JP2005042846A - Deceleration drive device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enhance the supporting rigidity of a differential device to a housing while interrupting the drive of an electric motor or the like from a wheel side. <P>SOLUTION: The deceleration drive device comprises an electric motor 5, first and second deceleration mechanisms 33 and 35, and a rear differential 37, and the rear differential 37 comprises a differential case 101, an inner case 111, and differential gear mechanisms 115, 117 and 119. An intermittent mechanism 143 which is capable of transmitting the torque from the differential case 101 to the inner case 111 attributable to the friction force of a brake shoe 133 when the differential case 101 is rotated prior to the inner case 111, and relatively rotating the inner case 111 to the differential case 101 is when the inner case 111 is rotated prior to the differential case 101 is provided between the differential case 101 and the inner case 111. The brake shoe 133 is disposed on the outer circumference of a bearing supporting part 50. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a reduction drive device used in a four-wheel drive vehicle.

An example of a conventional deceleration drive device is shown in FIG. The deceleration drive device 201 of FIG. 7 decelerates the output of the electric motor 203 and transmits it to the left and right axle shafts to drive the left and right rear wheels, for example. This electric motor 2
03 is used as an auxiliary drive source, and an engine is used as a main drive source on the front wheel side, and the left and right front wheels are driven by the engine.

The deceleration drive device 201 includes a first transmission shaft 207 and a housing 205 on a fixed side.
Is supported rotatably, and the rotation of the electric motor 203 is decelerated by the first decelerating mechanism 209 and transmitted.

The first transmission shaft 207 includes a reduction gear 211 that constitutes a second reduction mechanism 213.
Is provided. The other reduction gear 215 of the second reduction mechanism 213 is engaged with the reduction gear 211. The reduction gear 215 of the second reduction mechanism 213 is provided on the second transmission shaft 217. The second transmission shaft 217 is disposed in parallel to the first transmission shaft 207 and is rotatably supported by the housing 205.

The second transmission shaft 217 includes a reduction gear 221 that constitutes a third reduction mechanism 219.
Is provided. The input gear 225 of the two-way clutch 223 is engaged with the reduction gear 221 as the other reduction gear of the third reduction mechanism 219.

The rear differential 227 includes a differential case 229 and a differential gear mechanism 231.
It is comprised by. The differential case 229 is rotatably supported by the housing 205 by a bearing 233.

A two-way clutch 223 is provided on the circumference of the boss portion 235 of the differential case 229, and an inner ring 237 of the two-way clutch 223 is spline-connected to the boss portion 235 so as not to rotate relative thereto.

The two-way clutch 223 generates driving torque from the input gear 225 side for the inner ring 2.
The driving torque from the inner ring 237 side is not transmitted to the input gear 225 side.

Therefore, by driving the electric motor 203 at the time of starting or the like, torque transmission can be performed to the rear wheel side and the starting performance is improved. Furthermore, when the rotation of the differential case 229 exceeds the rotation of the input gear 225 due to driving from the rear wheels, the two-way clutch 223 is idled, and over-rotation of the electric motor 203 can be prevented.

Similarly, when the drive of the electric motor 203 is stopped, the two-way clutch 2
23 is idling, and the third speed reduction mechanism 219, the second speed reduction mechanism 213, the first speed reduction mechanism 209, and the electric motor 203 are not driven from the rear wheels, and energy loss is reliably suppressed and fuel efficiency is improved. The durability of the electric motor 203 can also be improved (see, for example, Patent Document 1).

However, in the structure as shown in FIG. 7, the two-way clutch 223 is disposed on the boss portion of the differential case 229, and the span between the bearings 233 that support the differential case 229 on the housing 205 is long. For this reason, there is a limit to the improvement of the support rigidity of the rear differential 227, which easily causes vibrations and the like, and the durability may be impaired.

JP 2000-104759 A

  The problem to be solved is that there is a limit to the improvement of the differential support rigidity, the occurrence of vibrations and the like is likely to occur, and the durability is also impaired.

  In order to improve the support rigidity of the differential device with respect to the housing, the invention of claim 1 is supported by the drive source, a speed reduction mechanism that is supported by the housing on the fixed side and decelerates the drive force of the drive source, and is supported by the housing. A differential device that distributes the output of the speed reduction mechanism to the axle side, and the differential device is supported by a bearing support portion of the housing and receives an output of the speed reduction mechanism; and the input rotation portion An output rotating part capable of relative rotation and a differential gear mechanism supported by the output rotating part, and a friction part between the input rotating part and the output rotating part are provided between the input rotating part and the output rotating part. Thus, when the input rotation unit rotates in advance with respect to the output rotation unit, torque can be transmitted from the input rotation unit to the output rotation unit due to the frictional force of the friction unit. The main feature is that an intermittent mechanism is provided that allows the output rotating portion to rotate relative to the input rotating portion when the output rotating portion rotates in advance, and the friction portion is arranged on the outer periphery of the bearing support portion. To do.

