JP2019182285A - Power transmission device - Google Patents

Abstract

To shorten the axial length of a power transmission device.SOLUTION: The power transmission device comprises: a connection release mechanism performing connection and release of the connection between a driving source and an axle; an oil pump driven by the rotation of a pump shaft 61; a first rotation transmission mechanism 70 capable of transmitting the rotation of a first rotation shaft on the side nearer the driving source than the connection release mechanism to the pump shaft; and a second rotation transmission mechanism 80 capable of transmitting the rotation of a second rotation shaft on the side nearer the axle than the connection release mechanism to the pump shaft. The first rotation transmission mechanism and/or the second rotation transmission mechanism have: gear-shaped members 73, 83 arranged coaxially with the pump shaft and rotatably supported by a case 62 through bearings 76, 86; and one-way clutches 75, 85 that transmit rotation from the gear-shaped member to the pump shaft but block transmission of rotation from the pump shaft to the gear-shaped member. Furthermore, the one-way clutch and the bearing at least partially overlap in an axial direction when viewed from a radial direction.SELECTED DRAWING: Figure 2

Description

  The present disclosure relates to a power transmission device.

  Conventionally, as this type of power transmission device, a forward / reverse switching device having an engaging element that is mounted on a vehicle and that connects and disconnects a drive source and an axle, and a rotation shaft of the drive source are separated from each other. An oil pump driven by the rotation of a certain pump shaft, a first rotation transmission mechanism capable of transmitting the rotation of the first rotation shaft closer to the drive source than the forward / reverse switching device to the pump shaft, and the axle side of the forward / reverse switching device A second rotation transmission mechanism capable of transmitting the rotation of the second rotation shaft to the pump shaft is known (for example, see Non-Patent Document 1). Here, the first rotation transmission mechanism includes a first sprocket attached to the first rotation shaft, a second sprocket attached to the pump shaft via a one-way clutch, and a chain spanned between the first sprocket and the second sprocket. Have The second sprocket is rotatably supported by the case by a bearing that is arranged in line with the one-way clutch in the axial direction. The second rotation transmission mechanism is configured similarly to the first rotation transmission mechanism.

Fuji Heavy Industries, Ltd. “SUBARU XV HYBRID New Car Manual”, pages 3-4, June 2013

  In the above-described power transmission device, the one-way clutch and the bearing are arranged so as to be aligned in the axial direction. Therefore, the shaft lengths of the first rotation transmission mechanism and the second rotation transmission mechanism are long, and the shaft length of the power transmission device is long. It has become.

  The main purpose of the power transmission device of the present disclosure is to shorten the axial length of the power transmission device.

  The power transmission device of the present disclosure employs the following means in order to achieve the main object described above.

The power transmission device of the present disclosure is:
Mounted on the vehicle,
A connection release mechanism for connecting and releasing the connection between the drive source and the axle;
An oil pump driven by rotation of the pump shaft;
A first rotation transmission mechanism capable of transmitting the rotation of the first rotation shaft closer to the drive source than the connection release mechanism to the pump shaft;
A second rotation transmission mechanism capable of transmitting the rotation of the second rotation shaft closer to the axle than the connection release mechanism to the pump shaft;
A power transmission device comprising:
The first rotation transmission mechanism and / or the second rotation transmission mechanism are arranged coaxially with the pump shaft and are rotatably supported by a case by a bearing, and the gear shaft and the pump shaft. A one-way clutch that transmits the rotation to the gear-shaped member, but transmits the rotation to the gear-shaped member.
The one-way clutch and the bearing at least partially overlap in the axial direction when viewed from the radial direction.
This is the gist.

