Mechanized tool

FIELD: mechanical engineering.

SUBSTANCE: mechanized tool comprises clutching unit and multi-speed planet transmission. The clutching unit comprises clutch member and pusher. The clutch member is connected with the transmission member which is mounted in the vicinity of the means for supplying input torque to the transmission and should be irrotational, allowing the transmission to increase the torque. The pusher is loaded for its engagement with the clutch member to prevent their mutual rotation. When the clutch member and transmission member are interconnected, transmission capable to increase the torque. When the value of the torque applied to the clutch member is sufficient to overcome friction between the pusher and clutch member, the clutch member and transmission member rotate thus preventing the transmission from increasing torque.

EFFECT: enhanced reliability.

25 cl, 38 dwg

 

The invention relates generally to mechanized tools such as rotary drills and power screwdrivers. More specifically, the present invention relates to a node of the clutch, which is actuated on the basis of torque, issued by the first stage of the multi-speed transmission.

More recently, manufacturers of mechanized tools began to introduce mechanized rotating tools with electric motors with speed control, in an attempt to provide users of such tools obtaining sufficient controls the rotational speed of the output shaft of the tool, to enable them to perform various operations without having to resort to more specialized tools. Many of the available tools include three-stage two-speed transmission, which provides a greater degree of control the rotational speeds of these instruments.

In a typical case, the known transmission devices do not have enough configuration that could provide a wide range of frequencies of rotation of the output shaft and torque, which could allow the tool to perform various operations, such as drilling holes through to the litsevoy saw large diameter, screws for panels of dry plaster or screws with a square cylinder of large diameter, and to perform high-speed drilling. Single-speed or two-speed transmission, which was commonly used in these tools typically do not have sufficient ability to lower speed to allow the use of these transmissions in different modes, because the configuration of these tools to perform high torque operations leads to a deterioration of their high-speed characteristics. In addition, rechargeable batteries, which were used in many of the first wireless rotating, mechanized tools, were not adapted for use in operations with low speed and high torque due to high energy consumption and the rate at which spent energy mechanized tool during such operations. As a result, consumers often forced to purchase two different rotating machinery tool, i.e. a tool for "standard" applications, such as drilling and fastening screws, and the tool high power, low speed, high torque output to perform more complicated operations.

With the advent of modern battery is high capacity and high voltage is made possible according to the energy needs of mechanized tools, which is used to perform operations with low speed and high torque. However, in the art there remains a need in the node clutch that can be used in a relatively large range of the lowering speed.

A typical node clutch allows the user of the tool to limit torque, issued last stage of the transmission of the instrument. In these units the clutch is typically used spring which loads two parts of the node clutch for introducing them to the contact. When torque, which gives the transmission exceeds a predetermined traction force, the bias force applied by the spring, becomes insufficient to hold the host part of the coupling in the coupled condition, and as such, one of the parts of the knot clutch is able to rotate relative to another part of the site of the clutch. Relative rotation of these two parts effectively prevents transmission of torque to the output shaft of the tool.

The use of such nodes clutch with a transmission having a relatively wide range of lower speeds, it is often impractical for the simple reason that the strength of the bias exerted by the spring does not have sufficient adjustment range to ensure proper adhesion and separation cha is the child node of the clutch in the whole range of the lowering speed. Accordingly, a relatively common practice is to supply several springs of different sizes with a knot clutch, which then requires that the user chose and installed the spring of the corresponding value for this operation. Although this approach is effective, it is, however, time consuming and difficult.

In a preferred embodiment of the present invention created a mechanized tool containing an electric motor having an output shaft; a transmission having a first portion with a first gear ratio and a second part having the output gear ratio, the first of which includes the node planetary gear set with the ring gear, a sun wheel and a node of the planetary gears, while the ring gear is not connected with the second part of the transmission, the node of the planetary gears has a planetary carrier and a set of planetary gears, the planetary carrier has a lot of pins for holding rotatably the set of planetary gears and the output sun wheel, and many the planetary gears is engaged with the sun wheel and the ring gear, the sun wheel is connected with the output shaft and receives input torque from the electric motor, the output sun wheel is the engagement with the second part and generates intermediate output torque, the second part takes the intermediate torque and creates an output torque; and a node coupling to limit the output torque of the mechanized tool, and the node coupling has an annular coupling element and the drive unit clutch, while the annular coupling element is connected with the annular gear wheel, an annular coupling element has a specified profile clutch, and the drive unit clutch has a pusher, the pusher abuts against the annular coupling element and interacts with a given profile of the coupling to prevent relative rotation between the annular coupling element and the plunger only when the intermediate value of the output torque is less than the specified maximum torque.

Preferably the annular coupling element and a ring gear formed as a single piece, and between the ring gear and the annular coupling element is absorbing the shock structure.

At least either the annular coupling element or shock absorbing structure includes a locking element for engagement with a mating locking element formed on the annular gear wheel, and the locking element is engaged with the mating locking element to prevent the Oia relative rotation between the ring gear and at least either the annular coupling element, or absorbing the shock structure.

The drive unit clutch includes a spring element to bias the plunger to the ring coupling element to prevent relative rotation between the annular coupling element and the plunger, when the intermediate value of the output torque is less than the specified maximum torque.

Machine tool further comprises a regulating mechanism for selective regulation of force applied by a spring element to the plunger.

The plunger has a spherical end portion for entering into contact with the predetermined profile of the coupling ring coupling element.

Given the profile of the coupling ring coupling element has a sinusoidal shape.

Given the profile of the coupling ring coupling element has many wedge-shaped inclined surfaces.

The plunger may be moved along an axis parallel to the longitudinal Central axis of the ring gear.

In another preferred variant created a mechanized tool containing an electric motor having an output shaft; a pinion gear that engages with the output shaft of the motor for joint rotation therewith; a three-stage, three-speed VL is netknow transmission, with the first planetary part, which is not associated with the output stage three-stage three-speed planetary transmission, and the first planetary part includes many of the planetary gears and the ring gear while the planetary gears are in mesh with the pinion and ring gear, the ring gear is not connected with any other stage three-stage three-speed planetary transmission; and node clutch for limiting the output torque of the three-step three-speed planetary transmission, the node clutch has an annular coupling element and the drive unit clutch, an annular coupling element is connected with the annular gear wheel and has a specified profile clutch, drive unit clutch has the plunger and the adjustment mechanism, the adjustment mechanism is configured to create a bias efforts of the preset value for the displacement of the pusher into contact with the annular coupling element, the plunger interacts with a given profile of the coupling ring coupling element to prevent relative rotation between the annular coupling element and the follower when the output torque of the first planetary part is less than the specified maximum torque.

In another embodiment, a machine tool includes a housing; a motor located in the housing; an output spindle; a transmission having a transmission sleeve first part and the second part, and the transmission sleeve includes a Central channel, which at least partially located first and second parts of the transmission, and the first part of the drive train connected to the motor and receives from it the input torque, the second part of the transmission is connected with the output spindle, the first part of the drive train has at least one notch in at least one stage includes a first stage with the annular gear wheel, the ring gear is not connected with any other part of the transmission, the first part of the powertrain generates intermediate output torque of the second part of the transmission, the second part of the powertrain adopts an intermediate torque and creates an output torque is continuously transmitted to the output spindle; and a node coupling connected to the transmission, the node contains an annular clutch element of the clutch and the drive unit clutch, while the annular coupling element is connected with the annular gear wheel and has a specified profile of the clutch, the drive unit clutch has a plunger located in the shell of the transmission and is arausiaca in the annular coupling element, moreover, the plunger interacts with a given profile of the coupling ring coupling element to prevent relative rotation between the annular coupling element and the plunger only when the value of the intermediate torque is less than the specified maximum torque.

In another one embodiment, the machine tool includes a motor; an output spindle; a transmission having a first part and a second part, the second part of the transmission is connected with the output spindle, the first part has at least one notch, at least one stage includes a node of the planetary transmission with multiple gears, including a ring gear, and the ring gear is not connected with the second part of the transmission, the first part connected to the motor and receives from it the input torque, while the first part generates intermediate output torque of the second part of the transmission, the second part transmission takes intermediate torque and creates an output torque is continuously transmitted to the output spindle; and a node coupling connected to the transmission, the node contains an annular clutch element of the clutch and the drive unit clutch, while the annular coupling element is connected with the ring subca the first wheel and has a specified profile clutch, the drive unit clutch has a plunger, rests in the annular coupling element and the plunger interacts with a given profile of the coupling ring coupling element to prevent relative rotation between the annular coupling element and the plunger only when the value of the intermediate torque is less than the specified maximum torque.

An annular coupling element and a ring gear formed as a single part. And between the ring gear and the annular coupling element is absorbing the shock structure.

At least either the annular coupling element or shock absorbing structure includes a locking element for engagement with a mating locking element formed on the annular gear wheel, and the locking element is engaged with the mating locking element to prevent relative rotation between the ring gear and at least either the annular coupling element, or absorbing the shock structure.

