Tube cold-rolling mill stand drive
FIELD: process engineering.
SUBSTANCE: invention relates to metallurgy. Proposed drive comprises drive shaft and two gear wheels, two con-rods, two cranks hinged to con-rods and fitted on coaxial crankshafts with wheelwork each including crankshaft with gear wheel fitted thereon and, if required, countershafts locked axially and provided with engaged gear wheels meshed with crankshaft gear wheel, and counterweights fitted on crankshaft and/or countershaft. Closure of side clearances in gearing during stand reciprocation is ensured by providing the drive with extra shaft to engage similar gear wheels of two wheelworks by extra gear wheels fitted on said shaft. Note here that said extra shafts floats axially and is furnished with axial pressure mechanism engaged with housing. All gear wheels represent helical gears with opposite direction of teeth. Drive shaft is arranged parallel about axis of crankshafts while drive gears are fitted directly at drive shaft to engage with similar gear wheels of wheelwork.
EFFECT: new design.
6 cl, 7 dwg
The invention relates to pipe production, namely the cold periodic longitudinal rolling of pipes.
The drive of the working stand cold rolling mill pipe is usually done from an engine through a system of gears and a crank mechanism that converts rotational movement of the rotor of the motor and the gear wheels in the reciprocating motion of the crate.
When the transmission of torque from one gear to the paired him a toothed wheel interaction between work side surfaces of the teeth of these gears, however, the outside lateral surfaces there is always backlash (see, for example, Aiedam, Man. Reference subarea. M: mechanical engineering, 1964, p.30). Side clearance is required for safe operation of the gearing. If the clearance is insufficient, increased noise, there is additional wear and possible burrs on the teeth. It should be noted that the magnitude of the lateral gap is different for different relative angular positions of paired gears and ranges of the normalized standards of tolerance backlash.
During the reciprocating motion of the working cage moves with variable both in magnitude and direction of velocity, i.e. acceleration and braking. The process is scortia stand its kinetic energy increases, this engine consumes energy, handing her the cage through the gears and crank mechanism. During braking stands its kinetic energy decreases. When this energy is transferred from the cage through a crank mechanism, a gear transmission to the engine. When changing the acceleration of the crate on its braking and Vice versa changing the interacting side surfaces of the paired teeth of gear wheels.
When this happens first disclosure of side clearance and subsequent collision of the opposite side surfaces of the teeth, in which the kinetic energy of the moving mass is converted to the potential energy of elastic deformation of the drive elements. As a result, gears and drive shafts are significant dynamic loads (see, for example, Migrashun, Weakenesse. Mills cold-rolling tube. M: mechanical engineering, 1967, p.148). In the area of the collision on the side surfaces of the teeth are formed significant contact voltage, and the legs of the interacting teeth are significant Flexural stresses. Under the action of elevated contact stresses is progressive wear of the side surfaces of the teeth, resulting in a lateral gap further increases.
The magnitude of the contact and bending stresses significantly hung the t of the velocity of mutual rapprochement colliding side surfaces of the teeth, the mass of the working stand and dynamic moments of inertia shaft mounted gears and other parts. With the increase in said speed, the mass of the bucket and dynamic moments of inertia of the rotating masses, these voltage increase. In turn, the rate of mutual rapprochement colliding side surfaces of the teeth increases with increasing lateral clearance and increase in the frequency of the reciprocating motion of the crate.
In addition, for the drive of mill cold rolling mill pipe inherent problems associated with high loads acting on the elements of the fastening bolts to the Foundation. The source of these loads are inertial forces that arise in the working stand in its reciprocating movement. With increasing frequency of the reciprocating movement of the cage the level of these inertial forces are growing and at high frequency reciprocating motion of the cage they can cause the destruction of the fastening elements of the drive.
To compensate for the inertial forces crates are widely used counterweights, which are mounted on rotating shafts. Having balances on rotating shafts of the drive can significantly reduce the level of stress generated in the fastening elements of the drive cage to the Foundation. However, the massive balances significantly in elichevu dynamic moments of inertia of the system. In the dynamic loads associated with the presence of backlash in the gear gearing optional increase.
Known drive stand cold rolling mill pipes (a.c. CCCP 820946, publ. 15.04.1981, bull. Fig. No. 14)containing fixed in the axial direction of a drive shaft rotated by the engine, wheel gears, moving crate, two connecting rod pivotally connected to the cage, two crank, individually pivotally connected with rods mounted on coaxial fixed in the axial direction of the crank shafts mounted in the housing, and the driven gear wheel mounted on the crank shafts.
The main disadvantage of this drive is the presence of a slack of backlash in the gear gearing, which leads to the formation of high dynamic loads on the drive elements.
Another disadvantage is the large load generated in the fastening elements of the drive cage to the Foundation, the source of which are the inertial force produced by the reciprocating movement of the cage.
Also known drive stand cold rolling mill pipe (RF patent 2247613, publ. 10.03.2005)containing fixed in the axial direction of the drive shaft, rotate the engine one drive sprocket, the movable crate, two of the connecting rod, one end of which is pivotally connected to glue the d, and the other end pivotally connected with mounted in the housing common crankshaft, the axis of which is parallel to the axis of the drive shaft. The crankshaft is provided with a single gear mechanism comprising a gear wheel mounted on this shaft, intermediate gear and the intermediate shaft. Leading gear, the intermediate gear wheel and the toothed wheel on the crankshaft consistently associated with each other. In addition, crankshaft and intermediate shaft installed counterweights. All gears are made cylindrical.
Through the use of balances in this drive is achieved at least partial compensation of the inertial forces of the cage acting on the body.
