4 is also equipped with kinematic chain closing of the gripper 50, which is associated with the kinematic scheme of the mechanism of cutting 3 through the arm 42, the rod 67 mounted on the shoulder of the rocker arm 42 of the cutting mechanism 3, the other end of which is connected with the lever 68, a circuit closing gripper also includes a lever 69, associated with the lever 68 through a torsion shaft 70, and with a thrust 71 and the lever 72 close grip 50 with the possibility of its interaction with the sleeve closing 56 capture 50 at its lower position. Additionally, the transfer mechanism 4 is arranged to interact with his sleeve opening 57 with lever 73 Denmark) 5 (Fig. 1, 6A) works from the second cycle of the working shaft 13 through a compound Cam 23, 24 and obecnie rollers 29, 30 and contains two mechanisms for handling the right (Fig. 6b) and left ends of the springs are identical. The mechanism of formation of the node and in the right and the left side contains a pair of cones capture - the inner 74 and outer 75 installed one another coaxially, and a counter (Fig.6A,b,C), i.e., the larger base of the inner cone 74 lies in the plane of the smaller base of the outer cone 75, and the base radius of the outer cone of greater radius at the base of the inner cone by an amount equal to the diameter used for the spring wire (adjusted for technological gaps), located with the formation of the annular pad 76 between them at the base of the conical engagement with a mounting seat for the reference coil spring in the form of a chute square or tapered cross-section (Fig.6g) with a side dimension equal to the diameter of the wire used (taking into account the technological gap), with the diameter of the platform equal to the diameter of the supporting coil rigidly fixed to each other; cone capture 74-75 made with a groove in the base of the grip. The groove is designed to position the end of the reference coil spring and is focused perpendicula and length) is determined from the inequality:

N D + h <l <step spring,

where l is the geometrical dimensions of the groove (width, length) equal to the length of the end of the reference coil spring, going to Uzlovaya;

N = an integer, the number of complete rings in the node; typically N=2, 3, but there may be others;

D is the circumference of one ring from the end of the reference coil;

D - ring diameter from the end of the reference coil;

h is the distance between the support and the inner coil in the area of location of the node (see Fig.7).

Capture 74-75 further provided with a plate 77 (Fig.6b), rigidly mounted on the tapered grip 74-75 at the far wall of the groove opposite the end point of the contact supporting turn in the tapered grip, the working surface is facing the groove made serving outside the cone of capture (of the groove) is about the size of the radius of the reference coil for reliability its contact with the end of the spring with a possible change in the orientation of the spring within certain limits and is oriented parallel to the longitudinal axis of the groove or at an acute angle thereto, and orientation of the working surface of the plate at an acute angle preferred.

Directly from groove placed firmly fixed in the grip liner 78 (Fig. 6b, 6D). Powermenu at an acute angle to the axis of the cone clamps in their closed position (to the spring axis, installed for uzlovataya); this surface is provided with a pad part of the previous (internal) coil springs (Fig.6D shows a rare hatching), the angle between the planes of which is equal to the angle of the lifting loop. For reliable orientation is folded around the end of the reference coil inside the groove to the center of the base of the grip 74-75 when it polome Playground at the end of the reference coil on the side surface of the liner may be made out to the side, the inner side of the groove surface of the liner 78. The liner is provided with a pin 79, the side surface of which is frequent shading) can also be made with a slope at an acute angle relative to the spring axis, i.e. parallel to the plane tangent passing through the sample and the inner coils of the spring.

Front liner 78 in the closed position taper grips at the base (frame 9) is the stop 80 (Fig.6E). The side surface of the stop 80 is made available under part of the loop and part of the inner loop; these sites, counter pads liner 78, shows the same hatching; the stop 80 is also equipped with a plug on its end opposite the pin in the closed position of the grippers, with internal dimensions corresponding to the taper grips. The gap between the opposing side surfaces of the pads liner 78 and the stop 80 under the control coil of the spring in the closed position cone capture 74-75 determined by the diameter used for the spring wire. The gap between the opposing side surfaces of the pads liner 78 and the stop 80 under an inner coil spring in position closed cone capture 74-75 defined somewhat larger than the diameter used for the spring wire, eliminating the rigid clamping of the inner coil spring, leaving little freedom to move.

Each part of the mechanism 5 also includes knotting box 81 (Fig. I) to contain and secure knotting pinion 82, provided with a bending bar 83, and spline gear 84, which is in constant mutual engagement (not shown). The transverse size of tying boxes (its thickness) is not greater than the width of the groove is tapered grip 74-75. Knotting box 81 is made with the possibility of a reciprocating or rotary motion to the spring, and from spring, i.e. about the axis of the cone location of the clamps in their closed position (spring axis set mode uzlovataya). The box is equipped with a groove located with STS into account the inclined position of the internal coil spring to the spring axis, equal to the angle of the lifting spring (Fig.6b knotting box 81 is shown placed in the groove taper grips 74-75).

Directly near cone capture 74-75 is plate-limiter 85, the plane of which is parallel to the plane of the base of the cone grip when it is in closed position (i.e., sandwiched in him a spring installed in the mode uzlovataya). A limiter is provided with protrusions, the inner plane of its ends, forming a bounding surface for supporting a coil spring cone in the capture, in the form of plots of an arc with a radius not greater than the difference between the radius of the reference coil springs and radius used for the spring wire, with the possibility of travel limit of the reference coil spring into the groove with the annular space 76 cone capture 74-75 in the axial direction of the spring; the tabs of the plates 85 are located along the length of the arc is not less than half the length of a circle with the specified radius. The plate with the tabs secured to the base 86 of the mechanism 5 education site on the supporting coil spring, i.e., is stationary relative to the frame 9, so that when closed, the capture plate is located opposite its base parallel to it at distance gap, 6g). On the outer surface of the inner cone 74 and inner surface of the outer

cone made samples for free navigenie tapered grip on the tabs of the plate 85 (Fig.6b).

The tapered grip 74-75 fixed console on a support 87 of the base 86. Console with the supports 88 87 made with the possibility of rotation around the axis perpendicular to the axis of the spring when it is their reference coils between the cones 74, 75. Tapered grips 74-75 both parts of the mechanism 5 are arranged in the formation area of the node in the initial position at an angle to each other; the maximum angle of opening" tapered grips in the initial position determines the distance between them is not less than the axial dimension of the spring. Tapered grips are made with the possibility of their mutual rapprochement with each other. The location of the grips at an angle to each other implies their convergence turn to set them opposite each other coaxially at a distance equal to or slightly smaller axial dimension of the spring. Possible installation cone grabs both parts of the mechanism coaxially opposite each other in parallel. In this case, the convergence of the grippers will be progressive.

Tying boxes 81 fixed each day capture 74-75 and knotting box 81, each associated with a composite Cam mechanism 5 through the kinematic chain their movement to spring, and from spring, two final link which side cone capture 74-75, and tying boxes 81 are connected between themselves and with conical seizure 74-75, plate 89 mounting tying boxes 81 axis of rotation "a", "b", "b", parallel to each other, with the possibility of installing them in one line (Fig. 6b), i.e. with the possibility of moving axis "b" to line "a"-"in". Tying gear 82 is also linked kinematic chain with a toothed sector fixed to the gear installed on the shaft of the second operating shaft 13.

Work handling mechanism ends 5 controls the composite Cam 23-24, mounted on the shaft 13 and is associated with the kinematic scheme of the mechanism 5 through obecnie rollers 29, 30. The kinematic scheme of the mechanism 5 includes a pair of actuators tapered grips, drives tying boxes, drives tying gear.

Each drive conical grips 74-75 works from the Cam 24 and its obratnogo roller 30 and includes a rocker arm 91 (located on the back behind the arm 99 in Fig.1); one shoulder of the rocker arm is connected with the lateral surface of the Cam 24 through the bearing 30, the second thrust 92 and forth with threapleton lever 93 with one axis of rotation (shoulder 93A - shoulder b), thrust 94, Korb associated with craving 98 along the axis of rotation "b", parallel to the axis, the other end of the traction bar 98 is connected with the console 88 cone capture 74-75 axis "a" parallel to axis "b". While the details 97B-98, namely the axis of rotation "a"-"b"-"b" form a system of knee tapered grips with the possibility of building in one line.