  In the power transmission device according to the present disclosure, the connection release mechanism that connects and disconnects the drive source and the axle, the oil pump that is driven by the rotation of the pump shaft, and the first rotation closer to the drive source than the connection release mechanism. A first rotation transmission mechanism capable of transmitting the rotation of the shaft to the pump shaft; and a second rotation transmission mechanism capable of transmitting the rotation of the second rotation shaft closer to the axle than the connection release mechanism to the pump shaft. The first rotation transmission mechanism and / or the second rotation transmission mechanism is arranged coaxially with the pump shaft and is rotatably supported by the case by a bearing, and rotates from the gear-shaped member to the pump shaft. A one-way clutch that transmits but interrupts transmission of rotation from the pump shaft to the gear-like member. Furthermore, the one-way clutch and the bearing at least partially overlap in the axial direction when viewed from the radial direction. Thereby, the axial length of the first rotation transmission mechanism and / or the second rotation transmission mechanism can be shortened. As a result, the axial length of the power output device can be shortened. Here, the “gear-like member” includes a sprocket in the winding transmission mechanism and a gear in the gear mechanism.

It is a schematic structure figure showing power transmission device 20 of this indication. FIG. 3 is a schematic configuration diagram of a main part of a power transmission device 20. 2 is a schematic configuration diagram of a main part of a power transmission device 120. FIG.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram illustrating a power transmission device 20 of the present disclosure. The power transmission device 20 is mounted on a front wheel drive vehicle, and is disposed horizontally so that a crankshaft 12 of an engine (drive source) 11 and left and right drive shafts 59 connected to drive wheels (not shown) are substantially parallel. The transaxle is connected to the engine 11. As shown in the figure, the power transmission device 20 includes a transmission case 22, a starting device 23 housed in the transmission case 22, a forward / reverse switching mechanism 30, a belt-type continuously variable transmission (hereinafter referred to as “CVT”). 40, a gear mechanism 50, a differential gear (differential mechanism) 57, an oil pump 60, and the like.

  The starting device 23 is configured as a fluid starting device with a lock-up clutch. The starting device 23 includes a pump impeller 23p connected to the crankshaft 12 of the engine 11 via a front cover 23f as an input member, a turbine runner 23t fixed to the input shaft 36 (always connected), a pump impeller 23p, A stator 23s disposed inside the turbine runner 23t for rectifying the flow of hydraulic oil (ATF) from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o for limiting the rotational direction of the stator 23s in one direction, a damper mechanism 24; It has a lock-up clutch 25 and the like.

  The pump impeller 23p, the turbine runner 23t, and the stator 23s function as a 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, and function as a fluid coupling when the rotational speed difference between the two decreases. To do. However, in the starting 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 function as only a fluid coupling.

  The damper mechanism 24 is fixed to, for example, an input element connected to the lockup clutch 25 or a turbine hub that is connected to the input element via a plurality of elastic bodies and is fixed to the input shaft 36 (always connected). Has output elements and the like. The lockup clutch 25 selectively locks up and unlocks the pump impeller 23p and the turbine runner 23t, that is, mechanically connects the front cover 23f and the input shaft 36 (via the damper mechanism 24). To run. 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 forward / reverse switching mechanism 30 includes a double pinion planetary gear mechanism 31, a clutch (disconnection mechanism) C1 and a brake B1 as hydraulic friction engagement elements. The planetary gear mechanism 31 supports a sun gear 31s fixed to the input shaft 36, a ring gear 31r, a pinion gear 31pa meshing with the sun gear 31s, and a pinion gear 31pb meshing with the ring gear 31r and a carrier coupled to the primary shaft 42 of the CVT 40. 31c.

  The clutch C1 releases the carrier 31c of the planetary gear mechanism 31 so as to be rotatable with respect to the input shaft 36 (sun gear 31s), and also removes the carrier 31c of the planetary gear mechanism 31 when hydraulic pressure is supplied from a hydraulic control device (not shown). It connects with the input shaft 36 (sun gear 31s). In addition, the brake B1 releases the ring gear 31r of the planetary gear mechanism 31 so as to be rotatable with respect to the transmission case 22, and the ring gear 31r of the planetary gear mechanism 31 to the transmission case 22 when hydraulic pressure is supplied from the hydraulic control device. It is fixed so that it cannot rotate.

