JP2016173119A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a power transmission device which has a ring gear supporting structure of a new structure having little problem, in which an increase in a number of components can be suppressed and a planetary gear can be configured in smaller size in an axial direction.SOLUTION: A power transmission device is equipped with, for example, a case; a planetary gear mechanism which has a sun gear, a ring gear stored in the case and formed in a cylindrical shape positioned on the outside in a diametrical direction of the sun gear, a pinion gear positioned between the sun gear and the ring gear and transmitting power between the sun gear and the ring gear, and a carrier rotatably supporting the pinion gear; a first supporting portion which supports an end portion on one side in an axial direction of the ring gear; and a second supporting portion which supports an end portion on the other side in the axial direction of the ring gear. The first supporting portion is provided on the carrier, and a washer interposed between the carrier and the pinion gear is interposed between the first supporting portion and the end portion on the one side in the axial direction of the ring gear.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a power transmission device.

  Conventionally, there has been known a power transmission device in which a ring gear of a planetary gear mechanism is supported by one and the other in the axial direction at a position away from the teeth of the ring gear via a portion extending in the radial direction on one side in the axial direction. It has been.

JP 2010-112529 A

  In the above prior art, the ring gear is supported at a position away from the ring gear teeth through a portion extending radially inward from the ring gear teeth on one side in the axial direction. There is a concern that the planetary gear may become larger in the axial direction due to the portion extending to.

  Accordingly, one of the problems of the present invention is to obtain a power transmission device having a ring gear support structure with a new configuration with less inconvenience, such as, for example, suppressing an increase in the number of parts and making the planetary gear smaller in the axial direction. That is.

  The power transmission device of the present invention includes, for example, a case, a sun gear, a cylindrical ring gear that is positioned outside in the radial direction of the sun gear, the sun gear, and the ring gear. A planetary gear mechanism having a pinion gear that is located between the sun gear and the ring gear and transmits a power between the sun gear and a carrier that rotatably supports the pinion gear; and an end of one side of the ring gear in the axial direction And a second support part for supporting the other end part in the axial direction of the ring gear, and the first support part is provided on the carrier, A washer interposed between the carrier and the pinion gear is interposed between the first support portion and one end portion in the axial direction of the ring gear.

  Therefore, according to the present invention, for example, compared to a configuration in which a portion extending long toward the bearing is provided so as to support the ring gear only on one side in the axial direction, the long extending portion can be shortened, or Therefore, the power transmission device can be made smaller in the axial direction. Further, for example, an increase in the number of parts can be suppressed as compared with a configuration in which bearings are separately provided for the pinion gear and the ring gear.

  In the power transmission device, the planetary gear mechanism has a plurality of pinion gears, and the washer is shared by the plurality of pinion gears. Therefore, for example, an increase in the number of parts can be suppressed as compared with a case where washers are separately provided with a plurality of pinion gears.

  Further, the power transmission device includes a movable part that suppresses rotation of the rotating element housed in the case, a piston that is driven by hydraulic pressure to move the movable part, a return spring that applies a reaction force to the piston, A brake having a support member interposed between the return spring and the case and supporting the return spring is provided, and the second support portion is provided on the support member. Therefore, since the second support portion can be provided on the support member of the brake that is provided in the case and is positioned relatively close to the ring gear that is located on the radially outer side of the planetary gear mechanism, for example, the axial direction of the ring gear The configuration that supports the other side of this is likely to be smaller.

  In the power transmission device, the second support portion is provided in the case. Therefore, since the second support portion can be provided in a portion of the case that is located relatively close to the ring gear, for example, the configuration for supporting the other side in the axial direction of the ring gear tends to be smaller.