Each drive knotting boxes 81, as the drive conical grips 74-75, operating on the second operating shaft 13 and a compound of the Cam, only from the other side part 23, as follows: the Cam 23, obkatkoj roller 29, the Cam 99, the rod 92, techplace lever 93 (shoulder 93A); this part of the kinematic chain coincides with the kinematic chain drives conical grips 74-75. The rocker arm 91 and 99 have the same design and a common axis of rotation in their middle part. Unlike schemes conical grips in treplace the lever 93 to transfer motion knotting boxes involved other shoulder 93 century, the shoulder through the rod 100 is connected with a yoke 101 (Fig. 6A,b) and then through the rod 102 and the plate 89 mounting tying boxes with knotting box 81. The components 101, 102, namely the axis of rotation a-b-in the form of another system of knee tying boxes with the possibility of building an axis of rotation "a", "b", "C" in one line (Fig. 6b).

Two shoulders lever 97 left side of the mechanism 5 education site provided dopolnitelnim shoulder V (Fig.6A), which, together with the thrust 103 and the lever 73 constitute the means for opening the gripper 50 of the transfer mechanism 4.

The tying drive gear 82 is fed from the second operating shaft 13, which is fixed to the gear 104 mounted inside the sector gear. Gear with a toothed sector selected for transmission of intermittent rotation tying gear during one revolution of the shaft as the most reliable system; as another system intermittent rotation can be used, and other well-known systems, such as the Maltese mechanism. Gear sector occupies approximately 1/3 of the circumference and spatial does not always coincide with the arc of contact tying boxes with spring L1 Cam 23; in this work the gear sector on time coincides with the work of the arc of contact of the Cam tying gear, which is achieved by adjusting the angular position of the gear sector and the Cam mechanism for the formation of the site on their desktop shaft 13, as well as adjustable shoulder separate the barrels 81 with spring Cam 23 or less; so, for reliable operation of the machine without crashing the angular size of the arc L1 120o, and the angular size of the gear sector 106,6o. The angular size of the gear sector selected smaller angular size of the arc of contact tying boxes in order to secure the stay of the latter in contact with the spring, while Uzlovaya tying gear 82 associated with gear sector, the presence of technological errors of execution of parts of the machine. With a high degree of accuracy of their production ideally, these dimensions will be equal, and the angular size of the gear sector can also be 120o. These sizes are determined based on the used variants of transmission links in the kinematic scheme of tying drive gears, the number of required turns tying gear and may vary within certain limits. Toothed sector gear 104 is located with the possibility of periodic engagement with the driven gear 105. Driven gear is made with parameters that allow you to rotate it from the gear sector one turn. Driven gear 105 is connected with the gear 106 with a gear ratio equal to two, and one tying gear 106 paernu change the direction of rotation 107, as shown in Fig.1) because of the direction of rotation tying gear 82 to the different ends of the springs must be different. Further increasing gear 106 is connected with a bevel gear 108 cardan mechanisms 109 directly related to spline gear 84. Type of gears and mechanisms are defined on the basis of layout solutions machine. For education site in three rings (N=3) with the specified ratio of the kinematic chain gear sector - tying gear it is necessary to increase the transmission spline gear 1.5 times.

Mechanism 6 to move the spring from the zone of uzlovataya the heat treatment includes the transport device and the capture device with means for closing the clamp opening. The transport device is associated with the working shaft 12 through the lever rotation 110 (Fig.1, 2A), mounted on a shaft 12, on the axis of rotation directly or eccentricity, the value of which, as well as the location of the arm relative to the other Cams, is determined by the layout of the machine; place of fastening of the lever of rotation is located with adjustable about the axis of rotation of the shaft 12, and more precisely determined experimentally in the configuration process. The lower and virgninia and the upper position of the capture mechanism 4 to move the spring from the zone of the cutting zone uzlovataya respectively. This is achieved by linking kinematic chains, adjustable shoulder of the individual links of the kinematic chain and the angular adjustment of the location of the levers of rotation on the working shaft.

Lever rotation mechanism 110 6 is associated with the capture device through the transport device: rod 111, the lever 112, the torsion shaft 113, which is fixed to the grip 114 (Fig.1 is shown conventionally in Fig.8A,b - its design in the open and closed position by measuring the swinging movement of the capture device 114, mounted on torsion shaft 113, relative to the rotation axis 115. Peak-to-peak swing of the grip 114 to the shaft 113 is determined by the position of the stops 116,117 (Fig.1, 8), interacts with the lever 118 through adjustable travel stops 119. The grip 114 has two positions: open (Fig. 8A) and closed (Fig.8b), while holding the workpiece wound springs for its transfer. The grip 114 contains a movable arm 120, a fixed arm 121, rod 122 and the bracket 123.

Movable arm 120 of the gripper attached to a fixed arm 121 on the rack axis can be rotated around this axis, perpendicular to the plane of movement of the moving lever 120. Rod 122 with one end fixed to the movable arm 120 can be rotated around the axis "a", parallel is a possibility of rotation about the axis "b", parallel to the axis of rotation of the movement arm 120 relative to the fixed arm 121. The other axis of rotation of the bracket 123 "in", parallel to the axis of rotation of the movement arm 120 relative to the fixed arm 121, mounted on the stationary rack lever 121. Fixed arm 121 is fixed splined connection to the torsion shaft 113 by means of the clamping plates 124.

The grip 114 also includes means for opening and closing the gripper, comprising a rod 125, the Cam 126 associated with the lever 127 along the axis of rotation, which is rigidly attached to the torsion shaft 113 by using the spline and the plate 128 rigidly mounted on the frame 9 of the machine. Plate 128 is equipped with stops 130, 131 and plate 132 stops 116, 117 on its sides (Fig.1, 8b). The stops 130, 131 are located on opposite sides of the second arm of the rocker arm 126 in front of him with the possibility of shock interaction with a second arm of the rocker arm 126. Fixed arm 121 is rigidly connected with the lever 118, mounted on torsion shaft 113 and located between the lugs 116, 117 of the plate 132, using the spline.

Rod 122, the bracket 123 with their rotary axes "a", "b", "b" form a system of the knee with the possibility of building them on the same line is ogiba) similarly, the capture mechanism 4; the lock provides greater enforcement efforts and reduce the speed of the rolling arm 120 relative to the stationary 121 at the end of its movement during the closing of the grip 114. Additionally, the fixed lever 121 is equipped with a limiter 133 bottom of the stroke axis "b" connection of thrust with bracket 122 123 located on the fixed lever under this axis and defining the parameters of boom deflection. Quantitatively axis "b" can go below. the middle line a-b in no more than 3 mm In the presence of deflection of the capture jams and securely holds the spring in spite of vibration of the machine during its operation; for wedging grip you need to make a big enough shock on his "pulling". In larger deflection (for this design lever grip, this is more than three millimeters) movable arm 120, to rotate around the axis "a", will begin to open, and clamp grip 114 is unreliable. The same ends of the levers 121, 120 at the end of the grip 114 is equipped with limiters 134,135, similar to the stops 60, 61 of the transfer mechanism 4, interoperable with a minimum gap between them equal to the diameter of the wire.

The heat treatment device 7 comprises a pair electra with a current source (not shown), need the value of which and the heat treatment time is determined using engineering calculations. The current source may be a transformer, the secondary circuit of which is in the form of a closed loop forms a very workpiece or welding machine. The on-off current source by using the limit switch 138, which interacts with the Cam 25 through heat treatment arm 139, obkatkoj roller 31.