However, open-loop lateral clearances in the toothed gearings accommodation on the shafts balances with significant dynamic moments of inertia, leads to an additional increase of the level of dynamic loads.
Besides, there is known a drive has a number of additional disadvantages.
Use one of the crankshaft to drive two rods fundamentally prevents the crank drive is unbiased. Unbiased is this a crank drive, in which the axis of rotation of the crankshaft (or cranks) lies in the plane of movement Sarnia the rods from the side of the cage.
The use of the actuator rods only one gear mechanism located on one side of the roll axis, due to the existence of appreciable torsional flexibility of the crankshaft, leads to inconsistent movement of the hinges connecting rods connected to the crankshaft.
You must install the intermediate shaft only one counterweight, the plane of rotation of which must coincide with the plane of rotation of the corresponding counterweight on the crankshaft, leads, in some cases, unnecessarily complicating the design of the drive.
Closest to the claimed technical essence is the drive of mill cold rolling mill pipes (U.S. patent 5540076, 30.07.1996)containing fixed in the axial direction of a drive shaft rotated by the engine, leading bevel gear, a movable crate, two connecting rod pivotally connected to the cage, two crank, individually pivotally connected with rods mounted on coaxial fixed in the axial direction of the crank shafts mounted in the housing. Cranks provided with a similar gear mechanisms. Each of the gear mechanisms includes a crank shaft has mounted on it a gear wheel, and may also contain fixed axially mounted in the housing intermediate VA is s, axis which is parallel to the axis of the crank shaft, mounted on these shafts intermediate gears. These intermediate gears and the gear on the crank shaft sequentially coupled with each other. In addition, the crank and/or the intermediate shaft can be installed counterweights.
The drive of each of the crank is from a separate timing mechanism that allows the crank mechanisms unbiased. The system balances lets well enough to compensate for the inertial load due to the reciprocating movement of the cage.
However, the known drive has a number of disadvantages.
So, multidirectional rotation of the cranks and connecting rods causes a transverse overturning moment acting on the crate.
In addition, the location of the axis of the drive shaft parallel to the axis of rolling requires the use of bevel gears for transmitting rotation from the drive shaft to the gear mechanisms. However, it is known that the bevel gear are less reliable than cylindrical.
The main disadvantage of this drive is the presence of a slack of backlash in the gearing paired gear wheels, that provides high level of dynamic n is grusak, generated when the shock closure of the above-mentioned gaps. He balances leads to additional dynamic loads.
The technical result of the application of the invention is to reduce the dynamic loads acting on the drive elements, by ensuring the closure of backlash in the gears during the entire cycle of the reciprocating motion of the crate.
The technical result is achieved due to the fact that the actuator is equipped with an additional shaft, combining similar gears of the two gear mechanisms through installed on the shaft of additional gears. Additional shaft is made floating in the axial direction with axial pressing, paired with the body. All gears are made cylindrical, while the gears are installed on different crank shafts have different direction of the angle of the teeth, in Addition, unlike the prototype, a drive shaft mounted parallel to the axis of the crank shaft, and wheel gears mounted directly on the drive shaft and associated with similar gears of the two gear mechanisms.
The absolute value of the angle of the teeth of gear-wheels is in the range from 5 to 45 degrees.
On the additional shaft also installed counterweights.
Drive shaft also installed counterweights.
The mechanism of axial pressing is made in the form of a hydraulic cylinder.
Parallel to the axis of the lead, crank, intermediate and additional shafts are arranged in space so that they do not belong to the same plane.
The prior art drive stand cold rolling mill pipes (Sagoff, Pamcallback and other Cold rolling pipe. Sverdlovsk, Metallurgizdat, 1962, pp.62-63), containing two leading helical gear mounted on the drive shaft, the axis of which is parallel to the axis of the crank shaft. As a rule, in the scheme of the actuator drive shaft is floating, which allows for slow rotation of the shaft more or less evenly distribute the load between the two toothed gearings. By increasing the speed of rotation increases axial inertial force acting on the drive shaft, resulting in uneven distribution of the load increases, up to the fact that the entire torque is transmitted by a single link.
The claimed technical solution is fixed in the axial direction of the drive shaft shall not be a member function that distributes the load between the links, and performs the task of closing the circuit, consisting of a gear mechanism of a single crank, an additional shaft and gear mechanism is ZMA second crank, what is necessary for the circuit of backlash.
The prior art also known device providing a closure of backlash in the two-stage gear transmission swing mechanism (patent RF 2225549, publ. 10.03.2004). In this device, the driving shaft is made floating in the axial direction, and all other shafts are fixed in the axial direction. This drive shaft has two helical gears with opposite direction of the tooth. On each of the two intermediate shafts mounted intermediate gear and the intermediate gear. Helical gear mounted on the drive shaft, connected with the intermediate helical wheels, and idler are associated with the slave gear wheel mounted on the output shaft. Floating drive shaft is spring-loaded in the axial direction. Closure of gaps in the two-stage gear transmission is carried out by application to the drive shaft of the required axial force of the spring. In the known device the rotation of the drive shaft is installed from it leading gears. In the General case, the rotational drive of the drive shaft can be carried out via a coupling or other device providing the connection of the drive shaft with the engine.
The main disadvantage of the known solution is that floating done the h drive shaft, associated with the mechanisms for its rotation. As a result, for example, on the teeth of a leading gear wheel of the forces which hinder axial movement of the shaft. Similar forces can also act clutch or other device connecting the drive shaft with the engine. In the known device does not provide a guaranteed circuit of backlash.
Another disadvantage is that the described scheme is applicable only to two-stage gear.
In addition, a spring-loaded drive shaft with massive gears forms an oscillatory system in which at certain speeds can result in resonance phenomena.
