JP2008248900A - Differential device with differential limiting mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide the differential device with differential limiting mechanism, the driving force transmission path running from an actuator to a friction clutch of which is reduced in weight and the structure of which is simplified. <P>SOLUTION: A hollow axis 48 to transmit an engagement force generated by an actuator A to the friction clutch 52 to restrict the differential motion of the differential mechanism D comprises: an axial portion 48a extending from the actuator A into a differential case 28; a plurality of diametrically enlarged portions 48b circumferentially branched with an interval from an end portion of the axial portion 48a within the differential case 28 and expanding in diameter along an inner surface of the differential case 28 and a plurality of compression portions 48c respectively extending from the enlarged portions 48b respectively and leading to the friction clutch 52 via a side portion of a pinion 32 on a pinion shaft 32, which allows not only the weight of the hollow axis 48 to be reduced more than the case where the enlarged portions 48b are annularly formed, but also further reduction in weight to be achieved with a concave portion 24e formed on the differential case 28 and directed towards the space formed between the adjacent enlarged portions 48b. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a differential limiter including a differential mechanism that distributes and outputs a driving force of a prime mover input to a differential case to two output shafts, and a friction clutch that limits differential rotation between the two output shafts. The present invention relates to a mechanism-equipped differential device, and in particular, relates to an actuator that generates an engaging force for engaging a friction clutch on an output shaft axis and outside a differential case.

In order to limit the function of the differential mechanism that distributes the driving force of the internal combustion engine to the left and right wheels of an automobile, an actuator that engages a differential limiting friction clutch provided in the differential case extends from the differential case to the outside. A hollow shaft fitted to the outer periphery of the half shaft is provided, the hollow shaft is driven in the axial direction via the ball cam mechanism by the driving force of the motor, and the friction engagement member of the friction clutch is pressed by the shaft end of the hollow shaft. What is to be combined is known from Patent Document 1 below.
JP 2005-249080 A

  By the way, the above-mentioned conventional one forms an annular enlarged portion whose outer diameter expands at the shaft end of the hollow shaft, and four pressing portions that branch from the enlarged portion and extend in the axial direction. The structure that presses the friction engagement member of the friction clutch at the tip not only has the problem that the annular and large-diameter enlarged portion causes an increase in weight, but also differentials the thrust force of the side gear of the differential mechanism. In order to support with the case, it is necessary to make the extension part projecting on the inner surface of the differential case pass through the through hole formed in the enlarged diameter part and contact the back surface of the side gear, which complicates the structure. was there.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to reduce the weight and simplify the structure of a driving force transmission path from an actuator of a differential device with a differential limiting mechanism to a friction clutch.

  In order to achieve the above object, according to the invention described in claim 1, a differential mechanism that distributes and outputs the driving force of the prime mover input to the differential case to the two output shafts; A friction clutch that is located on one side of the pinion shaft and restricts differential rotation between the two output shafts, and is located on the output shaft on the other side of the pinion shaft outside the differential case. In the differential device with a differential limiting mechanism comprising an actuator that generates an engagement force to be combined and a hollow shaft that transmits the engagement force generated by the actuator to the friction clutch, the hollow shaft is an outer periphery of the output shaft on the other side A shaft extending from the actuator to the inside of the differential case, and branching from the end of the shaft in the differential case with an interval in the circumferential direction, A plurality of diameter-expanded portions that expand along the inner surface of the differential case, and a plurality of pressing portions that extend from the respective diameter-expanded portions and pass through the side of the pinion on the pinion shaft and extend to the friction clutch. A differential device with a differential limiting mechanism is proposed.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the enlarged diameter portion and the pressing portion are integrally formed, and the inner surface of the differential case facing the pressing portion is formed in the radial direction of the pressing portion. There is proposed a differential device with a differential limiting mechanism, characterized in that a guide portion for preventing outward deformation is provided.

  According to the third aspect of the present invention, in addition to the configuration of the first or second aspect, the inner surface of the differential case facing the space formed between the enlarged diameter portions is expanded toward the side gear side of the differential mechanism. A differential device with a differential limiting mechanism is proposed in which a thrust support surface is formed and the thrust support surface supports the thrust force of the side gear.