The drive unit clutch includes a spring element to bias the plunger to the ring coupling element to prevent relative rotation between the annular coupling element and the plunger, when the value of the intermediate output is underwater torque is less than the specified maximum torque.

Machine tool according to the invention further comprises a regulating mechanism for selective regulation of force applied by a spring element to the plunger.

The plunger has a spherical end section for entering into contact with the predetermined profile of the coupling ring coupling element.

The plunger has a length which exceeds the radius determines the size of the spherical terminal section.

However given the profile of the coupling ring coupling element has a sinusoidal shape.

Moreover, given the profile of the coupling ring coupling element has many wedge-shaped inclined surfaces.

The plunger may be moved along an axis parallel to the longitudinal Central axis of the ring gear.

Preferably the first part of the transmission is a two-stage planetary gear. The ring gear is connected with the first stage of two-stage planetary gear set.

Additional advantages and features of the present invention will be understood when reading the following description and the appended claims data in conjunction with the accompanying drawings, in which:

figure 1 depicts a side view of a mechanized tool, constructed in accordance with the present invention;

figure 2 depicts a perspective view of the spatial separation of the parts part of the machine tool shown in figure 1;

figure 3 depicts a perspective view of the chassis of the mechanized tool of figure 1, showing the back side of the node of the end cap;

figure 4 depicts a front view of the node of the end cap;

figure 5 depicts a sectional view made along line 5-5 in figure 4;

6 depicts a rear view of part of the machine tool of figure 1 with the remote host end caps;

7 depicts a side view of part of the machine tool of figure 1 with the remote host end caps;

Fig depicts a view similar to that shown in figure 4, but illustrating the housing of the end cap to perform additional operations of molding;

Fig.9 depicts a view similar to that shown in figure 5, but illustrating the housing of the end cap to perform additional operations of molding;

figure 10 depicts a view similar to that shown in figure 4, but illustrating an alternative design is additionally molded element;

11 depicts a view in partial cross-section of part of a mechanized tool that utilizes the node of the end cap with optional molded element having the construction shown in figure 10;

Fig depicts a perspective is wny view from the spatially separated parts parts mechanized tools, shown in figure 1, illustrating the transmission node in more detail;

Fig depicts a perspective view of the spatial separation of the parts part of the mechanized tool of figure 1 illustrating the unit step-down gears, the transmission sleeve, the part of the body and part of the clutch mechanism in more detail;

figa depicts a sectional view made along the longitudinal axis of the second ring gear;

fig.13b depicts a sectional view made along the longitudinal axis of the third ring gear;

Fig depicts a side view of the sleeve of the transmission;

Fig depicts a rear view of the sleeve of the transmission;

Fig depicts a sectional view made along line 16-16 on Fig;

Fig depicts a sectional view made along line 17-17 on Fig;

Fig depicts the view from the spatially separated parts of the unit step-down gears;

Fig depicts a sectional view made along the longitudinal axis of the machine tool shown in figure 1, illustrating a portion of the block lower gears more detail;

Fig depicts a front view of the first reduction carrier;

Fig depicts a sectional view made along the longitudinal axis of the machine tool of figure 1 illustrating part of the unit step-down gear transmission is in more detail;

Fig depicts a rear view of part of the third reduction carrier;

Fig depicts a sectional view made along the longitudinal axis of the machine tool of figure 1 illustrating the transmission node set for the first gear ratio;

Fig depicts a sectional view similar to that shown in Fig, but illustrating the transmission node set for the second gear ratio;

Fig depicts a sectional view similar to that shown in Fig, but illustrating the transmission node set for the third gear ratio;

Fig depicts a top view of part of the machine tool of figure 1 illustrating the derailleur in more detail;

figa depicts a side view of the rotary Cam switch;

fig.27b depicts a top view of the rotary Cam switch;

figs depicts a sectional view made along the Central axis of the derailleur;

Fig depicts a rear view of the node of the output spindle;

Fig depicts a perspective view of the spatial separation of the parts of the mechanism of coupling;

figa depicts a perspective view of part of the clutch mechanism, illustrating another configuration of the coupling element;

fig.29b depicts the prospects of the first type with a spatial separation of the parts, illustrating the multi-element structure of the first ring gear and the coupling element;

Fig depicts a schematic illustration of the adjustment patterns in the "expanded" state;

Fig depicts a schematic illustration similar to that shown in Fig, but showing an alternative construction adjusting profile; and

Fig depicts a schematic illustration similar to that shown in Fig, but showing a portion of another alternative construction of the regulating profile.

Figures 1 and 2 mechanized tool, having a structure according to the invention, indicated generally by the reference number 10. As will be clear to experts in the art, the preferred embodiment of the present invention can be any device with an electric wire or wireless (battery powered) device such as a portable mechanized screwdriver or drill. In the specific embodiment of the invention of the mechanized tool 10 is a cordless drill with case 12, the node 14 of the motor, multi-speed transmission node 16, the mechanism of the clutch 18, the node 20 of the output shaft, jaw Chuck 22, the actuator unit 24 and a battery pack 26 power. Specialists in the art Boo is no clear several components of the machine tool 10, such as jaw Chuck 22, the trigger 24 and a battery pack 26 power, are in fact well-known components and do not require description in significant detail in this application.

For a more complete understanding of the known components mechanized tools 10, you can refer to a variety of publications. One example of such publications is jointly assigned U.S. patent No. 5897454, issued April 27, 1999.

The housing 12 includes the node 30 of the end cap and the node 32 of the housing arm, which includes a pair of mating halves of the housing 34 of the handle. Node 32 of the housing of the handle includes an engaged part 36 and part 38 for placement drive or Cabinet part. The actuator unit 24 and a battery pack 26 power mechanically connected with the capture part 36 and electrically connected to the node 14 of the electric motor. Body part 38 includes a recess 40 to accommodate the motor and the notch 42 to accommodate the transmission. The node 14 of the electric motor is located in the recess 40 to accommodate the motor and includes a rotary output shaft 44, which is held in the recess 42 to accommodate the transmission. Leading gear 46 of the electric motor, having a set of teeth 48, is connected with the output shaft 44 DL the joint rotation therewith. The trigger 24 and a battery pack 26 power interact to selectively supply electric power to the node 14 of the motor in a known manner to control the speed and direction, which rotates the output shaft 44.

The transmission node 16 is located in the recess 42 to accommodate the transmission and includes a mechanism 60 of the gearshift. Leading gear motor 46 connects the transmission node 16 with the output shaft 44, transmitting the transmission node 16 a relatively high speed and low torque. The transmission node 16 includes many step-down elements which selectively engages the mechanism 60 gear to get the gear ratios. Each of the gear ratios converts speed and torque supplied drive force given way, allowing you to change the speed and torque output transmission unit 16, as needed, from the relatively low output speed and high output torque to a relatively high output speed and low output torque. Output force transmission is transmitted to the output node 20 of the spindle, which is connected to jaw Chuck 22 for sovmestnog the rotation and transfer torque insertable cutting tool (not shown). The clutch mechanism 18 is connected to the transmission node 16 and is designed to limit the torque associated with a driving force elected to the specified torque limit.

Figure 2-9 shows the node 30 of the end cap comprising a body 100 of the end cap and additionally molded element 102. In the shown example, the housing 100 of the end cap is made by injection molding of a plastic material such as ABS (Acrylonitrile-butadienestyrene). The housing 100 of the end cap forms a recess 104 of the end cap, which has a size adapted to receive part of the node 14 of the electric motor, which steps back from node 32 of the housing arm. On the front surface 114 of the housing 100 of the end cap formed many first and second radial notches 108 and 110 for ledges and hard surface 128, and around the perimeter of the housing 100 end caps made many tides 116 for screws. Each of the first and second radial notches 108 and 110 for the protrusions has a size adapted for receiving one of the first radial protrusions 120 and second radial protrusions 122, respectively, which are formed on the back surface 124 of the halves 34 of the housing arm. First and second radial openings 108 and 110 for protrusions interact with the first and second radial protrusions 120 and 122 DL the proper alignment of the body 100 of the end cap relative to the node 32 of the housing arm, and to prevent relative rotation between them. Arcuate portion 128 of the front surface 114 of the housing 100 of the end cap aligned with the thrust surface 132 on the rear surface 124 of the halves of the arm 34 and mates with her. Tides 116 screw still allow you to attach the case 100 of the end cap to the housing 136 of the motor by means of a set screw 138. The geometry of the casing 136 of the motor is such that it is tightly attached to the inside halves of the housing 34 of the handle. As such, the attachment of the housing 100 of the end cap to the housing 136 of the motor provides a rigid holding the housing 100 of the end cap relative to the back surface 124 of the node 32 of the housing of the handle and closing the recesses 139 in the node 32 of the housing of the handle.