FIG. 1 is a schematic and exemplary configuration diagram of a power transmission device according to an embodiment. FIG. 2 is a schematic and exemplary cross-sectional view of a portion including the planetary gear mechanism of the power transmission device of the first embodiment. FIG. 3 is a schematic and exemplary view of the carrier of the planetary gear mechanism included in the power transmission device of the first embodiment viewed from the axial direction. FIG. 4 is a schematic and exemplary view of the carrier of the planetary gear mechanism included in the power transmission device of the first modification of the first embodiment as viewed from the axial direction. FIG. 5 is a schematic and exemplary cross-sectional view of a portion including a planetary gear mechanism of a power transmission device according to a second modification of the first embodiment. FIG. 6 is a schematic and exemplary cross-sectional view of a portion including the planetary gear mechanism of the power transmission device of the second embodiment.

  Hereinafter, exemplary embodiments of the present invention are disclosed. The configuration of the embodiment shown below, and the operation and result (effect) brought about by the configuration are examples. The present invention can be realized by configurations other than those disclosed in the following embodiments. Further, according to the present invention, it is possible to obtain at least one of various effects (including derivative effects) obtained by these configurations.

  Moreover, the same component is contained in embodiment and the modified example which are disclosed below. In the following, common reference numerals are given to the same components, and redundant description is omitted. In this embodiment, the left side in FIGS. 2, 5 and 6 is defined as the other side in the axial direction, and the right side in the same figure is defined as one side in the axial direction. The left side may be one side in the axial direction, and the right side in the figure may be the other side in the axial direction.

<First Embodiment>
A power transmission device 20 shown in FIG. 1 is a transaxle connected to an engine (not shown), and includes a transmission case 22, a fluid transmission device 23, an oil pump 30, a forward / reverse switching mechanism 35, a CVT 40 (continuously variable). transmission), a hydraulic control device (not shown), a gear mechanism 80, a differential gear (differential mechanism) 88, and the like. The transmission case 22 includes a converter housing 22a, a transaxle case 22b, a rear cover 22c, and the like that are integrally coupled to each other.

  A fluid transmission device 23 is accommodated in the transmission case 22. The fluid transmission device 23 is accommodated in the converter housing 22a. As shown in FIG. 1, the fluid transmission device 23 includes a pump impeller 23p, a turbine runner 23t, a stator 23s, a one-way clutch 23o, a damper mechanism 24, a lockup clutch 25, and the like. The pump impeller 23p is connected to the crankshaft of the engine via a front cover 21 as an input member. The turbine runner 23t is fixed to the input shaft 41 of the CVT 40. The stator 23s is arranged inside the pump impeller 23p and the turbine runner 23t, and regulates the flow of hydraulic oil (ATF) from the turbine runner 23t to the pump impeller 23p. The one-way clutch 23o limits the rotation direction of the stator 23s to one direction.

  The pump impeller 23p, the turbine runner 23t, and the stator 23s function as a torque amplifier (torque converter) by the action of the stator 23s when the rotational speed difference between the pump impeller 23p and the turbine runner 23t is large. The pump impeller 23p, the turbine runner 23t, and the stator 23s function as a fluid coupling when the rotational speed difference between them is small. However, in the fluid transmission device 23, the stator 23s and the one-way clutch 23o may be omitted, and the pump impeller 23p and the turbine runner 23t may be configured to function only as a fluid coupling. The damper mechanism 24 includes, for example, an input element coupled to the lockup clutch 25, an intermediate element coupled to the input element via the plurality of first elastic bodies, and an intermediate element coupled to the plurality of second elastic bodies. Output elements connected to the. The output element is fixed to the turbine hub.

  The lockup clutch 25 can selectively switch between a lockup state (connection state) and a release state (blocking state) in which the lockup state is released. In the lock-up state, the pump impeller 23p and the turbine runner 23t, that is, the front cover 21 and the input shaft 41 of the CVT 40 are mechanically coupled (via the damper mechanism 24). When a predetermined condition is satisfied after the engine is started and the automobile starts, the lock-up clutch 25 locks (directly connects) the pump impeller 23p and the turbine runner 23t (lock-up state). In the lockup state, power from the engine is mechanically and directly transmitted to the input shaft 41. The lock-up clutch 25 may be configured as a hydraulic single-plate friction clutch, or may be configured as a hydraulic multi-plate friction clutch.