The proposed actuator floating performed additional shaft, which is not related to external mechanisms and devices that prevent its free axial movement. This provides an opportunity for ensuring closure of backlash in an arbitrarily long chain on the gears in the whole range of mutual angular positions of the toothed wheels.
In addition, the execution mechanism of the axial pressing in the form of a hydraulic cylinder allows to eliminate possible resonance phenomena in the mechanism also prevents the guaranteed closing gaps.
The invention p is explained by the drawings, where
- figure 1 shows a diagram of the drive cage mill cold rolling of tubes in General;
- figure 2 shows a diagram of the drive of mill cold rolling mill pipes that do not contain intermediate shafts;
- figure 3 shows the mechanism of the axial pressing;
- figure 4 shows the drive of mill cold rolling mill pipes that do not contain the intermediate shaft and the axis of the shafts do not belong to the same plane (top view);
- figure 5 is given a cut of the drive (figure 4) vertical plane passing through the axis of rolling;
- figure 6 shows the same section of the actuator, each of the gear mechanisms which contains one intermediate shaft;
- figure 7 shows a similar section of the actuator, each of the gear mechanisms which contains two of the intermediate shaft.
Drive stand cold rolling mill pipes (figure 1) contains a movable crate 1, capable of reciprocating movement along the axis of rolling 2. With rolling stand 1 pivotally connected to two of the connecting rod 3.
Each of the connecting rod 3 is pivotally connected with its crank 4. The cranks 4 rigidly mounted coaxially on the crank shaft 5, mounted in the housing 6 and is fixed relative to the housing in the axial direction.
On the crank shaft 5 is rigidly mounted a gear-wheel 7, which tells the rotation shafts of the cranks. Drive krivos the surface is carried out by means of two similar gear mechanisms 8 and 9, consisting of similar elements that are conjugate to each other in the same sequence. Each of the gear mechanisms 8, 9 includes the already mentioned crank shaft 5 with the toothed wheel 7. In addition, the gear train includes fixed axially mounted in the housing 6 of the intermediate shafts 10, 11, 12 is rigidly mounted intermediate gears 13, 14, 15. Note that for the implementation of the proposed technical solution the number of intermediate shaft and the intermediate gear wheels is negligible, that is, between the intermediate shafts 11 and 12 can be mounted unlimited additional number of intermediate shafts mounted intermediate gears.
All intermediate shafts mounted in the housing in such a way that their axes parallel to the axis of the crank shaft.
The intermediate gears 10, 11, 12 and the gear wheel 7 on the crank shaft sequentially coupled with each other, i.e. form a kinematic chain wheel, alternately transmitting rotation from one to the other. The location of the gear wheel 7 in this circuit is not significant.
With the same intermediate gears 10 gear mechanisms 8 and 9 involve leading gear wheel 16 mounted directly the NGOs on the control shaft 17, fixed in the axial direction. Drive shaft 17 is installed in the housing 6 parallel to the axis of the crank shaft 5 and is driven by a motor (not shown) either directly or via a gear (belt, timing and so on).
On the crank shaft 5 can be installed counterweights 18 to compensate for the inertial forces from the rolling stand. The counterweight can be mounted on intermediate shafts, for example, the counterweight 19 is installed on the same two intermediate shafts 11.
According to the invention, the actuator is provided with an additional shaft 20. On the additional shaft 20 is equipped with two additional gears 21 through which this shaft is paired with a similar toothed wheels 15 gear mechanisms 8 and 9. In the specific example shown in the drawing figure 1, the wheels 15 are intermediate gears.
Additional shaft 20 is made floating, that is installed in the housing 6 can move in the axial direction. In addition, the additional shaft 20 provided with a mechanism of axial pressing 22, paired with the housing 6.
All gears of the drive cage (16 leading, intermediate, 13, 14, 15, wheel cranks 7 and an additional 21) is made cylindrical. This toothed wheel 7 installed on different crank shafts, as shown in the drawing Phi is .1, different direction of the angle of the teeth. It should be noted that setting the direction and amount of inclination of the teeth of gear wheels 7 completely and unambiguously defines the direction and magnitude of the tilt angle of the teeth for all other gears, such as gears, kinematically associated with each of the wheels 7, sequentially coupled to each other.
The absolute value of the angle of inclination of the teeth of the two toothed wheels 7 may be different, which does not affect the efficiency of the proposed device. However, preferred from the viewpoint of unification of the design is, when the absolute values of these angles are equal.
As shown by calculations, rational values of absolute values of the angles are in the range from 5 to 45 degrees. At angles less than 5°, the amplitude of the additional axial movement of the shaft 20, which provides compensation of kinematic errors of the gears becomes unreasonably large. At angles greater than 45°, requires unreasonably large axial force pressing additional floating shaft 20.
The proposed solution is able to ensure the closure of gaps in the gear mechanisms, containing an unlimited number of intermediate shaft and the intermediate gear wheels. Meanwhile, it is obvious that the tick shafts must have a functional purpose. In addition to the use of the intermediate shafts to install balances, these shafts can be used for connection to a drive additional external devices, sensors, etc. However, the analysis of these additional features is beyond the scope of the technical problem. In each case the number of intermediate shafts is determined by the constructive considerations of expediency.
Figure 2 shows the drive of mill cold rolling mill tubes, which contains intermediate shafts. Composition of structural elements of this drive is almost completely coincides with the actuator shown in figure 1, with the exception of one each of the gear mechanisms 8 and 9 includes a single shaft (crank shaft 5) and one toothed wheel (gear crank 7). Accordingly, the leading toothed wheel 16 and additional gears 21 are associated with a similar toothed wheel gear mechanisms 8 and 9, namely, the gear wheels 7 mounted on the shafts of the cranks 5.