  A second aspect of the present invention is the speed reduction drive device according to the first aspect, wherein the friction portion is mounted on an intermediate member disposed on an outer periphery of the bearing support portion so as to be relatively rotatable, and the intermediate portion is mounted on the housing. An actuator for engaging and disengaging a member with the housing is provided, and when the intermediate member is engaged with the housing by the actuator, a frictional force of the friction portion can be generated with respect to the intermediate member.

  A third aspect of the present invention is the reduction driving device according to the first or second aspect, wherein the intermittent mechanism is provided in a polygonal meshing portion provided in the input rotating portion and in the output rotating portion. A cylindrical coupling part that forms an inner / outer space facing the meshing part, a plurality of rollers interposed between the meshing part and the coupling part, and a support that supports the roller and rotationally engages the friction part It is characterized by comprising a member.

  According to a fourth aspect of the present invention, there is provided the reduction driving device according to the third aspect, wherein the meshing portion is disposed on an inner periphery of the coupling portion with the roller interposed therebetween, and the outer peripheral surface of the coupling portion is the input surface. The outer peripheral surface of the coupling portion is formed so as to be capable of frictional engagement with the inner peripheral surface of the input rotating portion by being elastically expanded and deformed by the elastic deformation of the coupling portion. To do.

  A fifth aspect of the present invention is the deceleration drive device according to any one of the first to fourth aspects, wherein the drive source is supported by the housing, and the deceleration mechanism decelerates the driving force of the drive source. A first speed reduction mechanism, and a second speed reduction mechanism that is disposed between the drive source and the first speed reduction mechanism and decelerates the output of the first speed reduction mechanism. A planetary carrier, a planetary gear rotatably supported by the planetary carrier, an internal gear and a sun gear meshing with the planetary gear, and the differential device distributes the output of the second reduction mechanism to the axle side. And

  According to a sixth aspect of the present invention, there is provided the speed reduction driving device according to the fifth aspect, wherein the first speed reduction mechanism is configured such that the planetary carrier is rotatably supported by a fixed housing, and the rotation shaft of the planetary carrier. A transmission shaft extending in the center and transmitting the output of the drive source is coupled to the sun gear, and the internal gear is fixedly provided on the housing side, and the second reduction mechanism is configured by the planetary carrier. And a ring gear of the differential device meshing with the reduction gear.

  A seventh aspect of the invention is the speed reduction drive device according to any one of the first to sixth aspects, wherein the drive source is a sub drive source with respect to another main drive source.

  The invention according to claim 8 is the deceleration drive device according to claim 7, wherein the main drive source is an engine and the sub drive source is an electric motor, and one of the engine and the electric motor is one of the front and rear wheels. The other is driven by the other.

  According to the first aspect of the present invention, a drive source, a speed reduction mechanism that is supported by a fixed housing and decelerates the driving force of the drive source, and a differential device that is supported by the housing and distributes the output of the speed reduction mechanism to the axle side. An input rotation unit that is rotatably supported by a bearing support unit of the housing and receives the output of the speed reduction mechanism, an output rotation unit that can rotate relative to the input rotation unit, and the output A differential gear mechanism supported by the rotating part, and having a friction part between the input rotating part and the output rotating part between the housing and the input rotating part relative to the output rotating part. Torque can be transmitted from the input rotating unit to the output rotating unit due to the frictional force of the friction unit during the preceding rotation, and when the output rotating unit rotates in advance from the input rotating unit, the output rotation is performed with respect to the input rotating unit. Part is provided an intermittent mechanism that enables relative rotation of the friction portion may be disposed on the outer periphery of the bearing support portion.

  For this reason, it is possible to reduce the span between the bearing support portions that support the input rotation portion of the differential device on the housing, while it is possible to cut off the driving source and the like from the wheel side by the intermittent mechanism. Therefore, it is possible to improve the support rigidity of the differential device, suppress vibrations, and improve durability.

  According to a second aspect of the present invention, in addition to the effect of the first aspect of the invention, the friction portion is mounted on an intermediate member disposed on the outer periphery of the bearing support portion so as to be relatively rotatable, and the intermediate member is mounted on the housing. An actuator for engaging and disengaging the housing is provided, and when the intermediate member is engaged with the housing by the actuator, a frictional force of the friction portion can be generated with respect to the intermediate member.

  For this reason, by releasing the engagement of the intermediate member with the housing by the actuator, the intermediate member can rotate relative to the bearing support portion even if the frictional force of the friction portion is generated with respect to the intermediate member. . Therefore, regardless of the state of the intermittent mechanism when the output rotation unit rotates in advance, the output rotation unit can immediately immediately rotate relative to the input rotation unit, and the drive source and the like from the wheel side can be surely cut off. Can do.

  According to a third aspect of the present invention, in addition to the effect of the first or second aspect of the invention, the intermittent mechanism includes a polygonal circular meshing portion provided in the input rotary portion and the meshing portion provided in the output rotary portion. A cylindrical coupling part that forms an inner / outer space in the opposite part, a plurality of rollers interposed between the meshing part and the coupling part, and a support member that supports the roller and rotationally engages the friction part Accordingly, the movement of each roller can be restricted when the support member receives the rotation resistance by the friction portion.

  For this reason, when the input rotating part rotates in advance with respect to the output rotating part, the meshing part engages with the roller and the roller meshes between the meshing part and the coupling part, and torque transmission from the input rotating part to the output rotating part is performed. It can certainly be possible.