  The oil pump 30 is configured as a so-called gear pump (trochoid pump) including a pump case, an external gear 33, and an internal gear 34. The pump case includes a pump body 31 and a pump cover 32. The pump body 31 and the pump cover 32 are located between the fluid transmission device 23 and the forward / reverse switching mechanism 35. The external gear 33 is an inner rotor having a plurality of external teeth. The internal gear 34 is an outer rotor that is arranged eccentrically with the external gear 33 and has internal teeth that mesh with the external gear 33. When the external gear 33 is rotated by the power of the engine, the oil pump 30 sucks the hydraulic oil (ATF) stored in an oil pan (not shown) through a strainer (not shown) and discharges the hydraulic oil. The operation of the oil pump 30 supplies hydraulic oil to each part and obtains a required hydraulic pressure.

  The forward / reverse switching mechanism 35 includes a planetary gear mechanism 10, a brake B1, a clutch C1, and the like. The planetary gear mechanism 10 is accommodated in a transaxle case 22b (case).

  As shown in FIG. 2, the planetary gear mechanism 10 includes a sun gear 11, a ring gear 12, a pinion gear 13, a carrier 14, and the like as rotating elements. The sun gear 11, the ring gear 12, and the carrier 14 are all supported so as to be rotatable around the rotation center Ax (FIG. 1). Therefore, the radial direction of the rotation center Ax is the radial direction of the sun gear 11, the ring gear 12, and the carrier 14, and the axial direction of the rotation center Ax is the axial direction of the sun gear 11, the ring gear 12, and the carrier 14. The sun gear 11 is connected to the input shaft 41 of the CVT 40, and the sun gear 11 and the input shaft 41 rotate integrally. The ring gear 12 is located outside the sun gear 11 in the radial direction. As shown in FIG. 3, three double pinions 15 (gear sets) are provided between the sun gear 11 and the ring gear 12. The double pinions 15 are arranged at three locations distributed 120 ° each when viewed from the axial direction. The double pinion 15 has two pinion gears 13 that mesh with each other. One pinion gear 13 meshes with the sun gear 11 and the other pinion gear 13 meshes with the ring gear 12. That is, the pinion gear 13 is configured to transmit power (torque, rotation) between the sun gear 11 and the ring gear 12. The carrier 14 rotatably supports three double pinions 15, that is, six pinion gears 13. The carrier 14 rotates according to the rotation around the rotation center Ax of the double pinion 15. The carrier 14 is connected to the primary shaft 42 of the CVT 40, and the carrier 14 and the primary shaft 42 rotate integrally. The ring gear 12 includes a cylindrical ring portion 12a and a tooth portion 12b provided on a radially inner surface of the ring portion 12a. The ring portion 12a can also be referred to as a base portion.

  The brake B1 shown in FIGS. 1 and 2 includes a state in which the ring gear 12 of the planetary gear mechanism 10 and the transaxle case 22b are connected (connected state), and a state in which the ring gear 12 and the transaxle case 22b are disconnected (blocked). Switch between (status). As shown in FIG. 2, the brake B <b> 1 has annular disks 91 and 92 that are alternately stacked in the axial direction. The disc 91 is supported by the transaxle case 22b so as to be movable in the axial direction and is immovably supported in the circumferential direction. The disk 92 is supported by the ring gear 12 so as to be movable in the axial direction and is immovable in the circumferential direction. That is, the disk 92 rotates integrally with the ring gear 12. A push member 93 is provided on the other side (left side in FIG. 2) of the disks 91 and 92 in the axial direction. A receiving member 94 is provided on one side (the right side in FIG. 2) of the disks 91 and 92 in the axial direction. The pressing member 93 is supported by the transaxle case 22b so as to be movable in the axial direction. The receiving member 94 is fixed to the transaxle case 22b at least in the axial direction. In such a configuration, when the pressing member 93 or the disk 91 located on the other side in the axial direction (left side in FIG. 2) is pushed by the actuator and moves to one side in the axial direction (right side in FIG. 2), the disk 91 And the disk 92 overlap each other and come into close contact with each other, and the frictional force acting between the adjacent disks 91 and 92 makes the disk 91 and the disk 92 relatively unrotatable. In this state, the ring gear 12 and the transaxle case 22b are connected, and the rotation of the ring gear 12 is stopped. On the other hand, when the state where the push member 93 or the disk 91 located on the other side in the axial direction (the left side in FIG. 2) moves to the other side in the axial direction is eliminated, the state where the disk 91 and the disk 92 are in close contact with each other is eliminated. The ring gear 12 is in a rotatable state (blocking state). The pressing member 93 and the disks 91 and 92 are an example of a movable part. The pressing member 93 can be omitted.