Pagetutor 8 consists of a tank 140 to collect the finished springs and a pair of actuating plates 141, spaced from each other at a distance equal to the axial dimension of the spring or less to output the finished spring from the zone of thermal treatment in the container 140 pagetutor. The Executive of the plate 141, the ends are made with scalloped cutouts under the coil springs are connected through the lever 142, the rod 143, the shoulder rotation 144 with the second working shaft 13. The location of shoulder rotation 144 on the shaft axis 13 defined by the layout of pagetutor 8 machine, with kinematics performed with the software matches the beginning of the zone uzlovataya (the beginning of the engagement gear sector gear 104 with its driven gear 105) extreme position patterny plates 143 in pagetutor (Fig.1 right Polozheniye motor 10, the rotation of its rotor through a belt drive is transmitted to the Central control shaft 11 (Fig.1). Being engaged through gears cyclic walking with two working shafts, the first 12 and second 13, the shaft 11 causes them to rotate in one direction and with the same speed. Through V-belt passing over the pulleys 14, 15 V-belt variator shaft 11 causes the rotation of the shaft 19 broaching gear and through him, and gear 18 pinch rollers 17, which rotates by means of two pairs of pressure rollers 16 start feeding the wire on the mechanism of morphogenesis 2.

When this first working shaft 12 begins to rotate mounted thereon Cams: forming 20 (Fig.2A), advances 21 (Fig.2B) rolling knife 40, the Cam cuttings 22 (Fig.2B), as well as rod 45 of the transfer mechanism 4, is rigidly fixed on the Cam 22, and the lever rotation 110 of the transfer mechanism 6 mounted on the shaft 12. Begins the process advances molding roller 33, repeating the motion obratnogo roller 26 that communicates with a lateral surface of the Cam formation 20, and the formation of the spring coils, the diameter of which will vary according to the law, the predefined shape of the side surface of the Cam formation 20. If the side surface of the Cam 20 has three zones: zone deleting points of the side Cam surface of the iron surface And*A, spring cone coils with supporting turns from both ends, with a maximum radius with a gradual decrease to the center of the spring, with a minimum radius in the middle part of the spring and with a gradual increase of the radius to its maximum value in the reference circuit, the other end of the spring. The movement from the Cam 20 to the molding roller 33 is passed through the circuit: obkatkoj roller 26, the rocker 35, rod 36, the Cam 37, the rod 38, the lever 39, a forming roller 33. Agazade stop 34, resting in the newly wound coil, determines the distance between the coils of the spring (step). View the links of the kinematic chain, quantity, place attachment is defined layout solutions machine. At the completion of the formation process of the first spring begins non-stop formation (wrapped) second spring.

At the beginning of the forming of the second spring, due to the location of the working surface of the Cam shifts 21 to the area of the minimum diameter of the spring begins the preparation process of rolling knife 40 for harvesting. This process is controlled by the Cam advances 21 (Fig.2B) and is as follows. The Cam shifts 21 rotates together with the Cam 20, the second coil of the second nalivaeva spring nachinaetsya point-side surface of the Cam 22 to the axis about*, as can be seen from Fig.2B, the difference of the radii obecnych rollers 27, 28, the roller 28 does not apply its Cam 22 and the roller 28 or the Cam 22 in the cutting movement of the knife 40 at this time is not involved. The Cam 21, the pushing roller 27 in the direction of the axis o, actuates a rocker arm 42, which rotate around its axis, the other his shoulder pushing rod 43, turning the knife 40 around its rotation axis 44 toward the stationary knife 41. The beginning of this process depends on the relative position of Cams forming 20 and advances 21, the place of their contact with the rollers relative to the axis of the shaft 12, which in turn takes into account the location of the movable knife 40 relative to the zone of formation (forming roller 33), the selected speed of movement of the knife 40, the shape of the Cam track progress 21 (the angle of its working area) using engineering calculations and empirically. Reaching a place of cutting, the knife 40 is stopped, since the point n* begins the second section of the side Cam surface 21 of constant radius, and movements of the knife 40 is not happening. During this time, the distance from the side surface of the Cam cuttings 22 to the axis of rotation about* increases the value, when the difference of the axial distances tocheck begins to touch the Cam cuttings 22 mm arc* at the beginning of the work area of the Cam cutting m*. The same roller 27 "hangs" in the air. Early slip of the knife 40 is caused by the need to accelerate the process of cutting coiled springs by reducing its progress at the moment of cutting. The brevity same process of cutting caused by the condition of continuous wire feed and continuity of the process of formation of springs, which is directly related to the productivity of the machine and increase reliability. From this point m* movement of the rocker arm 42 defines a Cam 22. At this time, in the place of felling plot is wrapped around the first spring, at the end of the last reference coil of the first spring and the first reference coil of the second spring. At the same time, due to the coincidence of the provisions of the early m* plot cuttings Cam cuttings 22, the roller 28 and a thrust mechanism 45 4 move the grip 50 of the transfer mechanism in an open condition reaches its extreme lower position, entering the wedge-shaped guide 63 his limiter in the "body" of the spring, with one of the coils of the spring will be in the space between the lugs 64 and 66 (Fig.5A,b,d). The space between the lugs 64, 66 is constrained to move in the spring; the height of the stop 64 to the level of rolling recov 64, 66 (rare shading surfaces Fig. 5B, d). Due to the presence of these beveled surfaces of the lugs 64, 66, lying parallel to the coil spring, and further restrict its spatial location, eliminating its bias relative to the grip 50. Initial felling begins with the interaction of the roller 28 with the initial plot cuttings Cam cuttings 22 (point m* Fig.2B). From this interaction again comes to the movement of the rocker 42, passing the time of movement of the lever 68 through the rod 67, which through a torsion shaft 70 will transmit this movement to another lever 69 through 71 on the deadlift lever 72. Under the effect of the moment arm 72 rotates his shoulder, which movement will hit the sleeve 56 closing of the gripper 50. From this blow, the arm 58 of the grip 50 (Fig. 5A), and receiving the movement will put pressure on the bracket 55 at the point of connection near its axis of rotation "b" is the mid-point of the knee, dropping point "b" to the level of the zero line "a-b"; the specified movement will be smooth, because the further down the point "b" to its zero point, the slower will be the increment of movement when the same force that characterizes the work of the strut. Point "b" will fall to the level line "a-b", slowly lowering the movable rasua of the deflection, but not more than 3 mm for the given design lever grip, below 3 mm from the average level it will not allow to fall limiter 59 fixed on the lever 53, as can begin opening capture by further turning movement of the moving lever 52 relative to the stationary 53. The spring is oriented oblique opposing surfaces of the stops 64, 66, while between them, under the action of Adigeni her bevelled surfaces (rare hatching in Fig.5B,d), parallel to one of the coils of the spring, will descend to the ground plate 62 in the wedge-shaped guide 63 (shown by the dotted line in Fig.5B); further, under the same action of the beveled surfaces of the stop 66, the spring will go into the space bounded on one side by the plate 62, on the other hand, the second pair of beveled surfaces (blacked out) stops 66, forming plots approximated arcs on the sides of the stop 66, the third side of the second pair of beveled surfaces (blacked out) stops 64, forming plots approximated arcs on the sides of the stop 64. This point will coincide with the lowering movement arm 52 on the stationary arm 53, the jamming of the knee, and the cutting is already clamped in the grip 50 of the spring. The roller 28 interacts with the Cam cutting jinnai harvesting), under the influence of powerful pressure causes the knife 40 to push the wire, the presence of spring harvesting, separating the end of the first spring blanks from the beginning of the reference coil of the second spring of the workpiece. This method of harvesting allows you to quickly cut the spring without impact, ensuring a clean cut and the quality of the cut springs. The end of the felling of spring corresponds to the point m** on the Cam 22 (Fig.2B). At this point, the Cam 21, while there was a process of cutting, continued to be rotated together with the Cam 22, the distance of points on the lateral surface to the axis about* gradually increased, to the point m** has reached its point n*** contact with the roller 27. At this point, the difference (n***o*- m**o*) was the difference of the radii of the rollers 27, 28 and in contact with its Cam went roller 27, touching the surface of the Cam 21 (point n***). From this point n*** begins the ascent of the last working section of the Cam cutting 22. This work area n***n**** may be steeper or flatter in relation to the parcel nn*, the angle of inclination of these sites depends on the speed of movement of the knife 40; as well as a segment of the ascent, as the plot nn* n***n**** will cause the knife to move in the same direction as before felling; the length of this section will determine the distance that will Promet problem quick return associated with the transition of changing the direction of movement, thereby throwing off the machine with the rhythm of the work, while preserving the quality of the spring. You can perform the work areas shifts knife nn* to logging and n***n**** after felling is not straight, but curved on a more complex law, but in this case it is possible to carry out the continuation of the movement of the knife 40 in the same direction at the same speed, more quickly in comparison with its movement before cutting, or more slowly, i.e., the function changes curvilinear side surface of the second working section of the Cam shifts (slope) can be the same (as the first work area or the other; to the knife continued its movement in the same direction, it is necessary that the first derivative of the function curved surface before and after harvesting would have the same sign (plus or minus). After completing spring return (not shown) will force to move the rollers 27 and 28 on the outside areas of their Cams.