  According to a fourth aspect of the invention, in addition to the effect of the third aspect of the invention, the meshing portion is disposed on the inner periphery of the coupling portion with the roller interposed therebetween, and the outer peripheral surface of the coupling portion is the input rotating portion. Since the outer peripheral surface of the coupling portion is formed to be capable of frictional engagement with the inner peripheral surface of the input rotating portion by elastic expansion and deformation of the coupling portion, the meshing portion of each roller. A force that frictionally engages the outer peripheral surface of the connecting portion with the inner peripheral surface of the input rotating portion can be applied to the meshing connection between the connecting portion and the connecting portion.

  Therefore, torque transmission from the input rotation unit to the output rotation unit can be more reliably performed.

  According to a fifth aspect of the present invention, in addition to the effects of any of the first to fourth aspects, the drive source is supported by the housing, and the reduction mechanism reduces the drive force of the drive source. A speed reduction mechanism, and a second speed reduction mechanism that is disposed between the drive source and the first speed reduction mechanism and decelerates the output of the first speed reduction mechanism. The first speed reduction mechanism is a planetary carrier. And a planetary gear rotatably supported by the planetary carrier, and an internal gear and a sun gear meshing with the planetary gear. The differential device can distribute the output of the second reduction mechanism to the axle side.

  Accordingly, in addition to the differential device, a configuration equivalent to that of a single transmission shaft on the side of the first speed reduction mechanism can be obtained, so that the overall size can be reduced and the weight can be reduced. It becomes possible.

  Further, since the second reduction mechanism is disposed between the drive source and the first reduction mechanism, and the first reduction mechanism is spaced from the drive source, the assembly error of the drive source causes the first reduction mechanism. The generation of vibration and abnormal noise in the first speed reduction mechanism can be suppressed, the sound vibration performance can be improved, and the durability can be improved.

  According to a sixth aspect of the present invention, in addition to the effect of the fifth aspect of the invention, the first speed reduction mechanism is configured such that the planetary carrier is rotatably supported by a stationary housing, and the rotation center portion of the planetary carrier. A transmission shaft that is extended and arranged to transmit the output of the drive source is coupled to the sun gear, and the internal gear is fixedly provided on the housing side, and the second reduction mechanism is provided on the planetary carrier. The second reduction mechanism is easily disposed between the drive source and the first reduction mechanism, and the drive force of the drive source is set to the first reduction force. It is possible to transmit the driving force that is decelerated by the first decelerating mechanism to the second decelerating mechanism from the planetary carrier of the first decelerating mechanism. This driving force can be further reduced by the reduction gear and the ring gear of the second reduction mechanism, and can be reliably transmitted to the differential device.

  In addition to the effect of the invention according to any one of claims 1 to 6, the invention according to claim 7 is small and light overall because the drive source is a sub drive source with respect to other main drive sources. Can be formed. In addition, the sound vibration performance of the sub drive source can be improved, and the durability can be improved.

  According to an eighth aspect of the invention, in addition to the effect of the seventh aspect of the invention, the main drive source is an engine, and the engine and the drive source are a drive source that drives one of the front and rear wheels and the other drives the other. Therefore, the reduction drive device that transmits power to one of the front and rear wheels in the hybrid vehicle can be configured to be small and light. In addition, it is possible to improve the sound vibration performance of the deceleration drive device and also improve the durability.

  The purpose of improving the differential support rigidity was realized by shortening the support span.

  FIG. 1 is a skeleton plan view of a hybrid vehicle to which a reduction drive device according to a first embodiment of the present invention is applied. As shown in FIG. 1, the hybrid vehicle 1 includes an engine 3 as a main drive source and an electric motor 5 as a sub drive source as a drive source. In this embodiment, the engine 3 drives the left and right front wheels 7 and 9, and the electric motor 5 is a drive source that drives the left and right rear wheels 11 and 13. However, the front wheels can be driven by the electric motor 5 as the auxiliary drive source, and the rear wheels 11 and 13 can be driven by the engine 3 as the main drive source.

  The output of the engine 3 is input to a front differential 17 that is a differential device via a transmission 15. The front wheels 7 and 9 are linked to the front differential 17 via left and right axle shafts 19 and 21.

  The output of the electric motor 5 is input to the deceleration drive device 23. The left and right rear wheels 11 and 13 are interlocked and connected to the output side of the deceleration driving device 23 via left and right axle shafts 25 and 27.

  The electric motor 5 is supplied with power from a battery 29. The electric motor 5 is supplied with power by a generator (not shown) that generates power when the output of the engine 3 is rotated, and the power generated by the generator is charged in the battery 29 when the vehicle is decelerated.

  Therefore, during normal travel, torque is transmitted to the front differential 17 via the transmission 15 by driving the engine 3. Torque is transmitted from the front differential 17 to the left and right front wheels 7 and 9 via the left and right axle shafts 19 and 21.

  In addition, power is supplied to the electric motor 5 by the power generation of the generator due to the rotation of the engine 3, and the output of the electric motor 5 is transmitted to the deceleration drive device 23. Torque is transmitted from the deceleration drive device 23 to the left and right rear wheels 11 and 13 via the left and right axle shafts 25 and 27.