Additional shaft 21 provided with a mechanism of axial pressing 22.
On the additional shaft installed counterweights 23.
Drive shaft installed counterweights 24.
The mechanism of axial pressing (figure 3) is made in the form of a hydraulic cylinder containing two basic elements: the body and the piston. One who C these elements, for example, the piston 25 of the cylinder, is rigidly connected with additional floating shaft 20, and the other, for example, the housing 26 of the hydraulic cylinder, is connected with the housing 6 of the drive. The cavity 27 of the hydraulic cylinder is connected with the pressure source p. This creates an opportunity to attach to the shaft 20 force acting in the direction of its axis.
Figure 4 shows the drive of mill cold rolling mill tubes, in which each of the gear mechanisms 8, 9 consists of the crank shaft 5 and the gear of the crank 7. Thus parallel to the axis of the lead 17, the crank 5 and 20 extra shafts are arranged in space so that they do not belong to the same plane (figure 5). As can be seen from the drawing, the axis of the lead 17 and 20 extra shafts are located below the axis of the crank shaft 5.
On the crank shaft 5 is equipped with counterweights 18, and the additional shaft counterweights 23.
The cranks 4 and the connecting rods 3 are located on the same side of the crank shaft 5, which is turned towards the axis of the rolling mill 2.
Thanks to this arrangement, aimed at the rational arrangement of the elements of the device in space, you can reduce the overall dimensions of the drive.
Figure 6 shows the drive of mill cold rolling mill tubes, in which each of the similar timing mechanisms consists of the crank shaft 5, the gear wheel of the crank 7, one ol the intermediate shaft 11 and one set on the shaft of the intermediate gear 14.
Parallel to the axis of the lead 17, the crank 5, the intermediate 11 and 20 extra shafts are arranged in space so that they do not belong to the same plane, namely, the axis of the lead 17 and 20 extra shafts lie in a horizontal plane below the horizontal plane passing through the axis of the crank shaft 5 and the axis of the intermediate shaft 11.
On the intermediate shaft 11 is installed counterweights 19. On the additional shaft 20 balances not.
In this embodiment, actuator, due to the low inertia of the additional shaft can be reduced axial force pressing, and without loss of effect guaranteed circuit of backlash in the gear links.
Figure 7 shows the drive stand cold rolling mill tubes, in which each of the similar timing mechanisms consists of the crank shaft 5, the gear wheel of the crank 7, two intermediate shafts 10 and 11 and two intermediate gear wheels 13 and 14.
Parallel to the axis of the lead 17, the crank 5, the intermediate 10, 11 and 20 extra shafts are arranged in space so that they do not belong to the same plane, namely, the axis of the lead 17 and 20 extra shafts lie in a horizontal plane below the horizontal plane passing through o and the crank shaft 5 and the axis of the intermediate shaft 10, 11. On the intermediate shafts 11 and 10 is installed counterweights 19 and 28, respectively.
An additional advantage of this drive is the possibility of full compensation overturning moment generated by the rotation balances.
It should be noted that the proposed actuator design stand cold rolling mill of the pipe allows you to crank mechanisms are unbiased, as illustrated in the drawings 5, 6 and 7.
All item numbers in the drawings, figure 4-7 not mentioned in the description of these drawings correspond to the previously adopted the notation in figure 1, 2.
Drive stand cold rolling mill pipes (figure 1) works as follows.
Consider an initial condition actuator, in which the motor is not rotating, the force of the axial pressing is absent, and the gaps in the teeth, the toothed wheels are not locked.
After application to the secondary shaft 20, is made floating in the axial direction, the axial forces generated by the mechanism of axial pressing 22, the additional shaft begins to move in the direction of its axis. In the absence of rotation of the additional shaft 20, taking into account the different directions of inclination of the teeth on additional gear wheels 21 side clearance in the gear toothed wheels these wheels with intermediate gears 15 are selected. After closure specified for the Directors gears 15, the shafts 12 which are fixed against axial displacement, begin to rotate in opposite directions (angles of rotation of the wheels is very small and determined by the angular amount of backlash). If this consistently happens sampling of backlash in all toothed gear wheels forming part of the gear mechanisms 8 and 9, and the gearing of the toothed wheel 13 with the leading toothed wheel 16. Note that in the process of closure of backlash similar toothed wheel gear mechanisms are rotated in opposite directions. Due to the fact that the leading gear 16 rigidly connected with the drive shaft 17, and it is fixed in the axial direction, after the selection of backlash rotation of the toothed wheel gear mechanisms is terminated. Because the force of the axial pressing continues to act on the secondary shaft 20 and after closure of backlash, the teeth on the paired gear wheels are tucked to each other forces, the magnitude of which is uniquely associated with the magnitude of the axial force pressing, and can be determined from the equilibrium conditions of the gears of the drive for the known dependencies.
When the drive is idling the motor causes the rotation of the drive shaft 17. In the start to rotate all the gears and drive shafts and crank fur the isms, consisting of cranks 4 and connecting rods 3, according to the reciprocating movement of the cage 1 along the axis of rolling 2. Thus the lateral clearances in the toothed gearings remain closed, because the force of the axial pressing continues to operate. Given the presence of kinematic error in the toothed gearings, guaranteed sample of backlash is provided by a small axial movements of the additional shaft during rotation of the actuator. It should be emphasized that a similar rotation of the toothed wheels and shafts is unidirectional, in contrast to rotate in sampling mode, lateral clearances described above.