  As the clutch C1, a hydraulic clutch having a hydraulic servo composed of a piston, a plurality of friction engagement plates (friction plates and separator plates), an oil chamber (engagement oil chamber and cancel oil chamber) to which hydraulic oil is supplied, and the like. Is adopted. As the brake B1, a hydraulic brake having a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an oil chamber (engagement oil chamber and cancel oil chamber) to which hydraulic oil is supplied, and the like. Is adopted.

  With this configuration, if the clutch C1 is engaged and the brake B1 is released, the power transmitted to the input shaft 36 can be transmitted to the primary shaft 42 of the CVT 40 as it is to advance the vehicle. Further, when the clutch C1 is released and the brake B1 is engaged, the rotation of the input shaft 36 is converted in the reverse direction and transmitted to the primary shaft 42 of the CVT 40, and the vehicle can be moved backward. Furthermore, if the clutch C1 and the brake B1 are released, the connection between the input shaft 36 and the primary shaft 42 can be released.

  The CVT 40 includes a primary pulley 43 provided on a primary shaft (first axis) 42 as a driving side rotation axis, and a secondary shaft (second axis) 44 as a driven side rotation axis arranged in parallel with the primary shaft 42. Secondary pulley 45 provided, transmission belt 46 spanned between the pulley groove of primary pulley 43 and the pulley groove of secondary pulley 45, and a primary cylinder that is a hydraulic actuator for changing the groove width of primary pulley 43 47 and a secondary cylinder 48 which is a hydraulic actuator for changing the groove width of the secondary pulley 45.

  The primary pulley 43 has a fixed sheave 43a formed integrally with the primary shaft 42, and a movable sheave 43b supported by the primary shaft 42 through a ball spline or the like so as to be slidable in the axial direction. The secondary pulley 45 is supported by a fixed sheave 45a formed integrally with the secondary shaft 44 and a return spring 49 which is supported by the secondary shaft 44 so as to be slidable in the axial direction via a ball spline or the like and is a compression spring. And a movable sheave 45b biased in the axial direction.

  The primary cylinder 47 is formed behind the movable sheave 43 b of the primary pulley 43, and the secondary cylinder 48 is formed behind the movable sheave 45 b of the secondary pulley 45. Hydraulic oil is supplied to the primary cylinder 47 and the secondary cylinder 48 from the hydraulic control device so as to change the groove width between the primary pulley 43 and the secondary pulley 45. As a result, the power transmitted from the engine 11 to the primary shaft 42 via the starting device 23 and the forward / reverse switching mechanism 30 can be shifted steplessly and transmitted to the secondary shaft 44. The power transmitted to the secondary shaft 44 is transmitted to the left and right drive wheels via the gear mechanism 50, the differential gear 57, and the drive shaft 59.

  The gear mechanism 50 includes a counter drive gear 51 that rotates integrally with the secondary shaft 44, and a counter shaft that extends in parallel with the secondary shaft 44 and the drive shaft 59 and is rotatably supported by the transmission case 22 via a bearing. (Third axis) 52, a counter driven gear 53 fixed to the counter shaft 52 and meshing with the counter drive gear 51, and a drive pinion gear (final drive) formed integrally with the counter shaft 52 or fixed to the counter shaft 52 Gear) 54, and a differential ring gear (final driven gear) 55 that meshes with the drive pinion gear 54 and is coupled to a differential gear 57 coupled to the drive shaft 59.