  The brake B1 includes an actuator 95 that hydraulically drives the disks 91 and 92 (the pressing member 93). The actuator 95 includes a piston 96, a return spring 97, and a support member 98. The piston 96 is movably accommodated in a cylinder 99 provided in the transaxle case 22b. The cylinder 99 is configured as an annular recess extending in the axial direction. The piston 96 has an annular shape and is accommodated in the cylinder 99 so as to be movable in the axial direction. A seal member 96 a such as an O-ring is attached to the piston 96. The seal member 96a seals between the piston 96 and the cylinder 99. An oil chamber 99a into which hydraulic oil having a required pressure is introduced is provided on the other side in the axial direction of the piston 96 in the cylinder 99 (left side in FIG. 2). When the required pressure of the hydraulic oil in the oil chamber 99a is applied to the piston 96, the piston 96 moves to one side in the axial direction (right side in FIG. 2) against an elastic reaction force by the return spring 97. . The piston 96 moves the push member 93 or the disk 91 located on the most other axial side (left side in FIG. 2) to one axial side (right side in FIG. 2) via an arm portion (not shown), The disc 91 and the disc 92 are brought into close contact with each other. As a result, the ring gear 12 and the transaxle case 22b are connected to each other, and the rotation of the ring gear 12 is stopped. On the other hand, when the pressure in the oil chamber 99a falls below the required pressure, the piston 96 is pushed to the other side in the axial direction (left side in FIG. 2) by the return spring 97. As a result, the state in which the push member 93 or the disk 91 located on the other side in the axial direction (the left side in FIG. 2) is moved to the other side in the axial direction is eliminated, and as a result, the ring gear 12 is rotatable (blocking state). It becomes.

  The return spring 97 is a coil spring that is elastically compressed in the axial direction. The return spring 97 is supported in the axial direction by a support member 98 positioned on one side (right side in FIG. 2) of the return spring 97 in the axial direction. The support member 98 has an annular shape and a plate shape. In the present embodiment, the return spring 97 applies an elastic force to the piston 96 on the other side in the axial direction (left side in FIG. 2), while on the one side in the axial direction (right side in FIG. 2) on the support member 98. An elastic force is applied. In the present embodiment, as an example, a radially outer edge of a fastener 98b such as a C-ring of the support member 98 is inserted and fixed in a groove provided in the transaxle case 22b. Is supported by the transaxle case 22b. That is, the return spring 97 is supported by the transaxle case 22b through the support member 98 and the fastener 98b.

  The clutch C1 switches between a state where the carrier 14 and the input shaft 41 (sun gear 11) of the planetary gear mechanism 10 are connected and a state where the carrier 14 and the input shaft 41 are disconnected.