After the acceleration of the actuator to the operating speed begin to push the workpiece into the cage 1, the reciprocating movement. In the implementation process for the crate are external technological force and the inertial force associated with acceleration and deceleration of the cage during its reciprocating movement. These forces have the same direction, is transmitted through the connecting rods 3 cranks 4 and, further, on the gears 8 and 9, the lead 17 and 20 extra shafts. The result forces the toothed gearings, formed by the action of the axial pressing on the secondary shaft 20, are starting to change. Moreover, in the gear mechanism one krivosha is as these forces increase, while in the gear mechanism of the other of the crank they decrease. To guarantee the closed state of the side clearances axial force pressing should be chosen in such a way as to force the toothed gearing of the whole drive was reduced to zero. The required amount of force axial pressing is determined by known methods, based on the conditions of dynamic equilibrium of the drive elements.
When the drive is at operating speed floating additional shaft 20 continues to make a small axial movement to compensate for kinematic errors gears and elastic deformation of load drive elements.
The process drives stand cold rolling mill tubes, shown in figure 2, 4, 6 and 7, is completely similar to that described above.
Guaranteed non-disclosure of backlash eliminates dynamic loads resulting from impact of closing gaps. Thereby is achieved a noticeable reduction in the overall level of stress in the drive elements and a corresponding increase their durability.
In practice, there are two possibilities of use of the achieved technical result, a reduction of dynamic loads. One is the intensification process by increasing the number of cycles of reciprocating motion of the texts stand, performed in unit time. Another is to reduce the material consumption of the drive by reducing the size of its elements.
1. The drive of the rolling mill stand for cold rolling of tubes containing fixed in the axial direction of a drive shaft rotated by the engine, wheel gears, two connecting rod pivotally connected to the cage, two crank, individually pivotally connected with rods mounted on coaxial fixed in the axial direction of the crank shafts mounted in the casing, and is provided with a similar gear mechanisms, each of which includes a crank shaft has mounted on it a gear wheel and, if necessary, fixed in the axial direction is mounted in the housing intermediate shafts, the axis of which is parallel to the axis of the crank shaft, mounted with these the shafts of the intermediate gears are sequentially coupled with each other and the toothed wheel on the crank shaft, with the installation of counterweights on the crank and/or the intermediate shaft, characterized in that it is provided with an additional shaft, combining similar gears of the two gear mechanisms through installed on the shaft of additional gears, while the additional shaft made floating in the axial direction and provided with a mechanism axially what about the clicking, paired with the body, all the gears are made cylindrical, toothed wheel, installed on different crank shafts have different direction of the angle of the teeth, a drive shaft mounted parallel to the axis of the crank shaft, and wheel gears mounted directly on the drive shaft and associated with similar gears of the two gear mechanisms.
2. The actuator according to claim 1, characterized in that the gear wheels are made with the absolute value of the angle of inclination of their teeth from 5 to 45°.
3. The actuator according to claim,1, wherein said additional shaft installed counterweights.
4. The drive to claim 1, characterized in that the drive shaft installed counterweights.
5. The actuator according to claim 1, characterized in that the mechanism of axial pressing is made in the form of a hydraulic cylinder.
6. The actuator according to claim 1, characterized in that parallel to the axis of the lead, crank, intermediate and additional shafts are arranged in space so that they do not belong to the same plane.
FIELD: four- and six-roll stands of rolling mill, operation method of such stands.
SUBSTANCE: four-roll stand includes two rolling rolls and two backup rolls driven by means of drive spindles. Both backup rolls are joined through disconnection device with motor. Each rolling roll is provided with disconnection device for joining respective drive spindles with rolling rolls. When small-diameter rolling rolls are used, said devices are disconnected and there is no connection with motor. When large-diameter rolling rolls are used, they are joined through said devices with motor. Six-roll stand includes two rolling rolls, two backup rolls and intermediate rolls arranged between rolling rolls and backup rolls. Each backup or intermediate roll driven by means of spindle is provided with disconnection device joined with one or several motors. Each rolling roll is provided with disconnection device for joining respective drive spindle with rolling rolls. When small-diameter rolling rolls are used said devices are disconnected and there is no connection with motor. When large-diameter rolling rolls are used they are joined with motor. Combination type drive unit of four- or six-roll rolling stand provides joining of large-diameter rolling rolls directly with motor but small-diameter rolling rolls are driven only due to friction with adjacent backup or intermediate rolls. In order to provide selective operation of rolls in four-roll stand having first small-diameter rolling rolls and second large-diameter rolling rolls, motor drives to rotation only backup rolls in case of operation of small-diameter rolling rolls and only rolling rolls in case of operation of large-diameter rolling rolls. In order to provide simultaneous operation of small-diameter and large-diameter rolling rolls in four-roll stand, motor drives respective backup roll for operation of small-diameter rolling roll and only rolling roll itself for operation of large-diameter rolling roll. In order to provide selective operation of rolls in six-roll stand having first small-diameter rolling rolls and second large diameter rolling rolls, motor drives only backup and(or) intermediate rolls for operation of small diameter rolling rolls and only rolling roll itself for operation of large-diameter rolling roll. In order to provide simultaneous operation of small-diameter and large-diameter rolling rolls in six-roll stand, motor drives only respective backup and(or) intermediate roll for operation of small-diameter rolling rolls and only rolling roll itself for operation of large-diameter rolling roll.
EFFECT: rapid adjustment for rolled materials of different thickness and (or) hardness values, possibility of selective operation with small-diameter and large-diameter rolling rolls at lowered cost.
20 cl, 2 dwg
FIELD: improved designs of drive un its for pilger tube cold rolling mills, possibly used in any mills with stand performing reciprocation motion.