  Therefore, the hybrid vehicle 1 can travel in a four-wheel drive state by driving the front wheels 7 and 9 by the engine 3 and auxiliary driving of the rear wheels 11 and 13 by the electric motor 5.

  When the vehicle starts traveling and the vehicle accelerates, power is supplied from the battery 29 to the electric motor 5 to enable smooth start traveling and acceleration traveling. When the vehicle is decelerating, the battery 29 is charged by power generation by the generator, and is prepared for the next start-up and acceleration.

  The deceleration drive device 23 of the hybrid vehicle 1 is, for example, as shown in FIG. FIG. 2 is a cross-sectional view of the deceleration drive device 23.

  As shown in FIG. 2, the speed reduction driving device 23 is attached to the vehicle body side, a first speed reduction mechanism 33 and a second speed reduction mechanism 35 as a speed reduction mechanism in a housing 31 on a fixed side, and a rear differential 37 as a differential device. And.

  The housing 31 has a structure in which a main body portion 39 and a lid portion 41 are combined. The main body portion 39 and the lid body portion 41 are fastened and connected by bolts and nuts (not shown). The housing 31 includes an input part side 43 and an output part side 45.

  Boss portions 47 and 49 are provided on the left and right of the output portion side 45 of the housing 31. Seal members 51 and 53 are attached to the open ends of the boss portions 47 and 49. Bearing support portions 48 and 50 are provided on the back side of the boss portions 47 and 49. One bearing support portion 50 is formed in a cylindrical shape and protrudes to the inside of the housing 31.

  On the input portion side 43 of the housing 31, a through portion 55 is provided in the main body portion 39, and a mounting flange 57 is provided on the outer periphery of the through portion 55. The electric motor 5 is attached to the attachment flange 57 and fastened and fixed by bolts and nuts (not shown). A seal member 59 is attached to the through portion 55.

  The first reduction mechanism 33 is disposed on the lid 41 side of the electric motor 5 with the main body 39 of the housing 31 interposed therebetween. The first speed reduction mechanism 33 is constituted by a planetary gear mechanism, and includes a planetary carrier 63, a planetary gear 65, an internal gear 67, and a sun gear 69.

  The planetary carrier 63 is obtained by connecting left and right carrier plates 71 and 73 with carrier pins 75. One carrier plate 71 is integrally provided with a hollow shaft portion 77. The shaft portion 77 is rotatably supported by the lid portion 41 via a ball bearing 79. The other carrier plate 73 is integrally provided with a hollow shaft portion 81. The shaft portion 81 is rotatably supported by the body portion 39 of the housing 31 by a ball bearing 83. Accordingly, the planetary carrier 63 is rotatably supported by the housing 31. The seal member 59 is interposed between the end portion of the shaft portion 81 and the through portion 55 of the main body portion 39. A reduction gear 85 is integrally provided at an intermediate portion of the shaft portion 81.

  A plurality of the planetary gears 65 are provided in the circumferential direction of the planetary carrier 63 and are rotatably supported by carrier pins 75, respectively.

  The internal gear 67 is fixedly provided on the housing 31 side. The internal gear 67 is formed on the inner peripheral surface of the ring member 87. The ring member 87 is fitted to the lid body 41 side of the housing 31, and the outer meshing teeth 89 mesh with the teeth 91 on the lid body 41 side to prevent rotation. A stopper 93 is provided at the end of the ring member 87, and the ring member 87 is positioned with respect to the lid body 41.

  The sun gear 69 is integrally provided at the end of the transmission shaft 95. The planetary gear 65 is engaged with the sun gear 69 and the internal gear 67.

  The transmission shaft 95 is disposed in the hollow shaft portion 81 so as to be relatively rotatable. The output shaft 97 of the electric motor 5 is linked to the transmission shaft 95 by spline fitting or the like. Accordingly, a transmission shaft 95 that extends from the rotational axis of the planetary carrier 63 and transmits the output of the electric motor 5 is coupled to the sun gear 69.

  The second reduction mechanism 35 includes the reduction gear 85 and a ring gear 99 of the rear differential 37 that meshes with the reduction gear 85. The reduction gear 85 is formed of a helical pinion gear. The ring gear 99 is formed of a helical gear, similar to the reduction gear 85. In the second reduction mechanism 35, since the reduction gear 85 and the ring gear 99 are formed of helical gears, the meshing rigidity is good and the generation of abnormal noise can be suppressed.

  The rear differential 37 includes a differential case 101 as an input rotating portion to which the ring gear 99 is attached. The differential case 101 is provided with left and right boss portions 103 and 105. In the differential case 101, boss portions 103 and 105 are rotatably supported by bearing support portions 48 and 50 of the housing 31 by ball bearings 107 and 109.

  In the differential case 101, an inner case 111 as an output rotating portion is accommodated and supported. The inner case 111 is rotatable relative to the differential case 101. The inner case 111 has a rotational axis that is concentric with the rotational axis of the differential case 101 and has a generally cylindrical shape.