Use for close grip 50 of the same kinematic scheme for progress (before and after felling) during cutting, the positive from the point of view of the synchronization operation of the machine as a whole, facilitate his scheme, could lead to malfunction AB is UNT output of a knife in the same direction from the zone of cutting, however, the presence in the circuit operation of the grip 50 of the torsion shaft 70 will prevent the impact of stroke on the lever 72 and through it on the sleeve of the rocker arm 58 of the gripper 50 at the further movement of the knife after cutting; a torsion shaft 70 will repay the impact energy by converting it into energy torsion, providing a reliable clamping of the gripper 50 at the time of the knife 40 from the cutting zone without crashing into the kinematic scheme.

Thus, due to the relative position of Cams forming, progress, cutting and thrust 45 of the transfer mechanism 4, obsitnik rollers to the time of thinning the first spring blank is wrapped around the first spring harvest will begin winding the second spring piece, not yet separated from the first, the knife 40 will come into contact with the latter supporting a coil of the first spring harvest and respectively with the first reference coil of the second spring piece, the transfer mechanism 4 spring harvesting will take its extreme lower position, it will be a shock to the contact arm 72 with the sleeve 56 closing of the gripper 50, from which the system will work the knee, i.e. the three point strut a, b, C lined up on a straight line, forming a deflection of up to 3 mm due to the stop 59, getting jammed securely grip 50 with proj same direction, upon reaching the end of the working zone of the Cam shifts 21 will stop under the action of a spring return (not shown) will return to its original position, without interfering with the winding of the subsequent spring. While the transfer mechanism 4 moves along the axis of the swing arm 51 toward its upper position, to the formation area of the site on the supporting coil spring (zone uzlovataya). After about 1/2 cycle after the time period (half of the turnover of the shaft 12), the moving mechanism 4 will take its upper position, transporting the workpiece in the area of uzlovataya end of the spring, and for a moment stop (position "instant zero"). Before reaching the capture of 50 with a spring to its upper position, due to the mutual position of Cam 22 and cutting the composite Cam 23-24 mechanism 5 with their rollers 28, 29, 30, due to the rotation of the shaft 13 synchronously with the shaft 12 obecnie rollers 29, 30 mechanism 5 will be in contact with the Cam 23-24 at the end of the waiting area for cone grips 74-75 and for tying boxes 81 with them tying gear 82. At this time, the tapered grips 74-75 are at an angle to each other equal to the maximum opening angle in the waiting area; tying boxes 81 also are in the waiting area with the maximum in the e compound Cam 23-24. The Cam 24, interacting with his obytnym roller 30, is pressing on it with your straight leg and actuates the kinematic chain: roller 30, the arm 91, the rod 92, the lever 93A, the lever b rod 94 (for each capture)(Fig.1); further along the chain: arm 95 (Fig.6A,b), rod 96, the arm 97A, the axis of rotation, the lever 97B, traction 98 (for each capture) - run drive conical grips 74-75, draw them together, reducing the angle of detection. The convergence of the conical seizure occurs while the transfer mechanism 4 is in the direction to its uppermost position, coming closer to him. In the time of arrival of the grip 50 with a spring blank is in its upper position the conical grips 74-75 closer to a distance of slightly greater length of coiled springs; conical sockets seizures, facing each other, ensures the reception of coiled springs even in this position. Reference coils fall in the gap between the cones 74, 75 and then approaching the grips start to fit into the groove in the annular space 76 between the cones 74, 75 and partially on the pad side surface of the insert 78, slipping on an inclined surface (heavy shading) pin 79 liner 78 and the inclined surface (heavy shading) vclone for their movement. Plate 77, located at an acute angle to the edge of the grooves taper grips or parallel to them, advancing together with closing cone grippers 74-75, acting through the ends of the spring, making it a slight turn when it is moving relative to the tapered grips around its longitudinal axis to position, when the excess length of the end of the spring, not placed in the groove taper grips, is included in the gap taper grips (seat anchor loop), and the required length of the free end is located in a groove tapered engagement, limited plate 77. If one end of the anchor coil will not get his plate, another end of the second supporting loop will rest on your plate the second part of the mechanism 5 when the locking spring cone grippers; dovorachivanie springs both plates in one direction. While supporting coil spring is located between the surface bounding plate 85 with the tabs and the base 76 of the chute cone capture, because when closing cone gripper plate 85 with their projections comes into the body of the spring and restricts their movement in space of the reference coil spring; sampling in the body conical surface Worley reference coil to maintain its spatial position between the cones into the groove regardless of the impact bending effort on it while twisting the ends of the spring relative to the reference coil, thereby accurately to withstand the diameter of the coils of the spring, ensuring their quality, and further improve the reliability of the retention springs in the area uzlovataya. During installation cone grippers 74-75 in their position of contact with the spring rod 96 carries over his shoulder 97A two shoulders of the lever 97 system lock to the closed position, arranging the axis of rotation "a", "b", "C" on one line, providing a reliable retention spring workpiece for supporting the coils. In this case, since the movement of the brace - rotary axes a, b, slows, tapered grips 74-75 clamp the ends of the spring the workpiece smoothly without shock, completing their convergence to the minimum length of the spring. At the last moment of navigenie cone gripper pad 78 of its lateral surface with areas under the coils of the spring on the opposite surface sites for the coils of the spring end stop 80, its pin 79 is included in the plug fixed stop 80; the same part of the support and the inner coils of the spring, caught on a support platform (light shading in Fig. 6D) liner 78, only with his other hand, are on the opposite site (light shading) of the lateral surface of the stop 80 (Fig.6E). Terminate traffic cone Zech and fix them in this position by wedging elements of their knee, fixing the reference coils due to their location between the cones on their landing place, limiting their progress in the seat between the cones plate 85 with the tabs on the length of the arc of a size not less than a semicircle, an additional clamp reference coils liner 78 and counter him stop 80, the fixing of the inner coils of the spring liner 78 and counter him stop 80. When this rigid fixing of the inner coil spring is not required to provide a small freedom of movement for the subsequent formation of the node from the end of the spring. At the time of actuation of the knee and taper grips through an additional lever W duplicera lever 97 one of the parts of the mechanism of formation of the node 5, the rod 103 actuates the lever 73, striking the sleeve opening 57 of the grip 50, embossing knee a-b-grip 50 and rasklinila; spring harvesting, while in conical grips 74-75, freed from the grip 50 of the transfer mechanism 4, which begins its downward movement in the open position (Fig.5A), back to the extreme lower position and returning for a new spring. Obkatkoj roller 30 of the Cam 24 comes into contact with its contact zone L2, i.e. with constant major radius (contact clamps with spring). Cone is the position obratnogo roller 30 in a straight branches of the Cam 24, the roller 29 will also interact with a direct branch of the Cam 23; tying boxes 81 moves in the direction towards the axis of the spring a little later, if the waiting area of the Cam 23 knotting boxes more waiting area of the Cam 24 taper grips. Delay the start of the movement knotting bolls in relation to the beginning of the movement of the conical gripper is required to guarantee navigenie tying boxes on the stationary spring when already closed grips that ensures uninterrupted operation of the machine. A more accurate implementation of the elements of the design of the machine allows you to perform the waiting area equal to, but more precise execution mechanisms increases the cost of manufacture of the machine. Tying boxes 81 coming in the spring, entering their grooves in the grooves taper grips 74-75, where by the end of the movement of boxes placed the ends of the spring. Stepping into the groove of the cone capture box with its end padlayat on the edge of the liner 78 the end of a coil spring located in the groove of the conical gripping, bending it to the spring axis to the center of the reference coil. A more accurate orientation podloman the end of the reference coil in the groove parallel to its longitudinal axis contributes to the implementation of a support point for the reference coil, the setting on the side surface ve deforming it. Together with box spring, namely at the end of the reference revolution - the beginning of the inner loop is the same knotting pinion 82 by its own groove. The rotary movement of the boxes to the spring axis (zoom in on the spring) is provided kinematic chain: Cam 23, it obkatkoj roller 29, the Cam 99, the rod 92, the lever 93A triplezero lever 93, his arm V, rod 100, the Cam 101, the rod 102, the plate 89 (namely, the axis of connection "and" thrust plate 102 89 Fig.6b), tying, box 81. Elements 101-102, namely the axis of rotation "a", "b", "b" form a system of strut. In the inflection point of the Cam 23 (transition from rectilinear branches on the arc of a large radius L1) arm 101 with a thrust of 100 "digimet" the midpoint of the knee "b" to the level of the middle line without a blow, fixing tying boxes and tying gear position contact spring.