SUBSTANCE: drive unit of mill for cold pilger rolling of tubes includes mounted in casing planetary gear-crank unit with vertical rotation axis and with crank-up pin performing straight reciprocation motion and supporting rolling bearing assembly; tie rod joining crank-up pin carrying movable cassette with working rolls and balancing weights. One of said weights is arranged on shaft of crank and other weight is mounted in planetary gear-crank unit. Drive unit also includes additional casing mounted on rolling bearing assembly and second tie rod. One ends of both tie rods are rigidly secured to additional casing; their other ends are coupled with movable cassette carrying working rolls. Additional casing is arranged lower than guide mounted along rolling process axis. Rolling bearing assembly of crank-up pin is spherical. Tie rods are mounted at both sides of said spherical bearing assembly in plane parallel to rolling axis. Balancing weight mounted in shaft of crank is arranged under tie rods and guide over casing that houses planetary gear-crank unit.
EFFECT: improved operational reliability, increased useful life period of drive unit due to its lowered loads.
FIELD: process engineering.
SUBSTANCE: rolling mill roll 1 has two necks 2 of which, at least, one is equipped with sleeve locked against turning. Note here that roll neck sleeve is surrounded by bearing bush 9 fixed in pad 10. Note also that polygonal joint between roll neck 2 and neck sleeve 4 allows their relative locking against turning. Besides, thrust ring 11 with collar is arranged between neck sleeve 4 and bearing bush 9. Collar polygonal inner edge enters with geometrical closure the polygonal outer edge of step 5,15 of roll neck 2.
EFFECT: new design of rolling mill.
6 cl, 3 dwg
FIELD: process engineering.
SUBSTANCE: proposed method comprises electroslag remelting of 470±5 "хвн." 270±5×3050±50 mm ingots from 04X14T5P2"Ф-Ш"-grade low-ductile steels with boron content of 2.0 to 3.0% with bottom and shrinkage parts and specified height to make Pilger heads in tube stock rolling and seed ends from ductile carbon steels, turning and boring to make hollow ingots to be rolled to tube stock. It comprises also removing machining wastes, that is, Pilger heads and seed ends to make tube sections of ductile carbon steels. Then, tube sections are cut to tube stock to be bored and turned to tube billets. Holes are bored for pull chain for hot shaping at ductile carbon steel parts. Note here that billet sizes and machining conditions are specified fat all machining steps.
EFFECT: reduced wastes and rejects.
FIELD: process engineering.
SUBSTANCE: proposed method comprises electroslag remelting of ingots from 04X14T5P2"Ф-Ш"-grade low-ductile steel with boron content of 2.0-3.0% and bottom and shrinkage parts from ductile carbon steels, turning said ingots to produce billets wherein through central bore is drilled, and heating them to 1040-1060°C. First, said ingots are pierced at helical rolling stand. Then, they are rolled at Pilger stand to tube sections to cut off process wastes so that ductile carbon tube 500-600-mm-long ends are made on dummy ingot and Pilger head side. Then, they are straightened and cut into multiple length tube stock and ends. Now, they are bored and turned to cylindrical tubes to be shaped to hexagonal tube billets. Note here that billet sizes and machining conditions are specified for all machining steps.
EFFECT: decreased wastes and ruled out rejects.
FIELD: process engineering.
SUBSTANCE: proposed method comprises making hollow ingots by electroslag remelting from low-ductile steel "04Х14Т5P2Ф-Ш" with boron content of 2.0 to 3.0%, boring and turning said ingots to hollow ingots and be heated and rolled to tube stock and cutting off process wastes, i.e. Pilger heads and seed ends. Thereafter, tube stock is hot-sawn into multiple tubes and ends, and straightened. Multiple tubes are cut into two billets to be bored and turned into tube billets to be shaped to preset size hexagonal tubes. Note here that billet sizes and machining conditions are specified for all machining stages.
EFFECT: decreased wastes rules out cracks and flaws.
3 cl, 1 tbl
FIELD: process engineering.
SUBSTANCE: proposed method comprises making ingot by electroslag remelting, turning their outer surface to remove casting defects, drilling central 100±5,0 mm-dia bore, heating the ingots, piercing at helical rolling mills, rolling at Pilger mill into tube stock, cutting the latter into tube sections, their straightening and hot hexagonal tube 257+2.0/-3.0X6.0+2.0/-1.0X4300+80/-30 mm-billets. Required quality is ensured by that electroslag remelting of 470±5 "хвн." 270+5×3050±50 mm ingots from 04X14T5P2"Ф-Ш"-grade low-ductile steels is performed to make Pilger heads in tube stock rolling and seed ends from ductile carbon steels, turning and boring to make hollow ingots to be rolled to tube stock. It comprises also removing machining wastes, that is, Pilger heads and seed ends to make tube sections of ductile carbon steels. Then, tube sections are cut to tube stock to be bored and turned to tube billets. Holes are bored for pull chain for hot shaping at ductile carbon steel parts. Note here that billet sizes and machining conditions are specified at all machining steps.
EFFECT: higher quality of tubes.
SUBSTANCE: device includes movable wedge moved with a screw fixed with its projection against longitudinal displacement in slot of bottom wedge, and wedges fixing the rack. Rack is installed in the housing restricting it against longitudinal displacement. Possibility of separate displacement of wedges and provision of minimum side gaps in rack-pinion engagement, reduction of metal consumption and labour intensity of production of roll stand equipment due to reducing the overall dimensions of wedge connection as to height and simplifying the production of wedges and bottom wedge, which do not require high accuracy of angles of their slopes is provided due to the fact that additional movable wedge is located opposite the movable wedge. Rotating nut is installed on screw in movable wedge. Bottom wedge is provided with two symmetrical surfaces for inclined surfaces of movable wedges. Screw has left and right threads interacting with corresponding threaded holed of wedge and nut. Racks are engaged with pinions of rolls. Bottom wedge is fixed in pinion rack with projections against longitudinal displacement.