  The oil pump 60 is configured as a mechanical oil pump that sucks hydraulic oil in an oil pan (not shown) and supplies hydraulic pressure to a hydraulic control device by rotation of a pump shaft 61 that is separate from the crankshaft 12 of the engine 11. And is accommodated in a pump case 62. The pump shaft 61 of the oil pump 60 is connected to the rotary shaft 23ps connected to the pump impeller 23p via the first rotation transmission mechanism 70 and to the primary shaft 42 of the CVT 40 via the second rotation transmission mechanism 80. Is done. Further, the outer diameter of the pump shaft 61 is set smaller than the outer diameter of the rotating shaft 23 ps and the outer diameter of the primary shaft 42. The rotating shaft 23ps is rotatably supported by the input shaft 36.

  The first rotation transmission mechanism 70 includes a first sprocket 72 attached to a rotation shaft 23ps connected to the pump impeller 23p, a second sprocket 73 disposed coaxially with the pump shaft 61 of the oil pump 60, and a first sprocket. 72 and a chain 74 spanned between the second sprocket 73 and a one-way clutch 75 that transmits rotation from the second sprocket 73 to the pump shaft 61 but blocks transmission of rotation from the pump shaft 61 to the second sprocket 73. Have. That is, it can be said that the rotary shaft 23 ps and the pump shaft 61 are connected via a one-way clutch 75 and a winding transmission mechanism having a first sprocket 72, a second sprocket 73, and a chain 74.

  The second rotation transmission mechanism 80 includes a drive gear 82 attached to the primary shaft 42 of the CVT 40, a driven gear 83 disposed coaxially with the pump shaft 61 of the oil pump 60, and an idler gear 84 that meshes with the drive gear 82 and the driven gear 83. And a one-way clutch 85 that transmits rotation from the driven gear 83 to the pump shaft 61 but blocks transmission of rotation from the pump shaft 61 to the driven gear 83. That is, it can be said that the primary shaft 42 and the pump shaft 61 are connected via a one-way clutch 85 and a gear transmission mechanism having a drive gear 82, a driven gear 83, and an idler gear 84. Further, by using the idler gear 84, the rotation direction of the rotating shaft 23ps connected to the pump impeller 23p, the primary shaft 42 of the CVT 40, and the pump shaft 61 of the oil pump 60 during forward traveling can be made the same.

  The first rotation transmission mechanism 70 and the second rotation transmission mechanism 80 have a rotation ratio γ1 between the rotation shaft 23ps connected to the pump impeller 23p and the pump shaft 61 of the oil pump 60 (the number of rotations of the rotation shaft 23ps / the pump shaft 61). The rotation ratio γ2 between the primary shaft 42 of the CVT 40 and the pump shaft 61 of the oil pump 60 (the rotation speed of the primary shaft 42 / the rotation speed of the pump shaft 61) is smaller than the value 1 and the rotation ratio γ2 is less than 1. It is designed to be Accordingly, when the rotational speed of the primary shaft 42 of the CVT 40 is relatively high, such as when traveling forward at a relatively high speed, the rotation of the primary shaft 42 is transmitted to the pump shaft 61 via the second rotation transmission mechanism 80. As the oil pump 60 is driven, the one-way clutch 75 is idled. On the other hand, when the rotational speed of the primary shaft 42 of the CVT 40 is relatively low, such as during forward running at a relatively low speed or when the engine 11 is stopped, the rotation of the rotary shaft 23ps connected to the pump impeller 23p. Is transmitted to the pump shaft 61 via the first rotation transmission mechanism 70 to drive the oil pump 60, and the one-way clutch 85 rotates idly. During reverse travel, the primary shaft 42 of the CVT 40 rotates in the reverse direction, so that the rotation of the rotary shaft 23ps connected to the pump impeller 23p is transmitted to the pump shaft 61 via the first rotation transmission mechanism 70, and the oil pump 60 is The one-way clutch 85 is idled while being driven.