Thus, the push tying boxes 81 with tying gear 82 on the already fixed in the cone spring clamps the workpiece ends end collisions tying boxes 81 at the end of the reference coil spring harvesting and podamos him about the edge of the liner 78 from the side of the groove, as shown in Fig. 6b by the dotted line. An inner coil spring included in the groove of korobchemo 82 will be located approximately along the sheared off the end of the reference coil spring the coil, and the revolution will be the axis of rotation of the bending of the strap 83.

At this time, the contact obratnogo roller 29 with the contact zone L1 Cam 23 knotting boxes 81 with a spring, which in fact coincides area uzlovataya defined toothed sector gear 104 mechanism 5. The contact area of the boxes with spring L1 represents an arc of a circle of constant radius is approximately 120o; at this time due to the immutability of the radii of the zones of contact Cams 23,24 above the links of the kinematic chain motions conical grips 74-75 and knotting boxes 81 will be fixed. Simultaneously with the completion of a collision boxes on the spring or delay the process begins uzlovataya, since the toothed sector gear 104 is engaged with the driven gear 10 at a time (or delay) with the running roller 29 of the contact zone knotting boxes 81 with spring Cam 23. Arc gear sector gear 104 is, as L1, 120oor slightly less in order to secure the completion of the process of collision boxes on the spring; its driven gear 105 performs one revolution in approximately one third part of the cycle of rotation of the shaft 13. The process of slovesa is on tying gear 82 via spline gear 84 tying boxes 81. It is necessary to say that education site on the reference orbit is treated fairly conventionally, since a node is formed at the transition site "support round - the inner revolution", which is not clearly defined, however, uses terminology education site on the reference orbit. Kinematic chain of the transmission of motion knotting pinion: gear 104 with the sector gear on the shaft 13 is driven gear 105, making one revolution during the rotation of the gear sector, gear 106 (for one of the gears 106 additional link 107) with a gear ratio equal to two, is a bevel gear 108 cardan mechanisms 109 - spline gear 84 with the transfer 1: 1,5 - tying gear 82. Therefore, when the rotation shaft 13 in one turn knotting gear gets three turns of rotation; these three turnover makes bending strap 83 tying gear 82, spinning the end of the spring blanks for supporting round three times, forming three rings on the base turn or less than three rings (2,5) depending on the length of the end of the reference loop.

After uzlovataya ends engages a toothed sector gear 104 is driven by the gear 105, one of the links transmitting rotation on tying six-fold roller 29 by means of the stop 32 of the power of the Central part of the Cam 23-24 goes on the back straight branch of the Cam 23, moving in the direction of the arc (zone) waiting knotting boxes. After some time, defined in one half of the difference between the lengths of arcs L2-L1, another obkatkoj roller 30 taper grips will reach the end zone contact L2 taper grips with spring (she more than 120oas it is seen in Fig.3A,b) Cam 24; with a different emphasis 32 opposite side of the Cam surface 24 of the roller 30 will begin to interact with the opposite rectilinear branch of the Cam 24, moving towards the waiting area taper grips. This will be used partly the same kinematic chain motions for tying boxes and cone grippers (rod 92, the lever 93A). Under the action of the Cam 23 and the work described kinematic scheme boxes 81 will remain in its original position maximum remove them from the axis of the spring piece, and under the action of the Cam 24 and the tapered grips will increase the angle of his erection. This date falls approximately at the time of the cutting knife 40 second coiled springs with the location of the transfer mechanism 4 in its lower position.

After the start of the challenge knotting boxes from spring through combining extreme lower positions of the gripper mechanisms perelom position, however due to the presence of the limiter 119 of the lever 118 and the stop 117 grip 114 hits his arm 118 through the corresponding limiter 119 about the stop 117, stopping, entering wedge-shaped guide 63 his limiter 134 in the "body" of the spring, with one of the coils of the spring will be in the space between the lugs 64 and 66, as in the transfer mechanism 4 (Fig.5A). The space between the lugs 64, 66 is constrained to move in the spring; the height of the stop 64 to the level of the movable arm 120 of the open gripper 114 spring will occupy a position between two pairs of opposing beveled surfaces of the lugs 64, 66 (rare hatching in Fig. 5B, d). Due to the presence of these beveled surfaces of the lugs 64, 66, lying parallel to the coil spring, and further restrict its spatial location, eliminating its bias against the grip 114.

However, the shaft 12 with the lever 110 continues to rotate and stopped by the stopper 119 focusing 117 torsion shaft 113 starts acting torque. While maintaining immobility plate 128 due to its rigid attachment to the frame 9 at its emphasis 131 faces the roller mounted on the lower arm of the rocker arm 126, and collapses into it (Fig.8b). From this blow drugogo 125, putting pressure on the connection of traction 125 with bracket 123 near the middle axis "b", causing the axle to drop down to the level of the average straight line "a" -"in" and a few below, with the formation of the deflection of, lowering the upper arm 120 of the grip on the fixed arm 121; below this level axis "b" will not allow to fall limiter 133 fixed on the lever 121. The spring is oriented oblique opposing surfaces of the stops 64, 66, while between them, under the action of Adigeni it beveled surfaces parallel to one of the coils of the spring, will descend to the ground plate 62 in the wedge-shaped guide 63; further, under the same action of the beveled surfaces of the stop 66, the spring will go into the space bounded on one side by the plate 62, on the other hand, the second pair of beveled surfaces (blacked out) stops 66, forming plots approximated arcs on the sides of the stop 66, the third side of the second pair of beveled surfaces (blacked out) stops 64, forming plots approximated arcs on the sides of the stop 64. This point will coincide with the closing brace (lower axis "b" to line "a"-"b") and holding a grip 114 with spring in the closed position. Adjustment provisions ogranichivat 114 in the closed position, but the magnitude of the cantilever deflection should not be more than 3 mm, since the lowering of the point "b" is further movable arm 120, turning around its axis, will start to move away from the fixed arm 121, weakening the spring clip.