EFFECT: improving reliability and operating life of device for transverse movement of racks of rack-and-pinion drive of rolls of roll stand of tube cold rolling mill.
FIELD: process engineering.
SUBSTANCE: proposed roll mill comprises stand with working rolls, main drive, tube turning mechanism with two transmission shafts coupled with main drive via converter of uniform rotation into irregular rotation. One of said shafts is articulated with mandrel rod chuck while another one is coupled via gearing with biller chuck and tube turning front chuck. Stepless adjustment of precise alignment of grooves in chuck cams with those in pass is ensured by coupling transmission shaft with gearing drive gear by means of clamping and bearing conical couplings furnished with clamping and unclamping bolts while front chuck cam cross-section profile is provided with grooves mating with profile of finished ribbed tube.
EFFECT: accurate sizes, reduced wastes, expanded range of finished products.
FIELD: process engineering.
SUBSTANCE: proposed method comprises refacing roller pass groove. After refacing, roller are mounted into stand. Note here that pass size is increased by amount of wear. Note here that rollers with variable-section pass groove are turned by amount compensating pass wear size on varying positions of rollers. Rollers are turned by displacing tooth-rack drive racks toward rolling start. Displacement of said racks is effected in lengthwise direction in compliance with stand design to allow aligning top and bottom roller pass grooves and make pass groove sections aligned with turn angle of crank that defines stand position.
EFFECT: simplified design, higher reliability, longer life, lower costs.
SUBSTANCE: invention refers to the rolling mill of cold pilger mill. Rolling mill includes reciprocal moving buckle plate with operating and support rolls and power stand comprising basis and cap with supporting rail, vertical stands connecting basis and cap, mechanism of cap position adjustment and mechanism of rolling only with direct move of the buckle plate. Possibility to eliminate hinge joints from the mill drive and thus to increase its reliability is ensured by the fact that the basis of the stand includes additional body with supporting rails at two eccentric shafts with bearings in the basis of the stand and general impulse rotation drive. At this support rails are installed in contact with lower support rolls of the buckle plate.
EFFECT: increased reliability of cold pilger mill construction.
1 dwg, 3 dwg
FIELD: process engineering.
SUBSTANCE: invention relates to metal forming and may be used at tube hot rolling mill stands. Proposed method comprises piercing the sleeve on mandrel in rolls with conical inlet and outlet and riser pad there between. Note here that mandrel front plane is arranged in roll riser pad. Distance between rolls at the point rolls break off rolls in outlet cone is kept constant while mandrel work section length equals that of outlet cone section. Arrangement of mandrel front plane in roll riser pad, billet free deformation (primary gripping) is executed solely in disk mill roll inlet cone while deformation of wall and roll diameter rising is performed in outlet cone.
EFFECT: higher process efficiency.
1 dwg, 1 ex
FIELD: rolled tube production, namely processes for piercing ingots and billets for making seamless hot-deformed large-diameter tubes.
SUBSTANCE: method comprises steps of heating ingots and billets until yielding temperature; piercing them to hollow thick-wall sleeves in first skew rolling mill for further expanding to thin-wall sleeves in second skew rolling mill and rolling to large-diameter tubes in plants provided with automatic or pilger mills; piercing ingots and billets to thick-wall sleeves in first piercing mill with working rolls driven to rotation in one side and expanding billets to thin-wall sleeves in second piercing mill with working rolls driven to rotation in opposite side.
EFFECT: enhanced geometry of tubes, lowered metal consumption, improved efficiency of tube rolling plants.
FIELD: tube production processes and equipment, namely preparation of rolls of pilger mills for hot rolling of tubes.
SUBSTANCE: method comprises steps of mechanically working portion of roll in roll-turning machine tool with use of contour follower for surfacing it with overlap 5 - 10° to side of cold portion from zero point and from angle of lengthwise outlet; under-flux surfacing working portion with wear-resistant refractory steel layer having allowance for mechanical working; mechanically working rolls with use of contour follower until their ready size and grinding working surface. Mechanical working of rolling portion of roll after surfacing is performed along portion from 0.25 - 0.30 of striker length until end of angle of lengthwise outlet adjoined to polishing portion. Grinding of polishing portion and of 0.25 - 0.30 of angle of lengthwise outlet adjoined to polishing portion is realized. Mechanical working of rolling portion of roll for surfacing from zero point until 0.25 -0.30 of striker portion is performed while taking into account allowance of surfaced layer for finish working.
EFFECT: enhanced strength of rolls of pilger mills, improved accuracy of their geometry size and quality of tube surface, lowered consumption of high-cost steel wire rod.
2 cl, 1 dwg, 1 tbl
FIELD: rolled tube production processes and equipment, namely manufacture of hot deformed mean- and large-diameter tubes of corrosion resistant hard-to-form steels and alloys, possibly making tubes in tube rolling aggregates with pilger mills.