In the side surfaces of the body 100 of the end cap formed many lateral slots 140 to ensure the passage of air flow through the node 32 of the housing arm and cooling node 14 of the electric motor are well known manner. In the rear surface of the housing 100 of the end cap formed many rear of the slots 144, each of the rear slots 144 includes a deep portion 146, which partially takes place in the direction of the outer surface 148 of the housing 100 of the end cap, and through the part 150, which passes completely through the chassis 100 that is zeway cover. A pair of retaining lobes 152 formed so that they pass from the inner surface 154 of the housing 100 of the end cap inside, in the recess 104 of the end cap. In the inner surface 154 of the housing 100 of the end cap shaped channel 156, crossing each of the rear slots 144 and holding the petals 152.

Of elastic material such as thermoplastic elastomer (e.g., HYTREL®, manufactured by E.I. du Pont de Nemours and Company), formed additionally molded element 102, which simultaneously form and connect with the body 100 of the end cap during the operation of molding. In the specific example additionally molded element 102 includes multiple buffer elements 170, a pair of insulators 172 and the connecting member 174. Each of the buffer elements 170 passes from a point approximately coincident with the inner surface 154 of the housing 100 of the end cap, to the point, receding back from the outer surface 148 of the housing 100 end cover approximately a distance of from about 0.5 mm to about 1.5 mm, and preferably about 0.75 mm This design allows the buffer elements 170 to provide a degree of shock absorption, which reduces the chance of damage to the body 100 of the end cap in case of falling of the tool 10. In addition, sometimes the operator is necessary is to exert a relatively large force to the tool 10, for example, when using circular saws for drilling holes of large diameter. In such situations, the operator tends to press on the back side of the tool 10 for application of force along the line of the axis of the Chuck 22. In such situations, the buffer elements 170 form for the operator relatively soft and comfortable surface that provides slip resistance and also reduces vibration transmitted to the operator.

Around holding petals 152 are formed insulators 172 located on the inner surface 154 of the housing 100 of the end cap. In the above example, each of the insulators 172 includes an annular element 180, protruding from the inner surface 154 of the housing 100 of the end cap. This design allows you to enter insulators 172 of the housing 100 of the end cap in contact with the outer perimeter 14a and the rear surface 14b of the casing 14C motor for fixed retention of the motor 14d inside the casing 136 of the motor. This prevents the moving components of the node 14 of the motor along the longitudinal axis of the tool 10, and also contributes to the damping of the vibrations generated during the operation of the node 14 of the electric motor. The connecting member 174 still connected with each of the buffer elements 170 and insulators 172. The connecting member 174 forms a channel through which panel the guy the material flows during the molding buffer elements 170 and insulators 172, thus making them difficult to extract from the case 100 of the end cap.

The person skilled in the art it will be clear that this aspect of the present invention can be incorporated into various other points of the node 32 of the handle to create a seal between two or more components, vibration damping or positioning of one component relative to another. One such example is shown in figure 10 and 11, where the isolators 172 modified so that they pass through the perimeter portion of the recess 104 of the cover and are in sealing contact with the rear surface 14b of the motor 14d. Insulators 172 seal off the border between the body 100 of the end cap and the node 14 of the electric motor, whereas the buffer elements 170 clog the rear of the slot 144 in the housing 100 of the end cap. The space 188, limited insulators 172, fill grease grease or other lubricant that lubricates the bearing 190 of the rotor of the electric motor.

On Fig shows the transmission node 16, which is a three-stage, three-speed transmission, comprising a sleeve 200 transmission unit 202 of step-down gears and mechanism 60 of the gearshift. As additionally shown in Fig-17, sleeve 200 powertrain includes wall 210, which limits the channel for the transmission or cavity 212 in which is located a block 202 lowering subc what's transmission. The sleeve 200 of the transmission includes a housing 214 and the base 216. The housing 214 of the sleeve 200 transmission has a fairly uniform diameter, which is smaller than the diameter of the base 216. The inner diameter of the base 216 is adapted to receive a cylindrical front portion 220 of the housing 136 of the motor.

On the basis of 216 formed many speakers pads 226. The exposed pad 226 restrict the set of first grooves 228 in the outer surface 230 of the base 216 and the multiple second grooves 232 in the inner surface 234 of the base 216. The first grooves 228 are made so that they took the centering ribs 238 formed on the inner surfaces 242 halves 34 of the handle to align the cartridge 200 of the transmission relative to the halves 34 of the handle and prevent relative rotation between the sleeve 200 of the transmission and the housing 12. Preferably, the first groove 228 and the centering ribs 238 is designed in such a way that the sleeve 200 of the transmission can be installed in half 34 of the handle with only one orientation (i.e., the configuration of the first grooves 228 and centering ribs 238 prevents rotation of the sleeve 200 transmission 180° required provisions concerning halves 34 arm). The second groove 232 will be described in more detail below.

The housing 214 of the sleeve 200 powertrain includes a cylindrical part 24 of the casing and part 248 to place the truss element. In the specific embodiment of the invention, the cylindrical portion 246 of the housing includes guide 250 copier switch, multiple grooves 252 for lubrication and the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel, respectively. Guide 250 copier switch has a generally rectangular cross-section and protrudes outward from the upper part of the outer surface 258 hull 246. Groove 252 for lubrication formed concentrically around the first half of the perimeter of the hull 246. Groove 252 for lubrication have a depth, comprising from about 0.01 inch to about 0,030 inch for holding lubricant, such as grease lubricant on the upper half of the perimeter of the hull 246. Work guide 250 copier switch and grooves 252 for lubrication will be described in more detail below.

The protruding flange 264 divides the inner space of the case portion 246 of the first and second parts 260 and 262, respectively. The first set of teeth 254 for engagement with the annular gear wheel formed on the inner surface 266 hull 246 and steps back from the speaker flange 264 towards the base 216. The second set of teeth 256 for engagement with the annular gear wheel formed on the inner surface of Cabinet frequent the 246, but recedes ahead of the speaker flange 264. Teeth 268 of the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel are evenly distributed on the inner surface 266 hull 246. The configuration of each prong 268 in the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel such that each tooth moves away from the speaker flange 264 has a pair of parallel contact surfaces 270 and ends the terminal part 272. Terminal part 272 of each prong 268 rounded and narrowed to facilitate entry into engagement with a part of the block 202 step-down gear, which will be described in detail below.

Part 248 to place the truss element recedes down from hull 246 for a substantial part of the length of the hull 246. In part 248 to place a core element formed hole 274 to drive, passing back through the base 216 of the sleeve 200 of the transmission. In the specific embodiment of the invention the hole 274 of the actuator has a ledge separating the first portion 276 of the first diameter in the rear part of the liner 200 of the transmission and the second part 278 smaller second diameter at the front of the liner 200 transmission. In the shown example, the first part of the 276 hole 274 of the actuator passes through the first wall is part 260 of the housing and forms a groove 280 in the inner surface 234 of the base 216. Part 248 to place the truss element will be described in more detail below.

In the sleeve 200 of the transmission formed by the first pair of grooves 284 to the bracket, and a second pair of grooves 286 for staples along the sides of the liner 200 of the transmission so that they are parallel to the longitudinal axis of the sleeve 200 of the transmission. The first pair of grooves 284 for staples are formed so that they pass through the sides of the hull 246 rear of the speaker flange 264 and go back towards the base 216. The depth of the first pair of grooves 284 for staples is that they do not pass through the portion 210 of the wall forming the base 216. The second pair of grooves 286 bracket is also formed so that they pass through the sides of the hull 246, continuing forward from the speaker flange 264, and pass through the front surface 288 of the liner 200 of the transmission.

As shown in Fig, 13, 18 and 23, block 202 lower gears includes a first step-down node 302 gears, the second step-down node 304 gears and the third step-down node 306 gears. First, second and third reduction nodes 302, 304 and 306 gears operate in an active mode and passive mode. When operating in the active mode step-down node gears performs the operation of reducing speed and increasing torque, while working the e step-down node gears in passive mode step-down node gears gives the output speed and torque, which is approximately equal to the rotational speed and torque of rotational motion, the reported downward node gears. In the specific embodiment of the invention each of the first, second and third lower nodes 302, 304 and 306 gears is a planetary gear. However, specialists in the art it will be clear that instead of one or more lower nodes gears forming unit 202 lower gears, can be applied to various other types of lower nodes gears known in this field.

As shown, the first step-down node 302 gears includes a first reduction element or ring gear 310, the first set 312 of the planetary gears and the first downward drove 314. The first ring gear 310 is an annular structure having a set of teeth 310a formed at the level of its internal diameter. On the outer perimeter of the front surface 318 of the first ring gear 310 formed surface 316 of the clutch, which will be described in more detail below. The first ring gear 310 is located inside the hollow part of the recess 212 formed in the base 216; the front surface 318 of the first ring gear 310 is in contact with the ledge 320, strmilov is authorized in the sleeve 200 of the transmission, thus limiting the ability of the first ring gear 310 to move forward in a hollow recess 212.