  FIG. 2 is a schematic configuration diagram of a main part of the power transmission device 20. The pump case 62 that accommodates the oil pump 60 includes a case main body 63 and an end of the case main body 63 on the second sprocket 73 side (right side in FIG. 2) in the axial direction of the oil pump 60 (the extending direction of the pump shaft 61). An arc-shaped (C-shaped) support portion 64 extending in the direction of the axis, and an arc-shaped (C-shaped) extending in the axial direction of the oil pump 60 from the end of the case main body 63 on the driven gear 83 side (left side in FIG. 2). ) Support portion 65.

  The second sprocket 73 of the first rotation transmission mechanism 70 includes an annular main body 73a having external teeth on the outer periphery (having a through-hole penetrating in the axial direction in the center), and oil in the axial direction from the inner periphery of the main body 73a. And a cylindrical shaft portion 73b extending to the pump 60 side (left side in FIG. 2). The shaft portion 73 b is disposed inside the support portion 64 of the pump case 62 and outside the pump shaft 61. The shaft portion 73b is rotatably supported by the support portion 64 by a bearing 76.

  The one-way clutch 75 has an inner race 75a, an outer race 75b, and a sprag 75c disposed between the inner race 75a and the outer race 75b. The inner race 75 a is formed integrally with the pump shaft 61 on the outer periphery of the pump shaft 61 of the oil pump 60. The outer race 75b is press-fitted into the inner periphery of the shaft portion 73b of the second sprocket 73. Thereby, the inner race 75a rotates integrally with the pump shaft 61, and the outer race 75b rotates integrally with the second sprocket 73.

  The bearing 76 includes an inner race 76a, an outer race 76b, and rolling elements (for example, balls) 76c that roll between the inner race 76a and the outer race 76b. The inner race 76a includes a stepped portion 73c formed in the vicinity of the boundary with the main body portion 73a on the outer periphery of the shaft portion 73b of the second sprocket 73, and a snap ring 77 fitted into a recess formed on the outer periphery of the shaft portion 73b. Thus, movement in the axial direction is restricted. The outer race 76 b is restricted from moving in the axial direction by a snap ring 78 that fits into a recess formed on the outer periphery of the outer race 76 b and a recess formed on the inner periphery of the support portion 64 of the pump case 62. From this, it can be said that the inner race 76 a is attached to the shaft portion 73 b of the second sprocket 73 and the outer race 76 b is attached to the support portion 64 of the pump case 62.

  The one-way clutch 75 and the bearing 76 overlap each other in the axial direction when viewed from the radial direction, and these include a support portion 64 of the pump case 62, a shaft portion 73b of the sprocket 73, and a pump shaft 61 of the oil pump 60. In addition, they overlap in the axial direction when viewed from the radial direction. The clearance Co1 between the inner race 75a and the sprag 75c of the one-way clutch 75 and the clearance Co2 between the outer race 75b and the sprag 75c are the inner circumference of the inner race 76a of the bearing 76 and the outer circumference of the shaft portion 73b of the second sprocket 73. The clearance Cb1 and the clearance Cb2 between the outer periphery of the outer race 76b of the bearing 76 and the inner periphery of the support portion 64 of the pump case 62 are larger.

  The driven gear 83 of the second rotation transmission mechanism 80 includes an annular main body 83a having external teeth on the outer periphery (having a through-hole penetrating in the axial direction in the center), and an oil pump 60 in the axial direction from the inner periphery of the main body 83a. And a cylindrical shaft portion 83b extending to the side (right side in FIG. 2). The shaft portion 83 b is disposed inside the support portion 65 of the pump case 62 and outside the pump shaft 61. The shaft portion 83 b is rotatably supported by the support portion 65 by a bearing 86.

  The one-way clutch 85 includes an inner race 85a, an outer race 85b, and a sprag 85c disposed between the inner race 85a and the outer race 85b. The inner race 85 a is formed integrally with the pump shaft 61 on the outer periphery of the pump shaft 61 of the oil pump 60. The outer race 85b is press-fitted into the inner periphery of the shaft portion 83b of the driven gear 83. Accordingly, the inner race 85a rotates integrally with the pump shaft 61, and the outer race 85b rotates integrally with the driven gear 83.