  The half shaft 11 and the left axle 13 of the embodiment correspond to the output shaft of the present invention, the guide groove 24d of the embodiment corresponds to the guide portion of the present invention, and the second hollow shaft 48 of the embodiment is Corresponding to the hollow shaft of the present invention, the internal combustion engine E of the embodiment corresponds to the prime mover of the present invention.

  According to the configuration of the first aspect, the hollow shaft that transmits the engagement force generated by the actuator to the friction clutch that limits the differential operation of the differential mechanism includes the shaft portion that extends from the actuator into the differential case, and the differential case. A plurality of diameter-expanded portions branching from the end portion of the shaft portion at intervals in the circumferential direction and expanding along the inner surface of the differential case, and extending from each diameter-expanded portion, side portions of the pinion on the pinion shaft And a plurality of pressing portions extending to the friction clutch, so that not only can the weight of the hollow shaft be reduced compared to the case where the enlarged diameter portion is formed in an annular shape, but also a space formed between adjacent enlarged diameter portions. By denting the differential case toward, the differential case can be reduced in size and further reduced in weight.

  According to the second aspect of the present invention, since the pressing portion formed integrally with the enlarged diameter portion is guided by the guide portion provided on the inner surface of the differential case, the enlarged diameter portion and the pressing portion are narrowed to reduce the weight. In addition, when the engaging force for engaging the friction clutch is applied, it is possible to reliably engage the friction clutch by preventing the enlarged diameter portion and the pressing portion from bending outward in the radial direction.

  According to the third aspect of the present invention, the thrust support surface is formed by expanding the inner surface of the differential case facing the space formed between the plurality of enlarged diameter portions provided on the hollow shaft. Since the thrust force of the side gear of the dynamic mechanism is supported, the thrust support surface can be easily formed without interfering with the diameter-expanded portion of the hollow shaft.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  1 to 9 show an embodiment of the present invention. FIG. 1 is a rear view of an internal combustion engine for an automobile, FIG. 2 is an enlarged sectional view of a differential mechanism and an actuator, and FIG. 3 is a structure of the differential mechanism. 2 is an enlarged view of part 4 of FIG. 3 showing the structure of the actuator, FIG. 5 is an enlarged view of part 5 of FIG. 3 showing the structure of the friction clutch, and FIG. 6 is a cross-sectional view taken along line 7-7 in FIG. 3 except for the pinion shaft, pinion and side gear, FIG. 8 is a cross-sectional view taken along line 8-8 in FIG. 3, and FIG. 9 is 9-9 in FIG. It is line sectional drawing.

  As shown in FIG. 1, an internal combustion engine E mounted horizontally on the front body of a front engine / front drive automobile has a transmission T integrally coupled to a left side surface thereof, and a difference between the rear surface of the transmission T and the rear surface thereof. A moving mechanism D is provided. A half shaft 11 (intermediate shaft) extends rightward from a differential mechanism D arranged to be shifted leftward from the vehicle body center line, and a right axle that drives a right drive wheel (not shown) to the halfshaft 11. 12 is connected, and a left drive wheel (not shown) is driven via a left axle 13 extending in the left direction from the differential mechanism D. The right end of the half shaft 11 is supported by a stay 10 fixed to the engine block 22.

  As is clear from FIG. 2, the housing 14 that houses the differential mechanism D covers the housing body 15 that is formed integrally with the casing of the transmission T and the left end opening of the housing body 15. And a cover plate 17 fixed by a plurality of bolts 16. A plurality of actuators A, which are separately attached to the right side of the differential mechanism D, are an actuator case 18 that fits into the right end opening of the housing body 15 of the differential mechanism D, and a plurality of actuators A so as to cover the right end opening of the actuator case 18. The actuator cover 20 is fixed by a plurality of bolts 19... And is fixed to the engine block 22 by a plurality of bolts 21 (see FIG. 1) penetrating the actuator case 18. The differential mechanism D and the actuator A constitute a differential device.

  The differential mechanism D housed in the housing 14 includes a first case 24 on the right side supported by the roller body 23 on the housing body 15 and a second case 26 on the left side supported by the roller bearing 25 on the cover plate 17. Are connected by a plurality of bolts 27..., And an axle drive gear 29 driven by a transmission T is fastened to the outer periphery of the first case 24 by the plurality of bolts 27. .