The first downward drove 314 formed in the form of a flat cylinder having many pins 322 protruding from its back surface 324. Almost at the outer perimeter of the first reduction carrier 314 formed many teeth 314a with depression 314b formed between each two adjacent teeth 314a. By staggering the teeth 314a one of the depressions (i.e. depression 314b') relatively more than other depressions 314b by eliminating teeth 314a on the outer perimeter of the first reduction carrier 314. In the specific embodiment of the invention the teeth 314a of the first reduction carrier 314 is made of such configuration that they do not come into direct engagement with the teeth 310a of the first ring gear 310.

On Fig and 20 depicts the profile of the teeth 314a. As shown, each prong ends 314a with radius 326 on the front surface 328 of the first reduction carrier 314, but is dropped vertically on the back surface 324 of the first reduction carrier 314. Radius 330 is also formed in the hollows 314b between teeth 314a.

Returning to Fig, 13, 15, 18 and 23, we note that behind the first down-node 302 gears is thrust washer 32, having a first annular portion 334, the second annular portion 336 and a lot of restraint petals 338. Holding the petals 338 engages with the second groove 232 in the base 216 of the sleeve 200 of the transmission, and, as such, prevents relative rotation between the first thrust washer 332 and sleeve 200 transmission. The inner diameter of the base 216 is adapted to receive casing 136 of the motor, and, in fact, the front surface 340 of the housing 136 of the motor prevents axial movement of the first thrust washer 332. The first annular portion 334 is in contact with the rear surface 342 of the first ring gear 310, forming surface wear and tool control values on which the first ring gear 310 is capable of moving in the axial direction. The second annular portion 336 attributed in the axial direction from the first annular portion 334, stepping forward from the first annular portion 334 for the formation of surface wear to the first set 312 of the planetary gears, which also forms a means of controlling the magnitude to which they can move in the axial direction.

The first set 312 of the planetary gears includes many planetary gears 344, each of which has an essentially cylindrical configuration and has a lot of teeth 44a, formed on its outer perimeter, and a hole 346 for pin formed in its center. Each planetary gear 344 rotatably retained on a respective one of the pins 322 and the first Panigale driver 314 and is located so that its teeth a are in direct engagement with the teeth 310a of the first ring gear 310. On the front and back surfaces 350 and 352 of each of the planetary gears 344 formed protruding surface 348, which prevents friction of the teeth a on the first downward drove 314 and the first thrust washer 332 and the formation of dust or sawdust, which could impair the characteristics of the transmission node 16 and reduce its service life. Because the teeth 46a pinion 46 of the motor shaft 44 also engages with the teeth a planetary gears 344, leading gear 46 serves as a sun wheel for the first down-node 302 gears.

The second step-down node 304 gears located inside the hollow part of the recess 212 formed in the first Cabinet part 260, and includes a second sun wheel 358, the second reduction element or ring gear 360, the second node of the planetary gears 362 and the second downward drove 364. The second sun wheel 358 fixedly mounted for rotation together keep lowering planet carrier 314. The second sun wheel 358 includes many teeth a that protrude forward from the front surface 328 of the first reduction carrier 314.

The second ring gear 360 is an annular structure having a set of teeth 360 ° formed on its inner diameter. Teeth 360 ° can be strongly oblique rear surface 366 of the second ring gear 360, but dropped vertically on the front surface 368. More preferably, there was formed a large radius 369 curves on the back surface 366 and the sides of each prong 360°, with a radius 369 rounding is applied is preferable to a strong slant, because a large radius 369 rounded teeth 360 ° provides better engagement between the second ring gear 360 and the first step-down planet carrier 314.

On the outer periphery of the second ring gear 360 formed many teeth 370 for engagement with the sleeve; the teeth 370 for engagement with the sleeve and pass forward to the front surface 368 of the second ring gear 360 and the pointed end part 372, which is rounded and tapering forward and inward. On the outer perimeter of the second ring gear 360 is also formed annular groove 374 for staples. In the example shown, the groove 374 to the bracket submitted is a groove of rectangular cross-section, having a pair of side walls 376. Groove 374 for the bracket will be described in more detail below.

The second downward drove 364 formed in the form of a flat cylinder having many pins 378, which depart from its back surface 380. The second node of the planetary gears 362 includes many planetary gears 382. Each planetary gear 382 has an essentially cylindrical configuration with many teeth a formed on its outer perimeter, and with a hole 384 for pin formed in its center. Each planetary wheel 382 is rotatably retained on a respective one of the pins 378, and the second downward drove 364 are set so that the teeth a planetary gears 382 engages with the teeth 360 ° of the second ring gear 360. Teeth a second sun gear 358 also engages with the teeth a planetary gears 382.

Third step-down node 306 gears located inside the hollow part of the recess 212 formed within the second Cabinet part 262, and includes a third sun wheel 398, the third step-down element or ring gear 400 and the third set of planetary gears 402, and the third down led 404. The third sun wheel 398 fixed to the second downward cage 364 the La rotation with him. The third sun wheel 398 includes many teeth a passing forward from the front surface 406 of the second reduction carrier 364.

The third ring gear 400 is an annular structure having a set of teeth 400A formed on its inner diameter. Teeth 400A can be strongly oblique to the front surface 412 of the third ring gear 400, but dropped vertically on the back surface 414. It is more preferable to form a large radius 407 bend on the front surface 412 and the sides of each of the teeth 400A to use a large radius 407 bend and not strong bevel, because a large radius 407 bending the prong 400A provides better engagement between the third ring gear 400 and the third step-down planet carrier 404. On the outer perimeter of the third ring gear 400 formed many teeth 418 for engagement with the sleeve; teeth 418 for engagement with the sleeve and pass back toward the back surface 414 of the third ring gear 400 and the terminal end part 420, which is rounded and tapering in the direction of the back and inside. On the outer perimeter of the third ring gear 400 is formed annular groove 422 for staples. In the example shown, the groove 422 to the bracket is a rectangular groove széchenyi is, having a pair of side walls 424. Groove 422 for the bracket will be described in more detail below.

Third down led 404 is formed in the form of a flat cylinder having many pins 428, protruding from the back surface 430. Almost the entire outer perimeter of the third reduction carrier 404 formed many teeth a, and between each two adjacent teeth a formed trench 404b. Due to the spacing of the teeth a one of the depressions 404b (i.e. trench 404b') relatively more than other depressions 404b by eliminating tooth a on the outer perimeter of the third reduction carrier 404. In the specific embodiment of the invention the teeth a of the third reduction carrier 404 is designed in such a way that they are not in direct engagement with the teeth a second planetary gears 382.

On Fig and 22 shown in more detail the profile of the tooth a. As shown, the rear surface 430 of the third reduction carrier 404 beveled, and on each side of the teeth a and troughs 404b formed rounding 434 large radius. Each prong a dropped vertically on the front surface 436 of the third reduction carrier 404.

Returning again to Fig, 13, 15, 18 and 23, we note that the third set 402 planetary gears includes many planetary gears 438. Each planet is Noah gear 438 is, essentially cylindrical configuration with many teeth a formed on its outer perimeter, and a hole 440 to pin formed in its center. Each planetary gear 438 rotatably mounted on a respective one of the pins 428, and the third down led 404 is set so that the teeth a planetary gears 438 directly engages with the teeth 400 of the third ring gear 400. On each of the front and rear surfaces of the planetary gears 438 formed protruding portion 442, which prevents friction of the teeth a on third down led 404 and the formation of dust or sawdust, which could impair the characteristics of the transmission node 12 and reduce its service life. Around the third sun gear 398 is a second thrust washer 450, and teeth a third sun gear 398 engages with the teeth a planetary gears 438. A second thrust washer 450 includes many holding petals 452, which are made with this configuration, so that they come into engagement with the corresponding grooves 454 for the petals (Fig)formed in the inner surface 266 of Cabinet portion 246 of the sleeve 200 of the transmission. Holding the petals 452 and grooves 454 for the petals to interact before the brasenia relative rotation between the second thrust washer sleeve 450 and 200 transmission.

The node 20 of the output shaft includes gear means 458 to connect the spindle 460 with the third step-down planet carrier 404 for joint rotation so as to transfer drive torque from block 202 lower gears push the cartridge 22. Such transmission facilities 458 is well known and can easily be adapted to the unit step-down gears corresponding to the present invention. Accordingly, there is no need to include a detailed description of the transmission facilities 458.