  The bearing 86 includes an inner race 86a, an outer race 86b, and rolling elements (for example, balls) 86c that roll between the inner race 86a and the outer race 86b. The inner race 86a includes a stepped portion 83c formed in the vicinity of the boundary with the main body portion 83a on the outer periphery of the shaft portion 83b of the driven gear 83, a snap ring 87 fitted in a recess formed on the outer periphery of the shaft portion 83b, This restricts the movement in the axial direction. The outer race 86b is restricted from moving in the axial direction by a snap ring 88 fitted into a recess formed on the outer periphery of the outer race 86b and a recess formed on the inner periphery of the support portion 65 of the pump case 62. From this, it can be said that the inner race 86 a is attached to the shaft portion 83 b of the driven gear 83 and the outer race 86 b is attached to the support portion 65 of the pump case 62. The one-way clutch 85 and the bearing 86 overlap each other in the axial direction when viewed from the radial direction, and these include a support portion 65 of the pump case 62, a shaft portion 83b of the driven gear 83, and a pump shaft 61 of the oil pump 60. In addition, they overlap in the axial direction when viewed from the radial direction.

  In the power transmission device 20 of the present embodiment configured as described above, in the first rotation transmission mechanism 70, the one-way clutch 75 and the bearing 76 are arranged so as to overlap in the axial direction when viewed from their radial directions. Accordingly, it is possible to suppress the axial length of the first rotation transmission mechanism 70 from becoming longer than that in which the one-way clutch 75 and the bearing 76 are arranged in the axial direction thereof. Further, in the second rotation transmission mechanism 80, the one-way clutch 85 and the bearing 86 are disposed so as to overlap in the axial direction when viewed from their radial directions. Accordingly, it is possible to suppress the axial length of the second rotation transmission mechanism 80 from becoming longer than that in which the one-way clutch 85 and the bearing 86 are arranged in the axial direction thereof. As a result, the axial length of the power transmission device 20 can be shortened.

  In the power transmission device 20 of the present embodiment, in the first rotation transmission mechanism 70, the clearance Co1 between the inner race 75a and the sprag 75c of the one-way clutch 75 and the clearance Co2 between the outer race 75b and the sprag 75c are The clearance Cb1 between the inner periphery of the inner race 76a and the outer periphery of the shaft portion 73b of the second sprocket 73 and the clearance Cb2 between the outer periphery of the outer race 76b of the bearing 76 and the inner periphery of the support portion 64 of the pump case 62 are larger. Yes. Due to the chain 74 spanned between the first sprocket 72 and the second sprocket 73, a load in the direction approaching the first sprocket 72 (upward in FIG. 2) acts on the second sprocket 73, but compared to the clearances Co 1 and Co 2. Since the clearances Cb1 and Cb2 are small, the load is received by the bearing 76. Thereby, the load in the direction approaching the first sprocket 72 acting on the one-way clutch 75 can be reduced. As a result, the one-way clutch 75 can be further downsized.

  Further, in the power transmission device 20 of the present embodiment, in the first rotation transmission mechanism 70, the inner race 75a of the one-way clutch 75 is formed integrally with the pump shaft 61 of the oil pump 60, and the outer race 75b is the second sprocket. 73 is press-fitted into the shaft portion 73b. Thereby, since it is not necessary to provide another member for restricting the axial movement of the inner race 75a and the outer race 75b, the axial length of the one-way clutch 75 can be shortened. In the second rotation transmission mechanism 80, the inner race 85a of the one-way clutch 85 is formed integrally with the pump shaft 61 of the oil pump 60, and the outer race 85b is press-fitted into the shaft portion 83b of the driven gear 83. Thereby, since it is not necessary to provide another member for restricting the movement of the inner race 85a and the outer race 85b in the axial direction, the axial length of the one-way clutch 85 can be shortened. As a result, the axial length of the power transmission device 20 can be further shortened.