  A pinion gear 115 constituting a differential gear mechanism is supported on the inner case 111 via a pinion shaft 113. Left and right side gears 117 and 119 constituting a differential gear mechanism are meshed with and coupled to the pinion gear 115. The side gears 117 and 119 are interlocked with axle shafts 25 and 27 on the rear wheels 11 and 13 side.

  At the end of the inner case 111, a cylindrical coupling part 121 is provided which is thinner than other parts. The boss portion 105 is provided with a meshing portion 123 located on the inner peripheral side of the coupling portion 121. The outer peripheral surface of the meshing portion 123 is as shown in FIG.

  3A is a cross-sectional view showing the relationship between the coupling portion 121 and the meshing portion 123, and FIG. 3B is a simplified development view showing the arrangement of the rollers.

  As shown in FIG. 3A, the outer periphery of the meshing portion 123 is formed in a polygonal shape, and a plurality of flat meshing surfaces 125 are provided. A roller 127 is interposed between the coupling portion 121 and each meshing surface 125. The rollers 127 arranged as shown in FIGS. 3A and 3B are rotatably supported by a support member 129, respectively. The support member 129 extends from the through hole 131 of the differential case 101 to the outside of the differential case 101 and engages with a brake shoe 133 that constitutes a friction portion.

  A ring-shaped spring 135 is wound around the outer periphery of the brake shoe 133. The brake shoe 133 is pressed against the inner peripheral side by the spring 135. A ring-shaped slide plate 137 having an L-shaped cross section as an intermediate member is provided on the inner peripheral side of the brake shoe 133. A brake shoe 133 is pressed against the slide plate 137 so that the brake shoe 133 generates a frictional force against the slide plate 137. The slide plate 137 is rotatably supported on the outer periphery of the bearing support portion 50 of the housing 31. An electromagnet 139 is disposed outside the housing 31 with respect to the slide plate 137. The electromagnet 139 is fastened and fixed outside the housing 31 by screws 141.

  The coupling part 121, the meshing part 123, the roller 127, the support member 129, the brake shoe 133, the spring 135, the slide plate 137, and the electromagnet 139 constitute an intermittent mechanism 143.

  Accordingly, the driving force is transmitted from the output portion of the electric motor 5 to the transmission shaft 95 by the rotation of the electric motor 5. As a result, the sun gear 69 rotates integrally, and the planetary gear 65 rotates. The planetary gear 65 revolves by meshing with the internal gear 67 while rotating, and the carrier plates 71 and 73 rotate with respect to the transmission shaft 95 through the carrier pins 75 at a reduced speed.

  The reduction gear 85 rotates together with the reduction rotation of the carrier plate 73, and torque is transmitted to the ring gear 99. The rotation is also reduced by the meshing rotation between the reduction gear 85 and the ring gear 99, and torque is transmitted to the differential case 101 by the reduced rotation.

  When the intermittent mechanism 143 is in a connected state, torque is transmitted from the differential case 101 to the inner case 111, and torque is transmitted to the axle shafts 25 and 27 via the pinion shaft 113, the pinion gear 115, and the side gears 117 and 119. And the rear wheels 11 and 13 are driven.

  During the differential rotation of the rear wheels 11 and 13, the side gears 117 and 119 rotate differentially through the rotation of the pinion gear 115, and the differential rotation between the rear wheels 11 and 13 can be allowed.

  When the intermittent mechanism 143 is in the shut-off state, even if the inner case 111 rotates, torque is not transmitted to the differential case 101 and the inner case 111 rotates relative to the differential case 101.

  The intermittent mechanism 143 is intermittently controlled by energization control to the electromagnet 139. When the electromagnet 139 is energized, the slide plate 137 is attracted to the electromagnet 139 side and is in close contact with the inner surface of the housing 131. With this close contact, the brake shoe 133 generates a frictional force against the slide plate 137 and exerts the frictional force on the support member 129.

  Each roller 127 supported by the support member 129 is restricted in movement in the rotation direction of the differential case 101 by the support member 129. When the differential case 101 further rotates at this time, the rotation of the differential case 101 precedes the inner case 111 and the roller 127 meshes with the meshing surface 125.

  When the roller 127 meshes with the meshing surface 125, a reaction force against the meshing portion 123 acts on the coupling portion 121 via the roller 127. Due to the action of the reaction force, the connecting portion 121 is expanded in diameter within the range of elastic deformation, and a pressing force is applied to the inner surface of the differential case 101 outward in the direction along the rotation radius.

  By this pressing force, the outer surface of the coupling part 121 and the inner surface of the differential case 101 are frictionally engaged.

  For this reason, the friction engagement between the outer surface of the coupling portion 121 and the inner surface of the differential case 101 is added to the engagement between the meshing portion 123 and the coupling portion 121 due to the roller 127 meshing with the meshing surface 125, and the differential case 101 and the inner case 111. Can rotate integrally and transmit torque to the rear wheels 11 and 13 as described above.

  When the energization of the electromagnet 139 is interrupted, the slide plate 137 is rotatable relative to the housing 31 side.