  In the present embodiment, the rotation transmission state can be switched as follows by the operation of the brake B1 and the clutch C1. That is, by disconnecting the brake B1 and connecting the clutch C1, the power transmitted to the input shaft 41 can be transmitted to the primary shaft 42 of the CVT 40 as it is. On the other hand, by connecting the brake B1 and disconnecting the clutch C1, the rotation of the input shaft 41 can be converted to the reverse rotation direction and transmitted to the primary shaft 42 of the CVT 40. In this case, the car moves backward. Also, by disconnecting both the brake B1 and the clutch C1, the connection between the input shaft 41 and the primary shaft 42 can be disconnected.

  The CVT 40 includes a primary pulley 43, a secondary pulley 45, a belt 46, a primary cylinder 47, and a secondary cylinder 48. The primary pulley 43 is provided on a primary shaft 42 as a drive side rotation shaft. The secondary pulley 45 is provided on a secondary shaft 44 serving as a driven side rotation shaft disposed in parallel with the primary shaft 42. The belt 46 is stretched over the groove of the primary pulley 43 and the groove of the secondary pulley 45. The primary cylinder 47 is a hydraulic actuator for changing the groove width of the primary pulley 43. The secondary cylinder 48 is a hydraulic actuator for changing the groove width of the secondary pulley 45.

  The primary pulley 43 includes a fixed sheave 43a and a movable sheave 43b. The fixed sheave 43 a is provided integrally with the primary shaft 42. The movable sheave 43b is supported by the primary shaft 42 so as to be slidable in the axial direction via a ball spline. The secondary pulley 45 includes a fixed sheave 45a and a movable sheave 45b. The fixed sheave 45 a is provided integrally with the secondary shaft 44. The movable sheave 45b is supported by the secondary shaft 44 through a ball spline so as to be slidable in the axial direction. The movable sheave 45b is elastically pressed in the axial direction by a return spring 49 that is a compression spring.

  The primary cylinder 47 is provided behind the movable sheave 43 b of the primary pulley 43, and the secondary cylinder 48 is provided behind the movable sheave 45 b of the secondary pulley 45. Hydraulic pressure is applied to the primary cylinder 47 and the secondary cylinder 48 to change the groove width between the primary pulley 43 and the secondary pulley 45. As a result, the CVT 40 can steplessly shift the power transmitted from the engine to the primary shaft 42 via the fluid transmission device 23 and the forward / reverse switching mechanism 35 and output it to the secondary shaft 44. The power output to the secondary shaft 44 is transmitted to the left and right drive wheels via the gear mechanism 80, the differential gear 88, and the axle 89.

  The gear mechanism 80 extends in parallel with the secondary shaft 44 and the axle 89 while being rotatably supported by the transaxle case 22b via a bearing and is supported by the transaxle case 22b via a bearing. A counter shaft 82 supported by the counter shaft 82, a counter driven gear 83 fixed to the counter shaft 82 and meshing with the counter drive gear 81, and a drive pinion gear 84 (final drive gear) formed (or fixed) on the counter shaft 82. , And a differential ring gear 85 (final driven gear) that meshes with the drive pinion gear 84 and is connected to the differential gear 88.

  In the present embodiment, both ends in the axial direction of the ring gear 12 are supported in the axial direction by two members different from the ring gear 12. One of the two members is positioned on one side in the axial direction of the ring portion 12a of the ring gear 12, and supports one end in the axial direction of the ring portion 12a of the ring gear 12 in the axial direction. The other of the two members is located on the other side in the axial direction of the ring portion 12a of the ring gear 12, and supports the end portion on the other side in the axial direction of the ring portion 12a of the ring gear 12 in the axial direction. . The axial support does not mean a state in which the ring gear 12 and the two members are always in contact with each other, and there is a gap in the axial direction between the ring gear 12 and at least one of the two members. Is provided. The movement of the ring gear 12 in the axial direction is limited by each of the two members.

  As illustrated in FIG. 2, in the present embodiment, the other axial side (the left side in FIG. 2) of the ring portion 12 a of the ring gear 12 is supported by the support member 98 of the brake B <b> 1. The support member 98 is an example of a member that supports the other end portion of the ring gear 12 in the axial direction in the axial direction, and the wall portion 98a that is positioned on the radially inner side of the support member 98 is a second support member. It is an example of a part.