Capture spring transport mechanism 6 is made up of conical wedging clamps 74-75. Because the position of the lever 110 corresponds to at this moment the site of contact obratnogo roller cone 30 of the gripping end of the contact zone taper grips with the Cam spring 24, the opposite rectilinear branch progress cone gripper Cam 24, interacting with obytnym roller 30 will begin to separate them already specified kinematic scheme, releasing the spring for movement mechanism 6. Divorce conical grips 74-75 made to the angle of maximum disclosure. In the closed position of the gripper 114 with a spring having the ends of the transfer mechanism 6 under the action of lever rotation 110 will change direction and go toward its upper position, the area of heat treatment.

When the grip 114 to its upper end position in the heat treatment device 7, namely, at the end spring-loaded contacts 137, due to the presence of the limiter 119 rich is in the bottom position of the gripper 114 a kick lever 118 about the stop 117) and stop capture 114 may be regulated by the position of the stops 119.

However, the shaft 12 with the lever 110 continues to rotate, and stopped by the stop 116, the lever 118 with limiter 119 torsion shaft 113 begins to act the torque of the other direction. When saving the stillness of the plate 128 by its emphasis 130 encounters the roller mounted on the lower arm of the rocker arm 126, and hits him. From this blow the other shoulder of the same arm 126 with a fixed thrust 126, turning "jerks" middle axis "b" up rasklinila capture by lifting the movable arm 120 relative to the stationary 121. Movable arm 120 is raised, releasing the spring and leaving it on the contacts 137 and the transport mechanism 6, subject to the rotation of the lever 110, changing the direction of movement, returns to the area uzlovataya.

At the time of installation of the spring on the spring-loaded contacts 137 roller 31 zooming through smooth step on the working surface of the Cam 25 and through the rocker arm 139 includes a switch 138, powered contacts 137 of the heat treatment equipment 7; however, the spring is part of the circuit operating in short circuit mode. The heat treatment cycle begins after the departure of the capture mechanism 114 6 move down and lasts about the time of the Commission of robotic through the spring and which is sufficient to heat the spring to a certain temperature tempering of the spring and its heat treatment.

At the completion of the cycle of the heat treatment plate 141 pagetutor 8 rotates due to the kinematic link: lever rotation 142, rod 143, the lever 144, being in the zone of heat treatment, gear spring with its scalloped cutouts and assign it without distortions capacity 140 pagetutor 8 in the rightmost position. Then the whole cycle repeats.

Thus, the proposed constructive solutions concerning the machine as a whole, its mechanisms and units covered by a single inventive concept, allow you to create the design of the machine for the production of springs are high quality, operating in automatic mode, making the entire production cycle, from procurement to the final product without the involvement of auxiliary, additional operations outside the machine, without requiring additional hardware, high-performance, reliable, without interruption and marriage.

Sources of information

1. SU 1570826, B 21F 35/02, bull. 22,1990,

2. SU 1052304, B 21 F 35/02, bull. 41, 1983 - the prototype of the mechanisms of movement and capture.

3. SU 1726098, B 21 F 35/00, bull. 14,1992,

4. SU 1234018, B 21 F 35/00, publ. 30.05.86.

5. SU o 776725, B 21 F 35/00, publ. 07.11.80.

6. SU 1268260, B 21 F 35/00, publ. 7.11.86.

7. SU ptx2">

10. SU 1799656, B 21 F 3/00, publ. 07.03.93.

11. SU 506460, B 21 F 35/00, publ. 15.03.76.

12. SU 599896, M. CL.2 B 21 F 35/00, published 30.03.78., bull. 12, the prototype for the machine and its cutting mechanism.

13. SU 471941, M. CL. B 21 F 35/00, publ. 30.05.75., bull. 20.

14. SU 1405938, INC4 B 21 F 35/00, publ. 30.08.88., bull. 24.

15. SU 996012, M CL.. 3 B 21 F 35/02, publ. 15.02.83, bull. 6 - the prototype of the mechanism of formation of the node.

16. SU 1282948, INC4 B 21 F 35/00, publ. 15.01.87., bull. 2.

17. SU 1657263, IPC 5 B 21 F 35/02, publ. in BI 23.

18. EN 2147965, MPK7 B 21 f 35/00, publ. 27.04.2000., bull. 12.

1. Spring-coiling machine, comprising a wire feeder, mechanism of formation, the cutting mechanism mounted on the frame, kinematically connected with the motor via a drive shaft, Cam means rigidly mounted on the working shaft of the machine, with the cutting mechanism kinematically connected with the shaft of the Cam formation, and the feeder wire to the drive shaft, the side working surface of the Cam formation is made curved, the law of removal of each point from the axis of rotation of the working shaft of the mechanism of formation corresponds to the law of change of the diameter of the spring, wherein the l is authorized with the capture device springs, with the device of the progress springs with device orientation support coil springs, with clamping springs, heat treatment device, mechanism for stacking plates of packaging, as well as mechanisms for moving workpieces springs from the cutting zone in the formation area of the site and area education site in the area of heat treatment of each capture device, and means for opening and closing mechanism of formation of the node, device, heat treatment and cutting mechanism each have their own Cam means when the Cam means of the mechanisms of forming and cutting rigidly installed on the same working shaft, which is associated with the levers rotation movement mechanisms, the Cam means of the mechanisms of formation of the host and of the heat treatment is rigidly installed on another working shaft, which is kinematically connected knotting gear mechanism of formation of the node through the mechanism of intermittent rotation, and plate packaging through the lever rotation, working shafts mounted for synchronous rotation, the Cam cuttings equipped with lifting a work area of its lateral surface, the beginning of which is located at the beginning of the zone of formation of the spring Cam formation, At line, connecting the beginning of the work area of the Cam felling with its axis of rotation, the mechanism for moving the spring blanks from the formation zones of the site to the zone of heat treatment is made with the possibility of coincidence of the end positions of the capture, with the same position of the capture mechanism for moving the workpiece from the cutting zone in the formation area of the site, the working surface of the Cam heat treatment is an arc of a semicircle, with the line connecting the center of the working surface with the axis of rotation coincides with the line connecting the beginning of the work area of the Cam cutting with the axis of rotation and focus it in one direction, the Cam mechanism of formation of the node with the contact zone knotting pinion with spring, with the final point of contact of the roller with a contact zone tying gear with spring-loaded Cam mechanism of formation of the node coincides with the starting point of the cutting Cam cutting, the end position of the plates packaging in the packaging area coincides with the beginning of the contact zone knotting pinion with spring, means closing the gripping mechanism to move the spring of the workpiece from the cutting zone in the formation area of the node associated with the kinematic chain mechanism is, the means of closing the opening of the gripper mechanism for moving the spring from the formation zones of the site to the zone of heat treatment kinematically associated with the kinematic chain of the swing.

2. The cutting mechanism containing a movable knife with the ability to interact with others with a knife during cutting, with the possibility of shifts in the winding and cutting the springs associated with the Cam cutting and kinematically associated with the Cam shifts, characterized in that the movable knife set can be rotated in the plane perpendicular to the coil spring at the point of felling, Cams shifts and cuttings mounted rigidly and coaxially on a single operating shaft, a link movable knife with the Cam movement and the Cam cuttings made by one kinematic chain through obecnie rollers advances and cutting, respectively, located coaxially on one shoulder rocker kinematic chains, each in front of his Cam, Cam cuttings equipped with lifting a work area of its lateral surface, the Cam advances provided with a first working lifting area of the side surface, which is located before the start of the working section of the Cam cutting, and the latest work by lifting the plot, the beginning of which coincides with the end of the work area ku is pout work area, and the Cam mechanism cuttings made with the possibility of different times of their interaction with their subcatname rollers.

3. The Cam mechanism cuttings containing Cam cutting, Cam motions knife fitted with a lifting section and made interoperable with the kinematic chain through a contact element at its end, characterized in that the Cam means of the cutting mechanism is a dual Cam, consisting of rigidly interconnected and installed coaxially of the Cam movement and the Cam cuttings, each of which with its contact element in the form of a roller, Cam cuttings are equipped with a work area lift his side surface, the Cams are made with the possibility of multi-temporal contact their working surfaces with their rollers, the side surface of the Cam advances made with four sections, the first section of the movement is located before the start of the working section of the Cam cutting and represents a branch of the ascent, the second segment is performed with a constant radius, and its beginning is also to the working area of the cutting Cam cuttings, and the end coincides with the beginning of the wheelhouse or other nonleaf point cutting Cam robk the to Cam track progress made lifting with a slope of the same sign, the first work area of the Cam shifts, working surfaces obecnych rollers located opposite surfaces of their Cams with a common axis of rotation.