  Therefore, since the slide plate 137, the brake shoe 133, and the support member 129 rotate as a unit, the rollers 127 are not restricted in movement and do not mesh with the meshing surface 125. Further, the coupling part 121 is not pressed against the inner surface of the differential case 101, and the inner case 111 is not frictionally engaged with the differential case 101. The inner case 111 is rotatable relative to the differential case 101.

  In this relatively rotatable state, when the electric motor 5 is stopped, even if torque is transmitted from the rear wheels 11 and 13 side to the axle shafts 25 and 27 and the side gears 117 and 119, the pinion gears from the side gears 117 and 119. 115, only the inner case 111 rotates via the pinion shaft 113, and the rotation is not transmitted to the differential case 101.

  For this reason, the second speed reduction mechanism 35 can be kept stopped, and the second speed reduction mechanism 35, the first speed reduction mechanism 33, and the electric motor 5 are rotated by the rotation of the rear wheels 11 and 13. Absent. Therefore, a large energy loss caused by driving the speed reduction mechanisms 35 and 33 from the reverse direction and an energy loss caused by driving the stopped electric motor 5 on the rear wheels 25 and 27 side are surely suppressed, thereby improving fuel efficiency. The durability of the electric motor 5 can also be improved.

  As is clear from the above description, the bearing support portions 48 and 50 for supporting the differential case 101 of the rear differential 37 on the housing 31 while the driving mechanism 143 can block the driving of the electric motor 5 and the like from the wheels 11 and 13 side. The span between them can be shortened. Therefore, it is possible to improve the support rigidity of the rear differential 37, suppress the occurrence of vibration, and improve the durability.

  The brake shoe 133 is mounted on a slide plate 137 disposed on the outer periphery of the bearing support portion 50 so as to be relatively rotatable, and an electromagnet 139 that engages and disengages the slide plate 137 with the housing 31 is provided on the housing 31. When the slide plate 137 is engaged with the housing 31 by the electromagnet 139, a frictional force of the brake shoe 133 can be generated on the slide plate 137.

  For this reason, by disengaging the slide plate 137 from the housing 31 by the electromagnet 139, the slide plate 137 is against the bearing support 50 even if the frictional force of the brake shoe 133 is generated against the slide plate 137. Relative rotation. Therefore, regardless of the state of the intermittent mechanism 143 when the inner case 111 rotates in advance, the inner case 111 can immediately rotate relative to the differential case 101, and it is ensured that the electric motor 5 and the like are driven from the wheels 11 and 13 side. Can be blocked.

  The intermittent mechanism 143 includes a polygonal circumferential engagement portion 123 provided in the differential case 101, and a cylindrical coupling portion 121 provided in the inner case 111 and facing the engagement portion 123 with an internal / external spacing therebetween. The brake shoe 133 includes a plurality of rollers 127 interposed between the meshing portion 123 and the coupling portion 121 and a support member 129 that supports the roller 127 and rotates and engages with the break shoe 133. The movement of each roller 127 can be restricted by receiving the rotation resistance of 129.

  For this reason, when the differential case 101 rotates in advance with respect to the inner case 111, the meshing portion 123 engages with the roller 127, and the roller 127 meshes between the meshing portion 123 and the coupling portion 121, and the differential case 101 moves to the inner case 111. Torque transmission can be reliably performed.

  The meshing portion 123 is disposed on the inner circumference of the coupling portion 121 with the roller 127 interposed therebetween, and the coupling portion 121 has an outer circumferential surface opposed to the inner circumferential surface of the differential case 101 so that the coupling portion 121 Since the outer peripheral surface of the coupling part 121 is formed to be able to frictionally engage with the inner peripheral surface of the differential case 101 by elastic diameter expansion deformation, the meshing coupling between the meshing part 123 of each roller 127 and the coupling part 121 is performed. In addition, a force that frictionally engages the outer peripheral surface of the coupling portion 121 with the inner peripheral surface of the differential case 101 can be applied.

  Therefore, torque transmission from the differential case 101 to the inner case 111 can be more reliably made possible.

  The speed reduction mechanism is disposed between the first speed reduction mechanism 33 that reduces the driving force of the electric motor 5 and the electric motor 5 and the first speed reduction mechanism 33, and the output of the first speed reduction mechanism 33. The first reduction mechanism 33 includes a planetary carrier 63, a planetary gear 65 rotatably supported by the planetary carrier 63, an internal gear 67 meshing with the planetary gear 65, and the planetary gear 65. The rear differential 37 is composed of a sun gear 69 and can distribute the output of the second reduction mechanism 35 to the axles 11 and 13 side.

  Therefore, it is possible to achieve a configuration equivalent to the case where one transmission shaft exists on the first reduction gear mechanism 33 side in addition to the rear differential 37, and the overall size can be reduced, and the weight can be reduced. It becomes possible.

  In addition, since the second reduction mechanism 35 is disposed between the electric motor 5 and the first reduction mechanism 33 and the first reduction mechanism 33 is placed at a distance from the electric motor 5, an assembly error of the electric motor 5 is caused. Can be prevented from reaching the first speed reduction mechanism 33, vibrations and abnormal noises in the first speed reduction mechanism 33 can be suppressed, sound vibration performance can be improved, and durability can be improved. Can also be improved.