As shown in Fig, 13A, 13b, 16, 17, 18, and 23 to 28, the mechanism 60 of the gear shift can be moved between the first position 500, the second position 502 and the third position 504 and includes a switching portion 510, receiving the force for switching speed, and the drive part 512 for manipulating unit 202 lower gears in accordance with the switching speed. Driving portion 512 in the working position connected with block 202 step-down gears and moves the second and third reduction nodes 304 and 306 gears between active and passive modes in the movement of the switching part 510 between the first, second and third positions 500, 502 and 504. In the specific embodiment of the invention, the driving portion 512 includes a rotating pen is kiuchumi copier 520, many wire clips 522 and the spring element 523. Each of the wire clip 522 formed from a wire of circular cross section which is bent in the form of a semicircle 524 with a pair of pads 526, protruding outward from the semicircle 524 and located approximately in the median plane of the semicircle 524. The semicircle 524 has a size, which is designed to fit in the groove 374 and 422 for brackets in the second and third ring gears 360 and 400, respectively. In this respect, the semicircle 524 is not acting radially outward from the corresponding one of the ring gears (360, 400) and not tamamlama side walls (376, 424) of the grooves (374, 422). In the example, the side walls (376, 424) of the grooves (374, 422) for staples assigned from each other by approximately 0.05 inches, and the diameter of the wire from which the formed wire clips 522 is approximately 0.04 in.

The tabs 526 of the wire clips 522 protrude outwards from the hollow recess 212 in the corresponding slots (284, 286) bracket, formed in the sleeve 200 of the transmission. The tabs 526 have sufficient length to pass outward from the outer surface 258 of the housing 214 of the sleeve 200 of the transmission, but not so much that they acted radially outward from a portion of the first grooves 284 to the bracket at the base 216 of the sleeve 200 of the transmission. Run the wire clips 522 of this form facilitates the Assembly unit 16 step-down gear is aradac, allowing the wire clips 522 on the second and third ring gears 360 and 400, then these nodes are inserted into the hollow recess 212 along the longitudinal axis of the sleeve 200 of the transmission.

On Fig and 27A-27C shows the rotating Cam 520 switch, containing the arched frame 530 switch, key switch 532 and many spacers 534. In case switch 530 is formed a pair of first curved grooves a and 540b, a pair of second curved grooves a and 544b, cut 546 for the spring and the guide notch 548. Case 530 switch has a size adapted to cover the outer diameter of Cabinet portion 246 of the sleeve 200 of the transmission with a sliding fit. The guide notch 548 has an essentially rectangular shape and dimensions adapted to enter into contact with the front and rear surfaces of the guide 250 copier switch. The width of the guide notch 548 substantially greater than the width of the guide 250 copier switch and has a size that allows you to rotate the rotating Cam 520 switch core 200 transmission between the first rotational position, the second rotational position and the third rotational position. Guide 250 copier switch interacts with the guide notch 548 to limit the range in which the rotating Cam 520 p the selector can be rotated on the sleeve 200 of the transmission, the first lateral side of the guide 250 copier switch comes in contact with the first side of the guide notch 548, when the rotating Cam 520 is in the first rotational position and a second lateral side of the guide 250 copier switch comes in contact with the second side of the guide notch 548, when the rotating Cam 520 switch is in the third rotational position.

Each of the first curved grooves a and 540b has dimensions adapted for receiving one of the tabs 526 of the wire clips 522 that is engaged with the second ring gear 360. In the specific embodiment of the invention, the first curved groove a includes the first segment 550, the second segment 552 and the intermediate segment 554. The first segment 550 is located at the first predetermined distance from the plane 558 reference, which is perpendicular to the longitudinal axis of the rotating Cam 520 switch, and the second segment 552 is located at the second distance from the plane 558 reference. The intermediate segment 554 connects the first and second segments 550 and 552 each other. The configuration of the first curved groove 540b is identical to the configuration of the first curved groove a, except that it is rotated relative to the rotating Cam 520 switch thus is m, each of the first, second and intermediate segments 550, 552 and 554 of the first curved groove 540b is oriented with a 180° relative to the first, second and intermediate segments 550, 552 and 554 of the first curved groove a.

Each of the second curved grooves a and 544b has dimensions adapted for receiving one of the tabs 526 of the corresponding one of the wire clips 522. In the specific embodiment of the invention the second curved groove a includes the first segment 560, the second segment 562, the third segment 564 and a pair of intermediate segments 566 and 568. The first and third segments 560 and 564 are located on the third specified distance from the reference plane, and the second segment 562 is located at a fourth distance from the plane 558 reference. The intermediate segment a connects the first and second segments 560 and 562 each other, and the intermediate segment 568 connects the second and third segments 562 and 564 with each other.

The configuration of the second curved groove 544b is identical to the configuration of the second curved groove a, except that it is rotated relative to the rotating Cam 520 switch so that each of the first, second, third and intermediate segments 560, 562, 564 and 566 and 568 of the second curved groove 544b rotated 180° relative to the first, second, third, and prom is mediate segments 560, 562, 564 and 566 and 568 of the second curved groove a.

When the tabs 526 of the wire clips 522 engages with the first curvilinear grooves a and 540b and second curved slots a and 544b, the rotating Cam 520 switch can be rotated on the sleeve 200 transmission between the first, second and third positions 500, 502 and 504 for selective introduction into engagement and separation of the second and third ring gears 360 and 400 and the first and third lower led 314 and 404, respectively. During the rotation of the rotating Cam 520 switch the first curved grooves a and 540b and second curved slots a and 544b hold the wire tabs 526 of the corresponding wire clips 522 and provide movement of the wire legs 526 along the longitudinal axis of the sleeve 200 transmission in the respective first and second grooves 284 and 286 for the brackets. Accordingly, the rotating Cam 520 switch operates to convert the rotational motion into axial linear motion, which causes the axial displacement of the wire legs 522 specified way. In the groove 252 for lubrication formed in hull 246 of sleeve 200 of the transmission, put a lubricant (not shown)used to lubricate the boundaries between the sleeve 200 of the transmission and the rotating Cam 520 switch.

Installation of the rotating Cam 520 switch in which the first rotational position 500 leads to the location of the tabs 526 of the wire clips 522, which engages with the second ring gear 360 in the first segment 550 of the first curved grooves a and 540b and the location of the tabs 526 of the wire clips 522 that is engaged with the third ring gear 400 in the first segment 560 of the second curved grooves a and 544b. Accordingly, installation of the rotating Cam 520 switch is in the first rotational position causes the occurrence of engagement of the second and third ring gears 360 and 400 with the second and third sets 362 and 402 of the planetary gears respectively. Simultaneously with entering into the engagement of the second and third ring gears 360 and 400 with the second and third sets 362 and 402 of the planetary gears teeth 370 and 418 for engagement with the sleeve of the second and third ring gears 360 and 400, respectively, are in engagement with the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel, respectively, to prevent relative rotation between the second and third ring gears 360 and 400 and sleeve 200 of the transmission to obtain, therefore, the provisions of 570 unit 16 step-down gear with the first overall reduction or ratio shown in Fig. Specialists in the art will understand that the target portion 272 of the teeth 26 of the first and second sets of teeth 254 and 256 for engagement with the annular gear wheel and the target part 372 and 420 teeth 370 and 418 for engagement with the sleeve, accordingly, rounded and narrowed to improve their ability to engage in the event of axial movement along the longitudinal axis of the block 16 step-down gears.

Installation of the rotating Cam 520 switch is in the second rotational position 502 leads to the location of the tabs 526 of the wire clips 522 that is engaged with the second ring gear 360 in the first segment 550 of the first curved grooves a and 540b and the location of the tabs 526 of the wire clips 522 that is engaged with the third ring gear 400, the second segment 562 of the second curved grooves a and 544b. Accordingly, installation of the rotating Cam 520 switch is in the second rotational position causes the occurrence engages the second ring gear 360 to the second set 362 planetary gears and to join in the engagement of the third ring gear 400 with the third set 402 of the planetary gears and the third step-down planet carrier 404. Installation of the rotating Cam 520 switch is in the second rotational position 502 also leads to the occurrence in the engagement of the teeth 370 for engagement with the sleeve and second ring gear 360 to the first set of teeth 254 for engagement with the annular gear wheel, while the teeth 418 for engagement with the sleeve t is Atego ring gear 400 is not included in engagement with the second set of teeth 256 for engagement with the annular gear wheel. Essentially, the relative rotation between the second ring gear 360 and the sleeve 200 of the transmission is prevented while relative rotation between the third ring gear 400 and sleeve 200 transmission Pets to obtain position 572 block 16 step-down gear with the second overall decline or ratio shown in Fig.