  Next, the structure of the differential mechanism D will be described with reference to FIGS. 3 and 5 to 8.

  The differential mechanism D housed in the housing 14 includes four pinion shafts 31 integrated so as to intersect in a cross shape. The pinion shafts 31 having a circular cross section are formed with chamfers 31a at the ends, and the chamfers 31a are formed in four pinion shaft support grooves 24a formed on the inner peripheral surface of the first case 24. Mating. Pinions 32 are rotatably supported on the four pinion shafts 31.

  The left end of the half shaft 11 inserted into the first case 24 is splined to the right side gear 34 </ b> R and is prevented from coming off by a set ring 35. The right end of the left axle 13 that passes through the second case 26 and is inserted into the first case 24 is splined to the left side gear 34L and is prevented from coming off by a set ring 38. The outer periphery of the side gear 34L The clutch inner 37 is fixed integrally. The left and right side gears 34L, 34R mesh with the four pinions 32, respectively.

  The rear surface of the right side gear 34R is in contact with four thrust support surfaces 24c... Projecting from the inner surface of the first case 24 via a thrust washer 50, and the rear surface of the left side gear 34L is formed on the inner surface of the second case 26. The annular thrust support surface 26 a is abutted through a thrust washer 51.

  A clutch outer 40 is integrally formed on the inner periphery of the first case 24 so as to face the outer periphery of the clutch inner 37, and a plurality of (four in the embodiment) clutch plates are formed on the inner peripheral surface of the clutch outer 40. The outer peripheral portions of 41... Are spline-fitted, and the inner peripheral portions of a plurality of (in the embodiment, five) clutch disks 42 are spline-fitted to the outer peripheral surface of the clutch inner 37. The clutch plates 41 and the clutch disks 42 are alternately arranged so that the friction materials 43 attached to both surfaces of the clutch disks 42 can come into contact with the clutch plates 41.

  The outer peripheral portion of the pressure plate 44 is spline-fitted to the inner peripheral surface of the clutch outer 40, and the left side surface of the pressure plate 44 is opposed to the right side surface of the clutch disk 42 located at the rightmost end. A plurality (four in the embodiment) of lever lever storage recesses 24b are formed on the inner surface of the first case 24 facing the right side surface of the pressure plate 44, and the lever lever storage recesses 24b are arranged at the radially outer ends. A fulcrum 45a of the lever lever 45 is supported in a swingable manner.

  Inside the actuator case 18, the first hollow shaft 47 is fitted on the outer periphery of the half shaft 11 via a needle bearing 46 so as to be relatively rotatable and axially movable. In the first case 24, the right end of the second hollow shaft 48 is engaged with the left end of the first hollow shaft 47 so as not to be relatively rotatable. The right half of the second hollow shaft 48 that engages with the first hollow shaft 47 is configured by a hollow shaft portion 48a, and the left half integrally connected to the shaft portion 48a has four at 90 ° intervals. It is comprised by the branched circular arc-shaped enlarged diameter part 48b ... and the linear press part 48c ... continuously connected to the front-end | tip of those enlarged diameter parts 48b ....

  On the inner peripheral surface of the first case 24, four guide grooves 24d, whose phases are shifted by 45 ° with respect to the four pinion shaft support grooves 24a, are formed. 2 The enlarged diameter portions 48b and the pressing portions 48c of the hollow shaft 48 are slidably guided. Between the four guide grooves 24d, four concave portions 24e (see FIG. 8) that are recessed radially inward are formed on the outer peripheral surface of the first case 24. The outer shape of the first case 24 is small at the position. The thrust support surface 24c for supporting the back surface of the right side gear 34R via the thrust washer 50 is provided by expanding the inner surface of the recess 24e inward.

  A protrusion 48d is formed at the tip of each pressing portion 48c of the second hollow shaft 48. By making this protrusion 48d face the radially inner end of the lever lever 45, the lever lever 45 from the lever lever housing recess 24b is formed. Is prevented from falling off. In addition to the fulcrum 45a located on the radially outer side, each lever lever 45 is located on the radially inner side and a force point 45b with which the tip of the pressing portion 48c abuts, and the pressure plate 44 located in the middle in the radial direction. And an action point 45c that comes into contact with the right side surface of the.