4. The Cam mechanism cuttings under item 3, characterized in that the radius obratnogo roller Cam felling more radius obratnogo roller Cam motions, and the distance from the side surface of the Cam shifts to the axis of rotation of the Cams is greater distances from the points on the side surface of the Cam cuttings to the axis of rotation of the Cams, the beginning of the work area of the Cam felling is the value at which the difference of the distances from the points of the side surfaces of the Cam movement and the Cam cuttings lying on one axial straight line to the axis of rotation of the Cams will be less than the difference between the radial dimensions of their obecnych rollers, the end of the third area is set to rise, when the difference between the distances from the points of the side surfaces of the Cam movement and the Cam cuttings lying on one axial straight line to the axis of rotation of the Cams will be more difference between the radial dimensions of their obecnych rollers.

5. The Cam mechanism cuttings under item 3, characterized in that the beginning of the work area of the Cam cutting is an arc, concave side kotonoha clip.

6. The Cam mechanism cuttings under item 3, characterized in that the parts of the lifting Cams are made straight or curved.

7. The capture device of the spring mechanism for the formation of the node on the reference orbit containing cone capture each core with a coil cone with cone movement capture and springs relative to each other, characterized in that the tapered grips each made in the form of a pair of cones: internal and external, installed one in another coaxially and oppositely, the base radius of the outer cone of greater radius at the base of the inner cone by an amount equal to the wire diameter, with the bell facing the spring, with the formation of the annular area between the cones at the base of the conical engagement with a mounting seat for the reference coil spring in the form of a gutter height, equal to the wire diameter, the diameter of the platform equal to the diameter of the supporting coil rigidly mounted between the tapered grips are installed at a distance not less than the axial dimension of the spring with the possibility of rapprochement.

8. The device shifts the spring mechanism for the formation of the node to the reference coil spring comprising a conical grip the spring with the groove crestlne as a pair of cones: internal and external, installed one in another coaxially and oppositely, with the radii of the bases, the difference between which is equal to the diameter used for the spring wire, with the formation of the seats between the cones at the base of the cone capture under the reference coil springs with a diameter equal to the diameter of the supporting coil rigidly mounted between spaced socket to the spring, the groove of the grip is made at the base of the cone capture the geometric dimensions of the groove defined by the inequality:

ND+h<I< step spring,

where I is the geometric dimensions of the groove;

N is an integer equal to the number of complete rings in the node;

D is the circumference of one ring from the end of the reference coil;

D - ring diameter from the end of the reference coil;

h is the distance between the support and the inner coil in the area of location of the site,

the tool advances further provided with a plate rigidly mounted on the tapered grip the wall of the groove opposite the end point of the contact supporting turn in the tapered grip, the working surface is facing the groove made serving outside the cone capture and oriented parallel to the length of the groove or at an acute angle thereto.

9. Device orientation support VI cone capture and springs relative to each other, characterized in that the tapered grip is made with the possibility of installing it in alignment with the spring mode uzlovataya, tapered grip made in the form of a pair of cones: internal and external, installed one in another coaxially and oppositely, the radius of the smaller base of the outer cone more than the radius of the larger base of the inner cone to the diameter of the wire, is the socket for the spring, with the formation of the seats between the cones at the base of the grip in the form of a trough with a height equal to the diameter of the wire used, the diameter of the platform equal to the diameter of the supporting coil rigidly fixed between them, the device is equipped with a restrictive plate with the tabs, ends of which are located in an arc with a radius, not a large difference of the radius of the reference coil spring and wire diameter, and a length of not less than one-half of the circumference, is rigidly fixed on the basis of the mechanism, while the outer surface of the inner cone and the inner surface of the outer cone is made with the sample surfaces opposite the respective inner surfaces of the protrusions of the plate with a closed grip, and the plate is located at a distance from the base of the closed cone of engagement, not less of dionza spring knotting pinion with a radial groove for supporting a coil and bending strap on the end of gear with the possibility of rotational movement of the gear with a bending strap around the anchor coil springs, the tapered grip support with a coil groove, with the possibility of movement of the cone capture and gears relative to each other and relative to the spring, wherein the tapered grips are made with a boarding place at the base of the grip between the cones with diameter equal to the diameter of the reference coil, the tapered groove grip made in its base opposite tying gear, longitudinal and transverse size which is set to be at least the size of the end of the reference coil springs required for the formation of the node, the height of tying gear with bending bar is less than the lateral dimension of the groove tapered grip, the grips are installed at a distance from each other no less than the axial dimension of the spring with a conical socket to the spring with the possibility of installing tapered grips coaxially with the spring, with the ability to bring them closer to each other, the tapered grip and knotting each gear associated with the Cam mechanism for the formation of the node through the kinematic chain, two final link which side tapered engagement, the gears are connected, the previous link and the tapered engagement, the gear axes of rotation are parallel to each other, with the possibility of installing secondary axis line connection crinagen limiter progress secondary axis.

11. The mechanism of formation of the node to the reference coil springs under item 10, characterized in that the tying gear installed in tying the box, attached to the wafer with the possibility of movement relative to the axis of the closed cone of capture, knotting box on the end with a groove located opposite the groove tapered grip and the inner coil spring, of a width larger than the diameter of the wire spring on the magnitude of the lifting coil springs, the connection tying gear with the Cam means of the mechanism of formation of the node is made through the plate knotting boxes.

12. The device clamp spring mechanism education site on the supporting coil springs, containing for each end of the spring cone capture support with a coil groove with traffic cone capture relatively springs with means for clamping spring, wherein the tapered grip is made with a mounting seat for the reference orbit with the annular space at the base with a diameter equal to the diameter of the supporting coil spring, a groove is made at the end of the reference coil springs at the base of the cone grip, tapered grips installed with the possibility of convergence and installed coaxially with pahute his groove, the surface of the liner facing the spring, made available under the reference part and the inner coil spring, the angle between the planes of which is equal to the angle of rise of the coil, and a stop fixed on the basis of the engine and located in a closed conical seizure in front of the liner opposite the surface is also provided with a pad portion of the abutment and the inner orbits parallel to the grounds of the liner, the gap between the opposing areas of the liner and the rest below the reference coil spring in position of the closed cone of capture is determined by the diameter used for the spring wire, the gap between the opposing pads liner and emphasis under the inner coil of the spring in the closed position of the conical grip determined not less than the diameter used for the spring wire.

13. The device clamp spring mechanism education site on the supporting coil springs under item 12, characterized in that the liner is provided with a pin protruding above the surface of the liner, the surface of the pin facing the spring, made beveled at an acute angle to the axis of the spring is equal to the angle of rise of the coil, the emphasis is equipped with a plug having internal dimensions corresponding to the dimensions of the pin liner, raspoutine node to the reference coil springs under item 12, characterized in that the surface of the liner facing the spring installed in the mode uzlovataya made at an acute angle to the axis of the spring.

15. The device clamp spring mechanism education site on the supporting coil springs under item 12, characterized in that the area under the reference coil springs on the insert is made into the lateral surface of the liner side of the groove tapered grip.