  The first speed reduction mechanism 33 is configured such that the planetary carrier 63 is rotatably supported by the housing 31 on the fixed side, and is extendedly arranged at the rotation axis of the planetary carrier 63 to transmit the output of the electric motor 5. A transmission shaft 95 is coupled to the sun gear 69, and the internal gear 67 is fixedly provided on the housing 31 side. The second reduction mechanism 35 includes a reduction gear 85 provided on the planetary carrier 63, and Since it comprises the ring gear 99 of the rear differential 37 that meshes with the reduction gear 85, the second reduction mechanism 35 is easily disposed between the electric motor 5 and the first reduction mechanism 33, and the driving force of the electric motor 5 is increased. Drive decelerated by the first reduction mechanism 33 and decelerated from the planetary carrier 63 of the first reduction mechanism 33 to the second reduction mechanism 35 It is possible to transmission a. This driving force can be further reduced by the reduction gear 85 and the ring gear 99 of the second reduction mechanism 35 and can be reliably transmitted to the rear differential 37.

  Since the planetary carrier 63 is rotatably supported by the housing 31 by ball bearings 79 and 83, the support rigidity of the first reduction mechanism 33 is good, the structure is simple, the generation of sound is small, and the reliability is improved. Can be high.

  The electric motor 5 is a sub drive source for the engine 3 which is another main drive source, the engine 3 is a drive source for driving the front wheels 7 and 9, and the electric motor 5 is a drive source for driving the rear wheels 11 and 13. Therefore, the reduction drive device 23 that drives the rear wheels 11 and 13 in the hybrid vehicle can be configured to be small and light. Further, the sound vibration performance of the deceleration drive device 23 can be improved, and the durability can be improved.

  Moreover, since the rear differential 37 can have a space on the side of the electric motor 5 in the direction along the rotation axis, the setting of the intermittent mechanism 143 for adding a free differential function to the rear differential 37 becomes extremely easy. .

  4 and 5 relate to the second embodiment of the present invention, FIG. 4 is a cross-sectional view of the speed reduction drive device, FIG. 5A is a cross-sectional view showing the relationship between the coupling portion and the meshing portion, and FIG. FIG. The basic configuration is the same as that of the first embodiment, and the corresponding components will be described with the same reference numerals.

  The deceleration drive device 23A of the present embodiment is obtained by changing the coupling portion 121A and the meshing portion 123A of the intermittent mechanism 143A. The coupling portion 121A of this embodiment is provided integrally with the inner case 111A. The meshing portion 123A is provided in the differential case 101A. The polygonal engagement surface 125A is formed on the inner surface of the differential case 101A. The roller 127 is interposed between the coupling portion 121A and the meshing portion 123A.

  Therefore, in this embodiment, when the roller 127 is restricted from moving via the support member 129, each roller 127 meshes with the meshing surface 125A with respect to the rotation of the differential case 101A, and the differential case 101A and the inner case 111A rotate integrally. To do.

  When the movement restriction of the roller 127 by the support member 129 is released, the engagement with the engagement surface 125A of the roller 127 is released, and the inner case 111A side can be rotated relative to the differential case 101A.

  Accordingly, in the present embodiment, as in the first embodiment, when the electric motor 5 is stopped, the first and second speed reduction mechanisms 33 and 35 are not forcibly rotated by the rear wheels 11 and 13 side, and fuel efficiency is improved. Can do.

  FIG. 6 is a cross-sectional view of a reduction driving device according to a third embodiment of the present invention. The basic configuration is the same as that of the first embodiment, and the corresponding components will be described with the same reference numerals.

  The deceleration drive device 23B of the present embodiment is obtained by changing the intermittent mechanism 143B. Whereas the interrupting mechanism 143 of the first embodiment includes the electromagnet 139 and the slide plate 137, the interrupting mechanism 143B of this embodiment omits this, and the brake shoe 133 is directly attached to the outer peripheral surface of the bearing support portion 50. It is provided.

  The brake shoe 133 generates a frictional force directly on the outer peripheral surface of the bearing support portion 50, that is, the housing 31.

  When the differential case 101 rotates in advance with respect to the inner case 111, the brake shoe 133 generates a frictional force on the bearing support portion 50 and exerts the frictional force on the support member 129.

  Each roller 127 supported by the support member 129 is restricted in movement in the rotation direction of the differential case 101 by the support member 129. When the differential case 101 further rotates at this time, the rotation of the differential case 101 precedes the inner case 111 and the roller 127 meshes with the meshing surface 125.

  For this reason, the friction engagement between the outer surface of the coupling portion 121 and the inner surface of the differential case 101 is added to the engagement between the meshing portion 123 and the coupling portion 121 due to the roller 127 meshing with the meshing surface 125 as in the first embodiment. The differential case 101 and the inner case 111 rotate integrally and can transmit torque to the rear wheels 11 and 13 as described above.

  When the inner case 111 rotates in advance of the differential case 101, each roller 127 is subjected to movement restriction via the support member 129, and is relatively returned to the center side of the meshing surface 125. The meshing between the parts 121 is automatically released. The roller 127 can rotate at the mesh release position when the inner case 111 further rotates. Further, the coupling portion 121 is not pressed against the inner surface of the differential case 101, and the inner case 111 is not frictionally engaged with the differential case 101. The inner case 111 is rotatable relative to the differential case 101.