  Here, the force applied to the support member 98 by the return spring 97 is set to be larger than the maximum value of the axial force acting on the support member 98 from the ring gear 12. The axial force of the ring gear 12 is maximized when the engine output torque is maximum. In the case where the ring gear 12 is a helical tooth, the maximum value of the axial force acting on the support member 98 from the ring gear 12 is a value corresponding to the torsion angle and the maximum torque.

  On the other hand, one side (the right side in FIG. 2) of the ring portion 12 a of the ring gear 12 in the axial direction is supported by the carrier 14. The carrier 14 includes a ring-shaped member 14a, a flange portion 14b, and a shaft 14c. The ring-shaped member 14a is located on one side in the axial direction of the pinion gear 13, and is formed in an annular shape and a plate shape. The flange portion 14b is positioned on the other side in the axial direction of the pinion gear 13, and extends from the primary shaft 42 in a plate shape outward in the radial direction. The shaft 14c extends in the axial direction at a position radially away from the rotation center Ax (FIG. 1) and connects the ring-shaped member 14a and the flange portion 14b. The shaft 14c rotatably supports the pinion gear 13 via a bearing 14d (radial bearing).

  As shown in FIG. 3, the ring-shaped member 14a has an annular base portion 14e and a protruding portion 14f that protrudes radially outward from the base portion 14e. The protruding portion 14f extends radially outward from the base portion 14e at a position where the pinion gear 13 (double pinion 15) is provided. As shown in FIG. 2, the end portion on one side (right side in FIG. 2) of the ring gear 12 in the axial direction is supported by the protrusion 14f. The carrier 14 (ring-shaped member 14a) is an example of a member that supports one end of the ring gear 12 in the axial direction in the axial direction, and the protrusion 14f is an example of a first support portion.

  As shown in FIG. 2, the carrier 14 supports the disk 100a of the clutch C1 so as to be movable in the axial direction. That is, the carrier 14 has a cylindrical portion 14g that supports the disk 100a. The cylindrical portion 14g is configured as a member (second member) different from the member (first member) having the base portion 14e and the protruding portion 14f, and the first member and the second member are They are integrated by being welded to each other at the welding position W. The first member and the second member may be integrated by means other than welding, such as being coupled by a coupling tool such as a screw.

  Further, there is a difference in rotational speed between the ring gear 12 and a member that supports the ring gear 12 in the axial direction. Therefore, in the present embodiment, a bearing (thrust bearing) is interposed between the ring gear 12 and a member that supports the ring gear 12 in the axial direction. In the example of FIG. 2, a washer 16 is provided as a bearing between the ring gear 12 and the support member 98 on the other axial side of the ring gear 12 (left side of FIG. 2). For example, the washer 16 is formed in an annular and plate shape with a material having relatively high wear resistance. In the present embodiment, the washer 16 is bent at the radially inner portion in the axial direction and supported by the ring gear 12. The washer 16 may be attached to the support member 98, or the support member 98 may be used as a washer by forming at least a part of the support member 98 from a material with high wear resistance.

  On the other hand, on one side of the ring gear 12 in the axial direction (the right side in FIG. 2), a washer 17 is provided as a bearing between the ring gear 12 and the carrier 14. The washer 17 is configured in a plate shape with a material having relatively high wear resistance, for example. The washer 17 is also interposed between the pinion gear 13 and the base portion 14 e of the carrier 14. That is, the washer 17 is shared between the carrier 14 and the pinion gear 13 and between the carrier 14 and the ring gear 12. Specifically, the washer 17 has a first portion 17 a positioned between the carrier 14 and the pinion gear 13, and a second portion 17 b positioned between the carrier 14 and the ring gear 12. Yes. Instead of providing the bearings, the surfaces facing each other in the axial direction may be subjected to a surface treatment that increases wear resistance, such as plating or nitriding.