Installation of the rotating Cam 520 switch in the third rotational position 504 leads to the location of the tabs 526 of the wire clips 522 that is engaged with the second ring gear 360, in the second segment 552 of the first curved grooves a and 540b and the location of the tabs 526 of the wire clips 522 that is engaged with the third ring gear 400 in the third segment 564 second curved grooves a and 544b. Accordingly, installation of the rotating Cam 520 switch in the third rotational position causes the occurrence engages the second ring gear 360 to the second set 362 planetary gears and with the first step-down planet carrier 314, while the third ring gear 400 is engaged only with the third set 402 of the planetary gears. Installation of the rotating Cam 520 switch in the third rotational position 504 also leads to the exit geared the I teeth 370 for engagement with the sleeve and second ring gear 360 to the first set of teeth 254 for engagement with the annular gear wheel and enter the engagement of the teeth 418 for engagement with the sleeve and the third ring gears 400 with the second set of teeth 256 for engagement with the annular gear wheel to allow relative rotation between the second ring gear 360 and the sleeve 200 of the transmission and prevent mutual rotation between the third ring gear 400 and the sleeve 200 of the transmission to obtain a position 574 of block 16 step-down gear with the third overall decline or gear ratio.

In the example shown in Fig, 27b and 28, from a flat rectangular plate of spring steel formed spring element 523, having a flattened Z-shaped portion 580 and a convex portion 584. Flattened Z-shaped part 580 is made of such configuration that it was around two straps 586, which are cut 546 for the spring, thus to hold the convex part 584 in a predetermined position, and to transmit the spring force between the rotating Cam 520 switch and spring element 523. As shown in Fig, the convex portion 584 of the spring element 523 has a size adapted to enter the notches 590 formed in the housing 592 node 20 of the output shaft. Between the notches 590 is formed protruding pad 594, carried on the circumference of the rotating Cam 520 switch. When the node 20 of the output shaft is located on the lower block 16 gears, andmechanism 60 gear set to one of the rotational positions, that is, in the first, second or third position 500, 502 or 504, a convex portion 584 of the spring element 523 is included in a corresponding one of the cut-590. The force generated by the spring element 523, when the convex part 584 moves down in the direction of the rotating Cam 520 switch in the entry in the contact convex portion 584 and serving areas 594 prevents unintentional rotation mechanism 60 of the gearshift. In addition, the location of the convex part 584 in the neck 590 provides for a user perceivable indication of positioning of the rotating Cam 520 switch.

In a specific embodiment of the invention shown in Fig and 27C, the switching portion 510 includes an arcuate strip 600, having formed therein the protruding hollow button switch 602 rectangular cross-section. Arcuate strip 600 is formed of a plastic material and configured so that it covered the outer diameter of the rotating Cam 520 switch. The open end of the button switch 602 is made of such form that he took the key switch 532, thus providing a connection to each other switching part 510 and the rotating Cam 520 switch without mounting means. The rotating Cam 520 switch formed many spacer e the cops 534, which are protruding parts, concentric relative to the housing 530 switch and protruding radially outward from him. Spacers support 534 arcuate strip 600, preventing entry into the arcuate contact strip with wire legs 526 in the first curvilinear grooves a and 540b. Spacers 534 can also be used to selectively strengthen areas of the rotating Cam 520 switch, such as the areas adjacent to the first curved grooves a and 540b.

Specialists in the art will understand that the rotating Cam 520 switch (that is, the first curved grooves a and 540b and second curved slots a and 544b) may have a different configuration for securing the entry engages the second ring gear 360 with the second planetary gears 362 and the first step-down planet carrier 314, while the third ring gear 400 is engaged with the third planetary gears 402 and the third step-down planet carrier 404 to obtain the position of the block 16 step-down gear with the fourth overall decline or gear ratio.

Specialists in the art will understand that instead of shown here mechanism 60 of the switch can be applied to mechanisms other switch configuration is rd. These mechanisms of the switches may include actuators driven rotational or sliding movement, and may include traction, Cams or other devices known in the field, to ensure the sliding of the second and third ring gears relative to the sleeve 200 of the transmission. Specialists in the art will also understand that when the second and third ring gears 360 and 400 can be independently moved between active and passive modes (i.e., the location of one of the second and third ring gears 360 and 400 does not dictate the location of the other of the second and third ring gears 360 and 400), the mechanism 60 of the switch could also be performed with a configuration suitable for installation of the second and third ring gears 360 and 400 independently from each other.

On Fig, 26 and 28-30 shows the mechanism 18 of the clutch containing element 700 clutch, the drive unit 702 clutch and control mechanism 704. The coupling element 700 is shown as a circular structure, which is fixed on the outer diameter of the first ring gear 310 and which is radially outward from him. Element 700 clutch has a curved surface 316 of the clutch formed on the front surface 318 of the first ring gear 310. The value of the external diameter of the element 700 clutch allows it to rotate inside the hollow part of the recess 212, formed by the base 216 of the sleeve 200 of the transmission. As shown in Fig, the surface 316 of the clutch in the example shown is formed by a set of vertices 710 and troughs 712 located relative to each other so that they form a series of inclined surfaces at an angle, constituting approximately 18°. However, specialists in the art will understand that can also be used in other configurations of the surface of clutch, such as surface 316' clutch sinusoidal (figa).

Although the first ring gear 310 and the coupling element 700 is shown as a single structure (i.e formed unitary), the specialist in the art will understand that they can have a different design. One such variant embodiment of the invention shown in fig.29b, where the first ring gear 310 is shown as having an annular ledge 1000 and many slots 1002 for the petals.

The annular ledge 1000 is shown as having a lot of inclined surfaces 1004 with gradients in two directions, but in other places flat. The first ring gear 310' in other respects identical to the first annular gear wheel 310. To the annular ledge 1000 adjacent ring buffer element 1008, with many petals 1010, which engages with the notches 1002 for petals in what erom the annular gear wheel 310' to prevent rotation of the buffer element 1008 relative to the first ring gear 310'. The buffer element 1008 contains a sizeable portion 1012 done with this circuit is that it matches the contour of the annular ledge 1000 and has many parts of 1014, which configuration is suitable for coupling with each of the inclined surfaces 1004. The buffer element 1008 is formed of a suitable shock absorbing material, such as acetyl. Element 700' clutch, which is annular element formed of wear-resistant material such as hardened steel 8620, is located on top of the buffer element 1008. As the buffer element 1008, the element 700' clutch has many petals 1020, which are locked in the notches 1002 for the petals to prevent rotation relative to the first ring gear 310', and many of the mating parts of the 1022. The mating inclined portion 1022 element 700' clutch come into contact with the mating inclined parts 1014 buffer element 1008. Although this design is more expensive in comparison with the previously described embodiment of the invention, it better stand high shock loads associated with the operation of the clutch mechanism 18.

In the specific embodiment of the invention, the node 702 clutch contains a truss element 720, spring 722 of the pusher and the pusher 724. A truss element 720 includes cylindricus the second portion 730, having an outer diameter providing a sliding fit within the second portion 278 of the hole 274 of the actuator, formed in part 248 to pivot cartridge 200 transmission. A truss element 720 also includes a terminal portion 732 and the cylinder 734. Terminal portion 732 is made in the form, suitable for entering into contact with the regulating mechanism 704, and in the example shown is formed on the end of the hull 730 core element 720 with a spherical radius. Head 734 is connected to the end of the hull 730, the opposite terminal parts 732, and is made in the form of a flat cylinder or drum having a size to provide a sliding fit within the first portion 276 holes 274 to drive. Accordingly, the cylinder 734 prevents the pushing rod element 720 forward from the opening 274 to drive.

Spring 722 pusher is a compression spring, outer diameter which provides a sliding fit within the first portion 276 holes 274 to drive. The front end of the spring 722 of the pusher comes into contact with the cylinder rod 734 element 720, while the opposite end of the spring 722 of the pusher comes into contact with the follower 724. Terminal part 740 of the pusher 724 has a cylindrical shape and a size to provide a sliding fit within the internal d is ametra spring 722 pusher. In this regard, the terminal part 740 of the pusher acts as a spring rod to prevent bending of the spring 722 pusher when it is compacted. The pusher 724 also includes a pushing part 744, which has a cylindrical housing portion 746, terminal part 748 and the ledge 750. Body part 746 has a size to provide a sliding fit within the first portion 276 holes 274 to drive. Terminal part 748 is configured for entering into contact with the surface 316 of the clutch and in the example shown is formed as an end of the carcass part 746 of the pusher 724 with a spherical radius. Step 750 is formed on the boundary between the carcass part 746 and terminal part 740. The ledge 750 has a flat shape and is designed to receive bias of the efforts transmitted by the spring 722 pusher.

Also shows the adjustment mechanism 704, including the adjustment structure 760 and ring 762. The adjustment structure 760 is made in the form essentially of a hollow cylinder having dimensions providing the fit in the case 766 node 20 of the output shaft. The adjustment structure 760 includes an annular surface 768, which formed the adjustment profile 770. The adjustment profile 770 contains the first adjustment segment 772, the last adjustment segment 774, many intermediate adjustment segments 776 the inclined section 778 between the first and last adjustment segments 772 and 774. In the shown embodiment of the invention between the last intermediate adjustment segments 776z and the last adjustment segment 774 included the second inclined section 779. In addition, in the specific embodiment of the invention, part of the adjustment profile 770 from the first adjustment segments 772 until the last intermediate of the adjusting segment 776z presented as an inclined surface having a constant slope. Accordingly, the Cam followers surface 780 connected to the housing 766 node 20 of the output shaft, loaded radially outward toward the inner diameter of the adjustment structure 760, where it interacts with many retainers 782 formed in the regulatory mechanism 704 (for example, in the installation ring 762). The pusher 724 and a lot of clamps 782 interact, providing to the user of the tool 10 feel the designation position of the adjustment profile 770, and also preventing free rotation of the adjustment structure 760 and holding the position of the adjustment profile 770 in the desired one of the adjustment segments 772, 774 and 776.