  Thus, the clutch inner 37, the clutch outer 40, the clutch plate 41, the clutch disk 42, the pressure plate 44, and the lever lever 45, constitute a friction clutch 52 for fastening the left axle 13 to the differential case 28. Is done.

  Next, the structure of the actuator A that engages the friction clutch 52 via the first and second hollow shafts 47 and 48 will be described with reference to FIGS. 2, 4, and 9.

  A first spring guide 61 is fitted on the outer periphery on the right end side of the first hollow shaft 47 extending inside the actuator case 18 and is fixed by a set ring 62, and the outer periphery of the first hollow shaft 47 on the right side of the first spring guide 61. The second spring guide 63 is spline-fitted. A return spring 64 made of a coil spring is disposed between the first and second spring guides 61 and 63 in a compressed state, and the second spring guide 63 is urged rightward by its elastic force.

  A cam cylinder 65 is fitted to the outer periphery of the half shaft 11, and a flange 65 a provided at the right end thereof is fixed to the actuator cover 20 by a knock pin 66. A first cam plate 67 and a second cam plate 68 are supported on the outer periphery of the cam cylinder 65 via needle bearings 69 and 70 so as to be rotatable and axially movable. The first cam plate 67 contacts the flange 63 a of the second spring guide 63 via the thrust bearing 85, and the second cam plate 68 contacts the flange 65 a of the cam cylinder 65 via the thrust bearing 86. Inclined cam grooves 67a..., 68a... Are formed on the opposing surfaces of the first and second cam plates 67 and 68, and the balls 71 are accommodated in the cam grooves 67a. The first and second cam plates 67 and 68 and the balls 71 constitute a ball cam mechanism 72.

  The first shaft 73 is supported on the actuator case 18 and the actuator cover 20 via a pair of ball bearings 74 and 75, and the second shaft 76 is supported via a pair of ball bearings 77 and 78. Of the second and third gears 81, 82 provided on the second shaft 76, the first gear 80 provided on the first shaft 73 connected in series to the output shaft 79 a of the motor 79 supported on the actuator case 18. Mesh with the second gear 81. In addition, fourth and fifth gears 83 and 84 are formed on the outer circumferences of the first and second cam plates 67 and 68, respectively. The fourth gear 83 meshes with the second gear 81 of the second shaft 76, and The fifth gear 84 meshes with the third gear 82 of the second shaft 76. The gear ratio between the second gear 81 and the fourth gear 83 and the gear ratio between the third gear 82 and the fifth gear 84 are slightly different.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  The differential mechanism D exhibits a differential limiting function in addition to the normal differential function, and the differential limiting torque generated by the differential limiting function is generated by the operation of the actuator A.

  First, the normal differential function of the differential mechanism D will be described.

  When the driving force of the internal combustion engine E is input to the axle drive gear 29 of the differential mechanism D via the transmission T, the differential case 28 coupled to the axle drive gear 29 with bolts 27 ... rotates. When the vehicle is in a straight traveling state, the four pinions 32 are not rotated with respect to the pinion shafts 31 and are not rotated with respect to the pinions 32, but the left side gear 34L meshed with the pinions 32 and the right axle meshed with the left axle 13 and the pinions 32. The side gear 34R and the integral half shaft 11 rotate at the same speed, and the driving force is evenly distributed to the left and right driving wheels.

  For example, when the vehicle is in a left turn state, the left axle 13 connected to the left drive wheel is decelerated and the half shaft 11 connected to the right drive wheel is accelerated, so that a differential rotation occurs between the left and right side gears 34L and 34R. Although generated, the differential rotation is absorbed by the rotation of the pinions 32 meshed with the left and right side gears 34L, 34R. Similarly, when the vehicle is in a right turn state, the left axle 13 connected to the left drive wheel is accelerated and the half shaft 11 connected to the right drive wheel is decelerated, so that the difference between the left and right side gears 34L and 34R. Although rotation occurs, the differential rotation is absorbed by the rotation of the pinions 32 meshed with the left and right side gears 34L, 34R.

  Next, the differential limiting function generated by the operation of the actuator A will be described.