  As described above, in the present embodiment, the ring gear 12 (the ring portion 12a) has a ring gear in which one end and the other end in the axial direction are members (different members) different from the ring gear 12, respectively. The 12 ring portions 12a are supported by portions located on one side and the other side in the axial direction. Therefore, according to the present embodiment, for example, compared to a configuration in which a portion extending in the radial direction toward the bearing is provided so as to support the ring gear only on one side in the axial direction, Since the power transmission device 20 can be shortened or omitted, the power transmission device 20 can be configured to be smaller in the axial direction. In addition, thereby, for example, effects such as reduction in the number of parts, labor and cost for manufacturing parts, and weight reduction can be easily obtained.

  Further, in the present embodiment, the other end portion in the axial direction of the ring gear 12 is supported by the wall portion 98a (second support portion) of the support member 98 used in the brake B1 as a member different from the ring gear 12. ing. Therefore, according to the present embodiment, for example, the second support member 98 of the brake B1 is provided in the transaxle case 22b and is located relatively close to the ring gear 12 located on the outer side in the radial direction of the planetary gear mechanism 10. Therefore, the configuration for supporting the other side of the ring gear 12 in the axial direction is likely to be smaller.

  In the present embodiment, the end of one side in the axial direction of the ring gear 12 is supported by the projecting portion 14 f (first support portion) of the carrier 14 as a member different from the ring gear 12. Therefore, according to the present embodiment, for example, the first support portion can be provided on the carrier 14 adjacent to the ring gear 12, so that the configuration for supporting one side of the ring gear 12 in the axial direction is likely to be smaller.

  In the present embodiment, the washer 17 is interposed between the carrier 14 and the pinion gear 13, and is interposed between the carrier 14 and the ring gear 12. That is, the washer 17 functions as an axial bearing with the pinion gear 13 and also functions as an axial bearing with the ring gear 12. Therefore, according to the present embodiment, for example, the number of parts can be reduced as compared with the case where the pinion gear 13 and the ring gear 12 are provided with bearings separately. Therefore, for example, labor and cost for manufacturing parts are likely to be reduced.

<First Modification of First Embodiment>
Further, as in the first modification of the first embodiment illustrated in FIG. 4, the washer 17 can be shared by a plurality of double pinions 15 (pinion gear 13, gear set). Specifically, the washer 17 has a first portion 17a provided in an annular and plate shape, and a plate-like second portion 17b projecting radially outward from the first portion 17a. ing. The first portion 17a can also be referred to as a base portion. The second portion 17b can also be referred to as a protruding portion. According to this second modification, the number of parts can be further reduced. Therefore, for example, the labor and cost for manufacturing the parts can be further reduced.

<Second Modification of First Embodiment>
Further, as in the second modification of the first embodiment illustrated in FIG. 5, a bearing 18 can be used instead of the washer 16. The bearing 18 is a needle bearing, for example. The bearing 18 is supported by the support member 98, for example. According to the second modification, for example, the wear resistance between the ring gear 12 and the support member 98 may be further improved. A bearing other than a needle bearing such as a ball bearing can also be used. A needle bearing or the like may be used instead of the washer 17 on one side in the axial direction.

Second Embodiment
The power transmission device 20A of this embodiment illustrated in FIG. 6 has the same configuration as the power transmission device 20 of the first embodiment. Therefore, according to this embodiment, the same effect based on the same configuration as that of the first embodiment can be obtained. However, in the present embodiment, the specific configuration for supporting the ring gear 12 in the axial direction is different from that of the first embodiment.