SUBSTANCE: method comprises steps of drilling electroslag-refining ingots or billets with diameter 380-500 mm; holding them on grates of furnace at temperature 500-550°C for 70-95 min depending upon diameter of blank; heating up to temperature 1120 - 1140°C at rate 1.4 - 1.5 °C/min; piercing billets for forming sleeves at revolution number of rolling rolls 25 - 40 rev/min on mandrel with diameter providing reduction degree in pilger mill no less than 25 mm; realizing first piercing of electroslag-refining ingots or billets with diameter 460-600 mm in piercing mill at elongation degree 1.2 -1.4 and at revolution number of rolling rolls 15 -25 rev/min; realizing second and next (if necessary) piercing or expanding processes at diameter fit no more than 5.0%, elongation degree 1.4 -1,75 and revolution number of rolls 25 - 50 rev/min; seasoning cold sleeves after their first piercing with diameter 460-600 mm at relation D/S = 3.0 -4.5 on grates at temperature 400-500°C for 50 - 70 min depending upon sleeve diameter and wall thickness; heating sleeves until yielding temperature 1100 - 1260°C at rate 1.6 - 1.8°C/min depending upon kind of steel; uniformly heating sleeves with temperature 600 - 800 C after piercing mill until yielding temperature 1100 - 1260°C at rate 1.7 - 2.0°C/min; before discharging sleeves out of furnace keeping them for 45 -60 min at plasticity temperature while tilting sleeves in 10-15 min by angle 180є. Process of piercing sleeves that begins from gripping ingots or billets until their complete fitting onto mandrel is realized at decreased revolution number of rolling rolls from 25 until 15 rev/min. Stable piercing process is performed is realized at 15 -20 rev/min. At outlet of sleeve revolution number of rolls is increased up to 35 -40 rev/min. Piercing (expanding) process beginning from gripping sleeve until complete fitting of it onto mandrel is realized at decreased revolution number of rolling rolls from 50 until 20 rev/min. Stable expanding process is realized 20-25 rev/min. At outlet of sleeve revolution number of rolls is increased up to 45 - 50. Tubes are rolled in pilger mill at elongation degree μ = 3.0 - 5.0. Invention provides possibility for making high quality hot deformed tubes of large and mean diameters from corrosion resistant hard-to-form steels and alloys in tube rolling aggregates with pilger mills.
EFFECT: reduced metal consumption factor at conversion of electroslag-refining ingot to hot rolled tube, lowered cost of tubes.
5 cl, 1 tbl
FIELD: drive systems of cold rolling pilger mills.
SUBSTANCE: drive system includes rolling stand that may perform reciprocation motion; at least one crank and connecting rod mechanism operated by means of drive unit and having crank arm with balancing weight at least for partially balancing inertia forces created by rolling stand; connecting rod jointly connecting rolling stand and crank arm; at least one arranged eccentrically and driven to rotation counter-balance for balancing inertia forces and (or) moments of inertia. Motion of crank and connecting rod mechanism and counter-balance is synchronized by means of gearing. At least one crank and connecting rod mechanism is provided with single counter-balance. Motion plane of balancing weight of crank and connecting rod mechanism driven to rotation coincides with motion plane of counter-balance driven to rotation. Crank and connecting rod mechanism, counter-balance and drive unit are mutually joined through gearing. Drive unit through said gearing drives shaft joined with counter-balance. Mounted on shaft pinion of said gearing through other gearing drives shaft joined with crank and connecting rod mechanism. Balancing weight or counter-balance is in the form of eccentrically arranged mass of one gear wheel of gearing.
EFFECT: lowered cost for maintaining simplified -design rolling mill, reduced investment cost.
11 cl, 10 dwg
FIELD: drive systems of rolling mills, namely of pilger cold rolling mill.
SUBSTANCE: drive system includes at least one rolling stand mounted with possibility of reciprocation motion; at least one crank and connecting rod mechanism having crank arm with balancing weight at least for partially compensating inertia forces of rolling stand; drive unit and connecting rod jointly connecting rolling stand and crank arm; at least one counter-balance mounted with possibility of eccentric rotation in order to compensate inertia forces and (or) moments of inertia. In order to provide effective compensation of inertia forces in simplified drive system, at least one counter-balance is mounted with possibility of driving it to rotation by means of autonomous drive unit isolated from drive unit of crank and connecting rod mechanism. Said autonomous drive unit of counter-balance acts in rotation direction opposite to rotation direction of crank arm. Mass values of mass of rolling stand, balancing weight, counter-balance are selected in such a way that to compensate as possible first-order components of inertia forces of rolling stand at operation of drive system. System is provided with unit for controlling or regulating autonomous drive unit depending upon angle ϕ6 and (or) revolution number of crank arm. Rotation center of counter-balance is selected in such a way that including inertia forces of rolling stand and (or) balancing weight moments of inertia of all masses of drive system are at least significantly compensated.
EFFECT: enhanced efficiency, simplified design of rolling mill.
13 cl, 1 dwg
FIELD: production of conversion tubes of low-ductility steel with boron content 1.3 - 1.8%.
SUBSTANCE: method comprises steps of drilling ingots of electroslag refining, heating them till ductility temperature, piercing in piercing mill for making sleeves; rolling sleeves in pilger mill to tube-blanks, cooling, repairing, cutting tube-blanks by two blanks, heating them up to ductility temperature, piercing-rolling in piercing mill and rolling conversion tubes in pilger mill. Ingots of electroslag refining with diameter 460 - 480 mm are drilled from their bottom end along length L = H - B, where H - height of ingot, mm; B - under-drilled part of ingot equal to 100 - 120 mm. Then ingots are soaked at temperature 450 - 500°C on grates of heating furnace without tilting for 90 - 120 min; heated till 800 - 850° C at rate 1.8 - 2.0°C/min; then heated up to ductility temperature 1050 - 1090°C at rate 2.1 - 2.2°C/min at tilting in 15 - 20 min and soaked at such temperature for 70 - 80 min at tilting by angle about 180° in 10 -15 min.
EFFECT: lowered content of waste material, improved quality of conversion tubes, reduced cost of ready product.
5 cl, 1 tbl