Ring 762 is connected to the outer surface of the adjustment structure 760 and includes many convex captured surfaces 790, which enable the user is Yu tool 10 is conveniently rotate and ring 762, and the adjustment structure 760 to set the required segment from the number of adjustment segments 772, 774 and 776 of the adjustment profile 770. For display position adjustment profile 770 relative to the housing 766 node 20 of the output shaft is the installation indicator 792. In the example installation indicator 792 includes arrow 794 located on the housing 766 node 20 of the output shaft, and on the circumference of the adjusting ring 762 marked scale 796.

During operation of the tool 10 primary drive torque is transmitted to pinion 46 of the electric motor from the node 14 of the motor on the first set 312 of the planetary gears, which causes rotation of the first set 312 of the planetary gears. The rotation of the first set 312 of the planetary gears of the first annular gear wheel 310 is communicated to the first intermediate torque. This point provides the resistance of the clutch torque, which is generated by the mechanism 18 of the clutch. Clutch torque prevents free rotation of the first ring gear 310, which causes the message to the first intermediate torque to the first downward cage 314 and the rest of the block 202 lower gears in such a way that it increases the first intermediate torque ass is authorized way in accordance with the setting of the change-over mechanism 60. In this respect, the mechanism 18 of the clutch holds the first step-down node 302 gears in active mode.

The magnitude of the clutch torque is set by the regulating mechanism 704 and, more specifically, the relative height adjustment segments 772, 774 or 776, which comes in contact with the target part 732 of the truss element 720. When installing the regulatory mechanism 704 at a given one of the adjustment segments 772, 774 or 776 rod element 720 is pushed back into the hole 274 to drive, thereby compressing the spring 722 pusher and creating traction force. Adhesive force is transmitted to the ledge 750 pusher 724, causing the coupling terminal part 748 of the pusher 724 surface 316 of the clutch and the creation of the clutch torque. The location of the terminal part 748 of the pusher 724 in one of the cavities 712 on the surface 316 of the clutch prevents rotation of the first ring gear 310 relative to the sleeve 200 of the transmission when the value of the clutch torque exceeds the first intermediate torque. However, when the first intermediate torque exceeds the clutch torque, the first ring gear 310 receives the opportunity to rotate relative to the sleeve 200 of the transmission. Depending on the configuration of the surface 316 of the clutch on Orot the first ring gear 310 may cause the increase of the adhesion forces sufficient to resist further rotation. In such situations, the first ring gear 310 is rotated in the opposite direction, when the value of the first intermediate torque is reduced, allowing the alignment of the terminal part 748 of the pusher 724 in one of the cavities 712 in the surface 316 of the clutch. If the rotation of the first ring gear 310 does not cause increase of the adhesion forces sufficiently to prevent rotation of the first ring gear 310, the first step-down node 302 gears will be in the position of a passive mode in which the first ring gear 310 rotates, preventing transmission of the first intermediate torque to the first downward cage 314. In such situations, the torque will not be transmitted to the parts of the transmission unit 16, which are located in front of the first set 312 of the planetary gears (for example, the first lowering planet carrier 314, the second sun wheel 358, a second set of 362 planetary gear wheels).

This configuration mechanism 18, the clutch has the great advantage that the magnitude of the clutch torque is set so that it withstood the first intermediate torque as opposed to the output torque of the tool 10, which is generated multistage is decreasing transmission node 16 and is passed through a jaw Chuck 22. In this respect, the mechanism 18 of the clutch may be of relatively small size, which thus increases its suitability for inclusion in the design of the tool 10 or mounting it. In addition, since the rotational speed or the gear ratio change after the first ring gear 310, the mechanism 18 of the clutch operates with a relatively large range of output torques. Compared with the conventional clutch mechanisms that operate to limit the output torque of the transmission, these devices typically operate in a relatively narrow range of torques, requiring replacement of their spring clutch, if you want a significant change in the value of the output torque. In contrast, the mechanism 18 of the clutch according to the invention can adapt to a significant change in the value of the output torque of the tool 10 by means of a simple operation transmission unit 16 with another (i.e. low or high) gear ratio.

When operating rotating machinery tools, such as tool 10, it is often necessary to change two settings of the clutch, for example when the tool 10 is used for drilling holes and then screwing the screw into this hole. The meet is but the adjustment mechanism 704 can be rotated with respect to the host 20 of the output shaft to install the regulatory mechanism 704 in accordance with the required adjustment segments 772, 774 and 776 to perform the first operation and then turn in the second position of the adjustment segments 772, 774 and 776 to perform the second operation. In contrast to the well-known clutch mechanisms regulating mechanism 704 according to the invention is designed so that the adjustment structure 760 and ring 762 can be rotated 360°. Assuming that the adjustment structure 760 should be installed in accordance with the interim adjustment segment BH, the rotation regulating mechanism 704 at an angle of 360° will cause rotation of the adjustment structure 760 with the passage of other intermediate adjustment segments 776, as well as the first and last adjustment segments 772 and 774 and an inclined section 778 so that the adjustment structure 760 can be re-installed in accordance with the adjusting segment BH. This feature is especially useful if you need to change the setting of the clutch from the relatively high strength of adhesion to a relatively low friction. In this regard, the inclined section 778 allows you to rotate the adjusting ring 762 (and adjusting structures shall 760) from the position of maximum adhesion forces, the last adjustment segment, at minimum power clutch corresponding to the first installation, without the need to establish a mechanism of the clutch 18 in one of the intermediate units of the clutch. Accordingly, the user of the tool 10 is capable of changing the setting of the adhesion forces from the highest setting to the lowest setting (and Vice versa) by turning the setting ring 762 at a relatively small angle.

Although the adjustment profile 770 so far was described as having a constant slope, specialists in the art will understand that the invention in a broader sense can be made any other way. For example, the adjustment profile 770' may be formed so that each of the first, last and intermediate adjustment segments 772', 774' 776' will have a locking recess, as shown in Fig. In this device, the locking elements 782 in the adjustment structure 760 and Cam followers surface 780 in the case 766 node 20 of the output shaft is not needed, because the adjustment segments 772', 774' 776' will interact with the node 702 clutch, providing to the user of the tool 10 feel the designation position of the adjustment profile 770' and preventing free rotation maintains the adjustment structure 760.

Another example is shown in Fig, where the adjustment profile 770", essentially similar to the adjustment profile 770, except that the inclined section 779 excluded, and, therefore, the last intermediate of the adjusting segment 776z directly adjacent to the last adjustment segment 774.

Although the invention has been disclosed in the description and illustrated in the drawings with reference to a specific variant of its implementation, specialists in the art it will be clear that it can be made various changes, and its elements can be replaced by equivalents without departing from the scope of protection of the invention defined by the claims. In addition, in a variant embodiment of the invention can be made many modifications to adapt to a particular situation or material without departing from the true scope of the invention. Thus, it is assumed that the invention is not limited to a particular variant of its implementation, shown in the drawings and disclosed in the description as the best currently considered a variant of implementation of the present invention, and will include all variants covered by the description of the accompanying claims.

1. Mechanized instrument containing an electric motor having an output shaft, the transmission having pervo the part with the first gear and the second part, with output gear ratio, the first of which includes the node planetary gear set with the ring gear, a sun wheel and a node of the planetary gears, while the ring gear is not connected with the second part of the transmission, the node of the planetary gears has a planetary carrier and a set of planetary gears, the planetary carrier has a lot of pins for holding rotatably the set of planetary gears and the output sun wheel, and a set of planetary gears engaged with the sun wheel and the ring gear, the sun wheel is connected with the output shaft and receives input torque from the electric motor, the output the sun-wheel is engaged with the second part and generates intermediate output torque, the second part takes the intermediate torque and creates an output torque, and the node coupling to limit the output torque of the mechanized tool, and the node coupling has an annular coupling element and the drive unit clutch, while the annular coupling element is connected with the annular gear wheel, an annular coupling element has a specified profile of the clutch and the drive unit clutch has a pusher, the pusher UE is extended into the annular coupling element and interacts with a given profile of the coupling to prevent relative rotation between the annular coupling element and the plunger, only when the value of the intermediate output torque is less than the specified maximum torque.