  First, in this embodiment, instead of the support member 98 of the brake B1, the protruding portion 22d provided on the transaxle case 22b serves as a second support portion that supports the other end portion in the axial direction of the ring gear 12. It is functioning. The protruding portion 22d protrudes from the transaxle case 22b toward one side in the axial direction. Between the protrusion 22d and the ring gear 12, an annular and plate-shaped washer 16A is provided as a bearing (thrust bearing). For example, the washer 16A is formed in an annular and plate shape with a material having relatively high wear resistance. In the present embodiment, the washer 16A has a radially inner portion bent in the axial direction and supported by the protruding portion 22d. Note that the washer 16 </ b> A may be attached to the ring gear 12. According to such a configuration, for example, since the second support portion can be provided in a portion of the transaxle case 22b that is located relatively close to the ring gear 12, the other side in the axial direction of the ring gear 12 can be provided. The configuration for supporting the end portion tends to be smaller.

  Moreover, in said 1st embodiment, the 1st member which has the base part 14e and the protrusion part 14f, and the 2nd member which has the cylindrical part 14g are integrated by welding etc., Therefore The ring-shaped member 14a which comprises the one side of an axial direction was comprised. On the other hand, in this embodiment, as shown in FIG. 6, the base part 14e and the cylindrical part 14g are comprised by one member. Further, at a position adjacent to the circumferential direction of the double pinion 15, a part of the cylindrical portion 14 g is separated and bent (cut and raised) outward in the radial direction to form a protruding portion 14 f. Thereby, for example, the ring-shaped member 14a of the carrier 14A having the base portion 14e, the protruding portion 14f, and the cylindrical portion 14g can be configured by one member. According to such a configuration, for example, labor and cost for manufacturing parts are likely to be reduced.

  As mentioned above, although embodiment of this invention was illustrated, the said embodiment is an example and is not intending limiting the range of invention. The embodiment can be implemented in various other forms, and various omissions, replacements, combinations, and changes can be made without departing from the scope of the invention. In addition, the configuration and shape of each example can be partially exchanged. In addition, the specifications (structure, type, direction, shape, size, length, width, height, number, arrangement, position, etc.) of each configuration and shape can be changed as appropriate. For example, the power transmission device according to the present embodiment is not a CVT, but may be another power transmission device having a planetary gear mechanism, for example, AT (automatic transmission), AMT (automated manual transmission), or the like. Further, the brake having the support member may be a rotating element other than the ring gear, for example, a sun gear or a carrier brake. The ring gear can also be supported by members other than those disclosed in the above embodiment.

  DESCRIPTION OF SYMBOLS 10 ... Planetary gear mechanism, 11 ... Sun gear (rotating element), 12 ... Ring gear (rotating element), 12a ... Ring part, 13 ... Pinion gear, 14, 14A ... Carrier (rotating element), 14f ... Projection part (first support) Part), 17 ... washer, 20 ... power transmission device, 22b ... transaxle case (case), 22d ... projecting part (second support part), 91, 92 ... disc (movable part), 93 ... push member (movable) Part), 96 ... piston, 97 ... return spring, 98 ... support member, 98a ... wall part (second support part), B1 ... brake.

Claims (4)

Case and
The sun gear, the cylindrical ring gear positioned outside the sun gear in the radial direction, and the sun gear and the ring gear positioned between the sun gear and the ring gear. A planetary gear mechanism having a pinion gear for transmitting power and a carrier for rotatably supporting the pinion gear;
A first support portion for supporting an end portion on one side in the axial direction of the ring gear;
A second support portion for supporting the other end portion of the ring gear in the axial direction;
With
The first support portion is provided on the carrier, and a washer interposed between the carrier and the pinion gear is connected to the first support portion and one end portion in the axial direction of the ring gear. Intervening,
Power transmission device. The planetary gear mechanism has a plurality of the pinion gears,
The power transmission device according to claim 1, wherein the washer is shared by the plurality of pinion gears. A movable part that suppresses rotation of the rotating element housed in the case, a piston that is driven by hydraulic pressure to move the movable part, a return spring that applies a reaction force to the piston, and between the return spring and the case A support member interposed between the support spring and the return spring.
The power transmission device according to claim 1, wherein the second support portion is provided on the support member.   The power transmission device according to claim 1, wherein the second support portion is provided in the case.

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