  When the motor 79 of the actuator A is driven, the rotation of the first gear 80 of the first shaft 73 coupled to the output shaft 79a is transmitted to the second gear 81 and the second shaft 76 rotates. When the second shaft 76 rotates, the first cam plate 67 rotates through the second gear 81 and the fourth gear 83, and the second cam plate 68 rotates through the third gear 82 and the fifth gear 84. However, since the gear ratio between the second gear 81 and the fourth gear 83 and the gear ratio between the third gear 82 and the fifth gear 84 are slightly different, the first and second cam plates of the ball cam mechanism 72 are different. 67 and 68 rotate relative to each other. As a result, the relative positions of the cam grooves 67a ... 68a ... of the first and second cam plates 67, 68 change from the state shown in FIG. 9A to the state shown in FIG. 1. The second cam plates 67 and 68 are driven in directions away from each other.

  The second cam plate 68 that has received a rightward load generated by the ball cam mechanism 72 is prevented from moving rightward by the actuator cover 20. Accordingly, the first cam plate 67 that has received the leftward load generated by the ball cam mechanism 72, that is, the engaging force for engaging the friction clutch 52, moves to the left, and the thrust bearing 85, the second spring guide 63, the first The first hollow shaft 47 is pressed leftward through the spring guide 61 and the set ring 62.

  When a leftward engagement force is applied to the first hollow shaft 47 by the actuator A, the second hollow shaft 48 coupled to the first hollow shaft 47 moves in the left direction, and the four pieces provided at the left end of the second hollow shaft 48 are provided. Of the four lever levers 45 press the force points 45b of the four lever levers 45. As a result, the lever levers 45 swing around the fulcrum 45a, and the action point 45c presses the pressure plate 44 to the left, so that the clutch plates 41 and the clutch disks 42 are in close contact with each other, and the clutch The inner 37 and the clutch outer 40 are coupled together.

  Since the distance L1 between the fulcrum 45a and the force point 45b of the lever lever 45 is set larger than the distance L2 between the fulcrum 45a and the action point 45c, the engagement force F1 input to the lever lever 45 is doubled by L1 / L2. The pressure plate 44 can be pressed by the doubled engagement force F2, and thus a sufficient engagement force can be applied to the friction clutch 52 even if the motor 79 of the actuator A is downsized.

  When the friction clutch 52 is engaged in this way, the left axle 13 integrated with the clutch inner 37 is integrated with the differential case 28, so that the left axle 13 and the half shaft 11, that is, the left axle 13 and the right axle. 12 is integrated so as not to rotate relative to each other, and the differential function of the differential mechanism D is limited, so that it is possible to escape from soft ground such as muddy, and stability during high-speed straight running can be improved. . At this time, by controlling the current that drives the motor 79 to change the engagement force generated by the actuator A and causing the friction clutch 52 to generate a predetermined slip, the differential mechanism D has a differential limit of an arbitrary magnitude. Torque can be demonstrated.

  As described above, the engaging force of the friction clutch 52 generated by the actuator A can be axially moved to the outer periphery of the half shaft 11 without relative to the half shaft 11 to which the driving force of the internal combustion engine E is transmitted, and is relatively rotated. Since transmission is performed via the first and second hollow shafts 47 and 48 that can be arranged, the actuator A is generated by the frictional force generated at the spline coupling portion of the half shaft 11 by transmitting the driving force of the internal combustion engine E. The engaging force to be applied is not reduced, and the friction clutch 52 can be stably engaged.

  The first and second hollow shafts 47 and 48 rotate together with the differential case 28. However, since the rotation is idling without transmission of the driving force of the internal combustion engine E, a large frictional force is generated when moving in the axial direction. Never do.

  Thus, the diameter-enlarged portion 48b of the second hollow shaft 48 that transmits the engagement force of the friction clutch 52 generated by the actuator A is formed so as to branch into four from the shaft portion 48a. The weight of the second hollow shaft 48 can be reduced as compared with the case where it is formed in an annular shape. Further, the first case 24 of the differential case 28 is recessed toward the space formed between the adjacent enlarged diameter portions 48b to form the recesses 24e, so that the first case 24 is reduced in size and further weight reduction is achieved. Can be achieved. Further, the thrust support surface 24c of the first case 24 that supports the thrust force of the right side gear 34R is disposed in a space formed between the adjacent enlarged diameter portions 48b, so that the thrust support surface is provided on the enlarged diameter portion. It is not necessary to form a through hole for penetrating 24c ..., and the structure of the second hollow shaft 48 can be simplified.