16. The Cam mechanism education site on the supporting coil springs, representing a compound Cam, mounted on the working shaft and connected through its contact elements with actuators, characterized in that the contact elements are in the form obecnych rollers, the Cam is made of a composite of three parts: a middle portion and two lateral Cams - Cam tying gear and Cam cone grip, lateral lobes each made with a lateral surface, consisting of four zones, one of which - the waiting area is an arc whose length is determined by the timeout tapered grip, gear, opposite arc expectations is a zone of contact, representing an arc of a circle whose length is determined by the time Antony from the axis of rotation of the Cam and connected to each other by two rectilinear branches - direct and inverse, the average power part of the Cam is equipped with stoppers located opposite each of its opposite branches in parallel at a distance equal to the diameter of the corresponding obratnogo clip in the end zone contact your Cam with the ability to interact with his obytnym roller, and the rollers are its side surface opposite the side surface of its Cam on the different axes of rotation.

17. The Cam mechanism education site on the supporting coil springs under item 16, characterized in that the side lobes are made symmetrical with respect to the line connecting the centers of the arcs out and contact.

18. The Cam mechanism education site on the supporting coil springs under item 16, characterized in that the lugs of the power part of the Cam is made at the ends with arc turned to my return.

19. The Cam mechanism education site on the supporting coil springs under item 16, characterized in that the length of the arc of contact of the conical gripper with spring is greater than the length of the contact knotting gears with a spring.

20. The mechanism for moving the spring workpiece, comprising a lever capture of two levers, rolling and C the capacity of the contact ends of the levers to each other with a gap, equal to the diameter of the wire spring of the workpiece, means for moving engagement with lever system kinematic connection with a working shaft of the machine, means for closing and opening the gripper, characterized in that the lever grip is made with the possibility to perform swinging movements between their extreme positions, means for closing and opening the gripper contain cravings, one end fixed on a movable arm on an axis parallel to the axis of rotation of the movement arm, with the possibility of rotation about this axis, the other end connected to the bracket on the middle axis of the strut can be rotated relative to the axis parallel to the axis of rotation of the movement arm, a bracket attached to a fixed arm on an axis that can be rotated around this axis parallel to the axis of rotation of the movement arm, sleeve opening, closing, installed with the possibility of shock contact with lever opening in one end position of the capture, with the closing lever in the other extreme position of the gripper attached to the shoulder of the rocker arm rigidly mounted on the bracket, with the possibility of moving average axis of the strut to the line connecting the extreme axis mounting end thrust on the movable R. and back, additionally, a means of opening and closing of the gripper is equipped with a limiter of change of the average axis of the strut specified line established on the fixed lever grip under the middle axis of the strut.

21. The mechanism for moving the spring blanks on p. 20, characterized in that the rocker is made double, between two planes of which is a bracket.

22. The mechanism for moving the spring workpiece, comprising a lever capture of two levers, movable and immovable, which are connected along the axis of rotation of the movement arm about a fixed and made with the possibility of contact of the ends of the levers to each other with a gap between them equal to the diameter of a wire spring of the workpiece, means for moving engagement with lever system kinematic connection with a working shaft of the machine, means for closing and opening the gripper, characterized in that the lever grip is made with the possibility to perform swinging movements between their extreme positions, means for moving the gripper includes a torsion shaft, the end of which is fixed a stationary lever grip, means for closing and opening the gripper include traction strut, one end of which is mounted on podvisotskogo lever, the other end of the bracket can be rotated relative to the Central axis of the strut, parallel to the axis of rotation of the movement arm relative to the fixed arm arm fixed arm can be rotated about an axis parallel to the axis of rotation of the movement arm relative to the fixed lever, pull the opening-closing set on the bracket can be rotated around an axis parallel to the axis of rotation of the movement arm relative to the fixed arm, with the possibility of moving average axis of the strut to the line connecting the end thrust of the strut, mounted on a movable arm, with fastening bracket on the fixed lever or move this line other end connected with one arm of the rocker axis of rotation, the axis of rotation of the rocker arm mounted on the lever associated with the other end of the torsion shaft, a plate rigidly mounted on the frame of the machine, provided with a first pair of stops located on opposite sides of the second arm of the rocker arm in front of him with the shock of contact with the second shoulder of the rocker arm, and a plate with the second pair of lugs on its sides, while the angular distance between the lugs of different pairs on different led what zmoznostjo shock of contact with them, rigidly connected with the fixed lever grip, mounted on torsion shaft, additionally, the fixed lever provided with a restrictor middle axis of the strut located below the axis.

23. The mechanism for moving the spring blanks on p. 22, characterized in that the lever of the opening-closing is further provided with limiters side stops made with the possibility of their regulation.

24. The capture device of the mechanism for moving the spring including a lever movable and stationary made with the possibility of contact of the ends of the levers to each other with a gap equal to the diameter of a wire spring, characterized in that the free ends of the levers at the end of the grip is equipped with limiters stationary and movable lever, a stopper fixed lever is made in the form of a plate rigidly mounted on the fixed lever, at one end provided with a wedge-shaped guide, and on each side two stoppers located symmetrically relative to the longitudinal axis of the plate along it, with two beveled surfaces each height is not less than the distance between the movable and stationary levers in the open position of the gripper, made at the end of the plate, along the side, near the bases of the each of emphasis inclined towards the wedge-shaped guide and to the plane of the plate, at the intersection with a plane parallel to the plane of the plate, forming parts of an arc with a radius equal to the radius of coil springs, each beveled surface of the other pair of beveled surfaces is at an angle to the plane of the plate, the line of intersection with the plane of the plate form parts of an arc with a radius equal to the radius of the coil springs, the height of the second pair of sloped surfaces is not less than the diameter of the wire, limiting the movement arm is a plate of a width not larger than the distance between the lugs of the first stopper fixed on the movable lever set with location parallel to the plate of the first stopper in the closed position of the gripper, the plate of the second limiter is equipped with two symmetrically arranged relative to the longitudinal axis of the plate lugs, arranged at an angle to each other at the end of the plate is equal to the angle of the wedge the wedge-shaped guide plate stopper fixed to the lever and at a distance from each other equal to the width of the wedge-shaped guide in the place of their interaction, lugs carried out with two pairs of beveled surfaces, each of which is parallel to the corresponding skolen the

 

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FIELD: machine engineering, machine tool manufacture.

SUBSTANCE: installation includes housing carrying feed mechanism with drive unit and having drive rollers and also carrying cutting mechanism having movable cutter with drive unit and stationary cutter. First drive roller and driving pinion are mounted drive shaft of feeding mechanism. Said pinion engages with driven gear wheel. Second drive roller is mounted on the same shaft as said driven gear wheel. Drive unit of movable cutter is mounted with possibility of rotation in cutting mechanism; said drive unit includes disc mounted on shaft of feeding mechanism and lever whose one end is mounted on movable cutter with possibility of rotation around axis normal relative to rotation axis of cutter and with possibility of engaging of its other end with disc for moving together with it along rotation path until disengagement of lever end and disc.

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EFFECT: enhanced accuracy and quality of cutting wire.

2 cl, 2 dwg

FIELD: plastic working of metals, possibly manufacture of chopped steel shots.

SUBSTANCE: apparatus includes successively arranged in housing: uncoiling unit; pulling rollers and cutting mechanism in the form of roll pair with uniformly arranged along circle lengthwise cutters shifted one relative to other by pitch half and having in their normal section dents and indentations. Said cutting mechanism is joined with pulling rollers through system of idle gear wheels and pinions. Rolls of cutting mechanism are hollow ones and they are mounted vertically. Indentations of cutters are through ones, they have sizing zone of predetermined length in inlet and they are joined with inner cylindrical surface of rolls.

EFFECT: simplified design, improved operational reliability of apparatus.

7 dwg

FIELD: mechanics.

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EFFECT: provides upgraded cut quality.

4 cl, 1 dwg

Wire-cutting device // 2334581

FIELD: technological processes.

SUBSTANCE: device includes power drive with parallel shafts performing simultaneous oncoming rotation and bearing discs with mated radial grooves. Additionally, clamping discs sprung in axial direction to contact the discs are mounted on the shafts with possibility to move parallel to axes. Knives are mounted in the radial disc grooves and can move parallel to the shaft axis, with discs and clamping conical facet discs as surfaces contacting wire.

EFFECT: extended technological capabilities.

2 dwg

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