2. Machine tool according to claim 1, in which the annular coupling element and a ring gear formed as a single item.

3. Machine tool according to claim 1, in which between the ring gear and the annular coupling element is absorbing the shock structure.

4. Machine tool according to claim 3, in which at least either the annular coupling element or shock absorbing structure includes a locking element for engagement with a mating locking element formed on the annular gear wheel, and the locking element is engaged with the mating locking element to prevent relative rotation between the ring gear and at least either the annular coupling element, or absorbing the shock structure.

5. Machine tool according to claim 1, in which the drive unit clutch includes a spring element to bias the plunger to the ring coupling element to prevent relative rotation between the annular coupling element and the plunger, when the intermediate value of the output torque is less than the specified maximum torque.

Mohaisany tool according to claim 5, optionally containing a regulatory mechanism to selectively control the force applied by a spring element to the plunger.

7. Machine tool according to claim 1, in which the plunger has a spherical end portion for entering into contact with the predetermined profile of the coupling ring coupling element.

8. Machine tool according to claim 1, in which the specified profile coupling ring coupling element has a sinusoidal shape.

9. Machine tool according to claim 1, in which the specified profile coupling ring coupling element has many wedge-shaped inclined surfaces.

10. Machine tool according to claim 1, in which the plunger can move along an axis parallel to the longitudinal Central axis of the ring gear.

11. Mechanized instrument containing an electric motor having an output shaft pinion gear that engages with the output shaft of the motor for joint rotation with it, a three-stage, three-speed planetary transmission having a first planetary part, which is not associated with the output stage three-stage three-speed planetary transmission, and the first planetary part includes many of the planetary gears and the ring gear while the planetary gear is going in engagement with the pinion and the annular gear wheel, the ring gear is not connected with any other stage three-stage three-speed planetary transmission, and the node coupling to limit the output torque of the three-step three-speed planetary transmission, the node clutch has an annular coupling element and the drive unit clutch, an annular coupling element is connected with the annular gear wheel and has a specified profile of the clutch, the drive unit clutch has the plunger and the adjustment mechanism, the adjustment mechanism is configured to create a bias efforts of the preset value for the displacement of the pusher into contact with the annular coupling element, the plunger interacts with a given profile of the coupling ring coupling element to prevent relative rotation between the ring element clutch and follower when the output torque of the first planetary part is less than the specified maximum torque.

12. Machine tool, comprising a housing, a motor located in the housing, an output spindle, the transmission having a transmission sleeve first part and the second part, and the transmission sleeve includes a Central channel, which at least partially located first and second parts of the transmission, and the first part of the tra is sessii connected to the motor and receives from it the input torque, the second part of the transmission is connected with the output spindle, the first part of the drive train has at least one notch, at least one stage includes a first stage ring gear, the ring gear is not connected with any other part of the transmission, the first part of the powertrain generates intermediate output torque of the second part of the transmission, the second part of the powertrain adopts an intermediate torque and creates an output torque is continuously transmitted to the output spindle, and a node coupling connected to the transmission, the node contains an annular clutch element of the clutch and the drive unit clutch, while the annular coupling element connected with the annular gear wheel and has a specified profile of the clutch, the drive unit clutch has a plunger located in the transmission sleeve and abutting against the annular coupling element and the plunger interacts with a given profile of the coupling ring coupling element to prevent relative rotation between the annular coupling element and the plunger only when the value of the intermediate torque is less than the specified maximum torque.

13. Mechanized instrument containing an electric motor, an output spindle, transmission, yousuper part and the second part, in this second part of the transmission is connected with the output spindle, the first part has at least one notch, at least one stage includes a node of the planetary transmission with multiple gears, including a ring gear, and the ring gear is not connected with the second part of the transmission, the first part connected to the motor and receives from it the input torque, while the first part generates intermediate output torque of the second part of the transmission, the second part of the powertrain adopts an intermediate torque and creates an output torque is continuously transmitted to the output spindle, and a node coupling connected to the transmission moreover , the site contains an annular clutch element of the clutch and the drive unit clutch, while the annular coupling element is connected with the annular gear wheel and has a specified profile of the clutch, the drive unit clutch has a plunger, rests in the annular coupling element and the plunger interacts with a given profile of the coupling ring coupling element to prevent relative rotation between the annular coupling element and the plunger only when the value of the intermediate torque is less than the specified maximum torque.

14. Mechanizers the config tool 13, in which the annular coupling element and a ring gear formed as a single item.

15. Machine tool according to item 13, in which the annular gear wheel and the annular coupling element is absorbing the shock structure.

16. Machine tool 15, in which at least either the annular coupling element or shock absorbing structure includes a locking element for engagement with a mating locking element formed on the annular gear wheel, and the locking element is engaged with the mating locking element to prevent relative rotation between the ring gear and at least either the annular coupling element, or absorbing the shock structure.

17. Machine tool according to item 13, in which the drive unit clutch includes a spring element to bias the plunger to the ring coupling element to prevent relative rotation between the annular coupling element and the plunger, when the intermediate value of the output torque is less than the specified maximum torque.

18. Mechanized tool 17, further containing a regulatory mechanism to selectively control the efforts of the spring elements is ω pusher.

19. Machine tool according to item 13, in which the plunger has a spherical end section for entering into contact with the predetermined profile of the coupling ring coupling element.

20. Machine tool according to claim 19, in which the plunger has a length which exceeds the radius determines the size of the spherical terminal section.

21. Machine tool according to item 13, in which the specified profile coupling ring coupling element has a sinusoidal shape.

22. Machine tool according to item 13, in which the specified profile coupling ring coupling element has many wedge-shaped inclined surfaces.

23. Machine tool according to item 13, in which the plunger can move along an axis parallel to the longitudinal Central axis of the ring gear.

24. Machine tool according to item 13, in which the first part of the transmission is a two-stage planetary gear.

25. Machine tool according to paragraph 24, in which the ring gear is connected with the first stage of two-stage planetary gear set.



 

Same patents:

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmissions controlled by electronic unit and hydraulic devices. Proposed hydromechanical transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. All planetary trains have negative inner gear ratio output link of torque converter is coupled with sun gear 8 of second planetary trains and is connected through friction clutch 17 with carrier 6 of first planetary train. Carrier 6 is coupled with sun gear 14 of fourth planetary train and, through friction brake 21, with case 1. Sun gear 5 of first planetary train is coupled with case 1 through friction brake 20. Ring gear 10 of second planetary train is connected through friction brake 19 with case 1 and through friction clutch 18, with carrier 12 of third planetary train. Carrier of 9 of second planetary train is coupled with sun gear 11 of third planetary train. Ring gear 13 of third planetary train is coupled with carrier 15 of fourth planetary train which is coupled with case through friction brake 22. Ring gear 7 of first planetary train is connected with ring gear 16 of fourth planetary train and with carrier 12 of third planetary train which is coupled link of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of nine forward speeds and one reverse speed at preservation of overall dimensions.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmission controlled by electronic unit and hydraulic devices. Proposed transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. All planetary trains have negative inner ratio. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 6 of first planetary train, and through friction clutch 17, with sun gear 5 of said train which is connected with case 1 through friction brake 19. Carrier 6 is connected with ring gear 13 of third planetary train and, through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with sun gear 11 of third planetary train. Ring gear 10 of second planetary train is coupled with sun gear 14 of fourth planetary train which is coupled through friction brake 22 with case 1. Carrier 15 of fourth planetary train is coupled, through friction brake 21, with case 1. Ring gear 16 of fourth planetary train is coupled with carrier 12 of third planetary train being output link of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of ten forward speeds and one reverse speed at preservation of overall dimensions.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used in automatic transmissions controlled by electronic unit and hydraulic devices. Proposed hydromechanical transmission contains hydrodynamic torque converter 2 and planetary reduction gear consisting of four planetary trains. Output link of torque converter is coupled with sun gear 8 of second planetary train, is connected through friction clutch 18 with carrier 12 of third planetary train and through friction clutch 17, with gear 11 of this train which is connected with case 1 through friction brake 22. Sun gear 5 of first planetary train is connected with case 1 through friction brake 19. Ring gear 10 of second planetary train is coupled with carrier 6 of first planetary train and through friction brake 20, with case 1. Ring gear 7 of first planetary train is coupled with carrier 9 of second planetary train and with rings gears 13 and 16 of third and fourth planetary gear trains. Sun gear 14 of fourth planetary train is coupled with carrier 12 of third planetary train and, through friction brake 21, with case 1. Carrier 15 of fourth planetary gear train is output link of transmission.

EFFECT: enlarged mechanical capabilities of transmission owing to provision of ten forward speeds and one reverse speed at preservation of overall dimensions.

1 dwg

FIELD: transport engineering.

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1 dwg

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1 cl, 3 dwg

FIELD: mechanical engineering.

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FIELD: mechanical engineering.

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EFFECT: enhanced convenience of operation and prolonged service life.

1 cl, 2 dwg

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