  Therefore, this embodiment can achieve the same effects as those of the first embodiment. In this embodiment, since the electromagnet 139 and the slide plate 137 are omitted, the structure is simpler, the assembly and component management are easier, and the manufacturing can be performed at lower cost.

1 is a skeleton plan view of a hybrid vehicle to which a first embodiment of the present invention is applied (Example 1). FIG. It is sectional drawing of the deceleration drive device which concerns on Example 1 (Example 1). (A) is sectional drawing which shows the relationship between a coupling | bond part and a meshing part, (b) is a simplified expanded view which shows the arrangement | sequence of a roller (Example 1). It is sectional drawing of the deceleration drive device which concerns on Example 2 of this invention (Example 2). (A) is sectional drawing which shows the relationship between a coupling | bond part and a meshing part, (b) is the simplified expanded view which shows the arrangement | sequence of a roller (Example 2). It is sectional drawing of the deceleration drive device which concerns on Example 3 of this invention (Example 3). It is sectional drawing of the power interruption apparatus which concerns on another prior art example.

Explanation of symbols

1 Hybrid vehicle 3 Engine (main drive source)
5 Electric motor (sub drive source, drive source)
23, 23A, 23B Deceleration drive device 33 First reduction mechanism 35 Second reduction mechanism 37 Rear differential (differential device)
63 planetary carrier 65 planetary gear 67 internal gear 69 sun gear 85 reduction gear 99 ring gear 133 brake shoe (friction part)
143, 143A, 143B Intermittent mechanism

Claims (8)

A driving source;
A speed reduction mechanism that is supported by a fixed housing and decelerates the driving force of the driving source;
A differential device that is supported by the housing and distributes the output of the speed reduction mechanism to the axle side;
The differential device is supported by an input rotation unit that is supported by a bearing support unit of the housing and receives an output of the speed reduction mechanism, an output rotation unit that can rotate relative to the input rotation unit, and the output rotation unit. With a differential gear mechanism,
Due to the frictional force of the friction part when the input rotary part rotates in advance with respect to the output rotary part with the friction part between the input rotary part and the output rotary part between the housing. An intermittent mechanism is provided that enables torque transmission from the input rotation unit to the output rotation unit and enables the output rotation unit to rotate relative to the input rotation unit when the output rotation unit rotates in advance from the input rotation unit,
A reduction driving device characterized in that the friction part is arranged on an outer periphery of the bearing support part. The reduction drive device according to claim 1,
The friction part is mounted on an intermediate member arranged to be rotatable relative to the outer periphery of the bearing support part,
The housing is provided with an actuator for engaging and releasing the intermediate member with the housing,
A reduction driving device characterized in that when the intermediate member is engaged with the housing by the actuator, a frictional force of the friction portion can be generated on the intermediate member. The reduction drive device according to claim 1 or 2,
The intermittent mechanism includes a polygonal circular meshing portion provided in the input rotation portion, a cylindrical coupling portion provided in the output rotation portion and facing the meshing portion with an internal / external spacing, and the meshing A speed reduction drive device comprising: a plurality of rollers interposed between a portion and a coupling portion; and a support member that supports the rollers and rotationally engages the friction portion. The reduction drive device according to claim 3,
The meshing portion is disposed on the inner periphery of the coupling portion via the roller,
The coupling portion has an outer peripheral surface disposed opposite to an inner circumferential surface of the input rotating portion, and the outer circumferential surface of the coupling portion is rubbed against an inner circumferential surface of the input rotating portion by elastic expansion of the coupling portion. A speed reduction drive device characterized by being formed to be engageable. It is the deceleration drive device in any one of Claims 1-4,
The drive source is supported by the housing;
The deceleration mechanism is arranged between a first deceleration mechanism that decelerates the driving force of the drive source and a second deceleration mechanism that is disposed between the drive source and the first deceleration mechanism and decelerates the output of the first deceleration mechanism. Consisting of a deceleration mechanism
The first reduction mechanism is composed of a planetary carrier, a planetary gear rotatably supported by the planetary carrier, an internal gear and a sun gear meshing with the planetary gear,
The differential drive device distributes the output of the second speed reduction mechanism to the axle side. The reduction driving device according to claim 5,
In the first speed reduction mechanism, the planetary carrier is rotatably supported by a housing on a fixed side, and a transmission shaft that extends from a rotation shaft center portion of the planetary carrier and transmits an output of a driving source is the sun gear. And the internal gear is fixedly provided on the housing side,
The second reduction mechanism comprises a reduction gear provided on the planetary carrier and a ring gear of the differential device meshing with the reduction gear. It is the deceleration drive device in any one of Claims 1-6,
A reduction driving device characterized in that the driving source is a sub driving source with respect to another main driving source. The reduction drive device according to claim 7,
The main drive source is an engine and the sub drive source is an electric motor,
One of the engine and the electric motor drives one of the front and rear wheels, and the other drives the other.

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