  Further, since the guide groove 24d formed on the inner surface of the first case 24 guides the enlarged diameter portion 48b and the pressing portion 48c of the second hollow shaft 48, the enlarged diameter portion 48b and the pressing portion 48c are used to reduce the weight. .., Even when the frictional clutch 52 is engaged, the diameter-enlarged portion 48b and the pressing portion 48c are prevented from bending outward in the radial direction, and the friction clutch 52 is securely engaged. Can be combined.

  As mentioned above, although embodiment of this invention was explained in full detail, this invention can perform a various design change in the range which does not deviate from the summary.

  For example, the actuator A is not limited to an electric type, and a hydraulic actuator may be employed.

  In the embodiment, the hollow shaft is divided into the first and second hollow shafts 47 and 48. However, a single hollow shaft or three or more hollow shafts can be employed.

  In the embodiment, the guide groove 24d of the first case 24 guides both the enlarged diameter portion 48b and the pressing portion 48c of the second hollow shaft 48, but the guide groove 24d is at least the pressing portion 48c. Anything that guides you.

  In the embodiment, the number of the enlarged diameter portions 48b and the pressing portions 48c of the second hollow shaft 48 is four, but the number can be arbitrarily set as long as it is plural.

Rear view of automotive internal combustion engine Enlarged sectional view of differential mechanism and actuator 2 is an enlarged view of part 3 of FIG. 2 showing the structure of the differential mechanism. 4 is an enlarged view of part 4 in FIG. 3 showing the structure of the actuator. FIG. 3 is an enlarged view of part 5 showing the structure of the friction clutch. 6-6 sectional view of FIG. The figure which excluded the pinion shaft, the pinion, and the side gear in the 7-7 line cross section of FIG. Sectional view taken along line 8-8 in FIG. Sectional view along line 9-9 in FIG.

Explanation of symbols

11 Half shaft (output shaft)
13 Left axle (output shaft)
24c Thrust support surface 24d Guide groove (guide part)
28 Differential case 31 Pinion shaft 32 Pinion 34R Side gear 48 Second hollow shaft (hollow shaft)
48a Shaft portion 48b Expanded diameter portion 48c Pressing portion 52 Friction clutch A Actuator D Differential mechanism E Internal combustion engine (prime mover)

Claims (3)

A differential mechanism (D) that distributes and outputs the driving force of the prime mover (E) input to the differential case (28) to the two output shafts (11, 13);
A friction clutch (52) located on one side with respect to the pinion shaft (31) of the differential mechanism (D) and limiting differential rotation between the two output shafts (11, 13);
An actuator (A) that is positioned on the output shaft (11) on the other side of the pinion shaft (31) outside the differential case (28) and that generates an engaging force for engaging the friction clutch (52);
A hollow shaft (48) for transmitting the engagement force generated by the actuator (A) to the friction clutch (52);
In a differential device with a differential limiting mechanism comprising:
The hollow shaft (48) includes a shaft portion (48a) extending from the actuator (A) to the inside of the differential case (28) on the outer periphery of the output shaft (11) on the other side, and a shaft portion in the differential case (28). (48a) branch from the end portion in the circumferential direction with a plurality of diameter-expanded portions (48b) that expand along the inner surface of the differential case (28), and extend from each diameter-expanded portion (48b). And a plurality of pressing portions (48c) extending through the side of the pinion (32) on the pinion shaft (31) and extending to the friction clutch (52). .   The enlarged diameter portion (48b) and the pressing portion (48c) are integrally formed, and the inner surface of the differential case (28) facing the pressing portion (48c) is prevented from being deformed radially outward. The differential device with a differential limiting mechanism according to claim 1, further comprising a guide portion (24d).   A thrust support surface (24c) is formed by bulging the inner surface of the differential case (28) facing the space formed between the enlarged diameter portions (48b) toward the side gear (34R) side of the differential mechanism (D). The differential device with a differential limiting mechanism according to claim 1 or 2, wherein the thrust force of the side gear (34R) is supported by the thrust support surface (24c).

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