  In addition, in the power transmission device 20 of this embodiment, in the first rotation transmission mechanism 70, the shaft portion 73b of the second sprocket 73 is rotatably supported by the support portion 64 of the pump case 62 via the bearing 76. In the second rotation transmission mechanism 80, the shaft portion 83 b of the driven gear 83 is rotatably supported by the support portion 65 of the pump case 62 via the bearing 86. This eliminates the need to change the design of the transmission case 22 in order to support the shaft portion 73b and the shaft portion 83b.

  In the power transmission device 20 of the present embodiment, the outer diameter of the pump shaft 61 of the oil pump 60 is smaller than the outer diameter of the rotating shaft 23ps connected to the pump impeller 23p, and the one-way clutch 75 is not on the rotating shaft 23ps side. Provided on the pump shaft 61 side. Thereby, the outer diameter of the one-way clutch 75 can be reduced. As a result, when designing the first rotation transmission mechanism 70 so that the rotation ratio γ1 between the rotation shaft 23ps and the pump shaft 61 becomes a desired rotation ratio, the outer diameters of the first sprocket 72 and the second sprocket 73 are reduced. The diameter can be reduced, and space saving and mass reduction of the first rotation transmission mechanism 70 can be achieved. Further, the outer diameter of the pump shaft 61 of the oil pump 60 is smaller than the outer diameter of the primary shaft 42 of the CVT 40, and the one-way clutch 85 is provided not on the primary shaft 42 side but on the pump shaft 61 side. Thereby, the outer diameter of the one-way clutch 85 can be reduced. As a result, when designing the second rotation transmission mechanism 80 so that the rotation ratio γ2 between the primary shaft 42 and the pump shaft 61 becomes a desired rotation ratio, the outer diameters of the drive gear 82 and the driven gear 83 are reduced. Space saving and mass reduction can be achieved.

  In the power transmission device 20 described above, in the first rotation transmission mechanism 70, the one-way clutch 75 and the bearing 76 are arranged so as to overlap in the axial direction when viewed from the radial direction. It is good also as what is arrange | positioned so that 76 may overlap with an axial direction seeing from those radial directions. Further, in the second rotation transmission mechanism 80, the one-way clutch 85 and the bearing 86 are arranged so as to overlap in the axial direction when viewed from their radial directions, but the one-way clutch 85 and the bearing 86 have their diameters. It is good also as what is arrange | positioned so that it may overlap in an axial direction seeing from a direction.

  In the power transmission device 20 described above, the shaft portion 73b of the second sprocket 73 is disposed inside the support portion 64 of the pump case 62, and the pump shaft 61 is disposed inside the shaft portion 73b of the second sprocket 73. Although the clutch 75 is disposed radially inward of the bearing 76, the shaft portion 73b of the second sprocket 73 is disposed outside the support portion 64 of the pump case 62 and the pump shaft 61 is disposed in the second sprocket 73. The one-way clutch 75 may be disposed on the outer side in the radial direction from the bearing 76. Further, the shaft portion 83 b of the driven gear 83 is disposed inside the support portion 64 of the pump case 62, the pump shaft 61 is disposed inside the shaft portion 83 b of the driven gear 83, and the one-way clutch 85 is radially inward of the bearing 86. However, the shaft portion 83b of the driven gear 83 is disposed outside the support portion 65 of the pump case 62, the pump shaft 61 is disposed outside the shaft portion 83b of the driven gear 83, and the one-way clutch 85 is It is good also as what is arranged on the diameter direction outside rather than bearing 86.

  In the power transmission device 20 described above, in the first rotation transmission mechanism 70, the clearance Co1 between the inner race 75a and the sprag 75c of the one-way clutch 75 and the clearance Co2 between the outer race 75b and the sprag 75c correspond to the inner race 76a of the bearing 76. The clearance Cb1 between the inner periphery and the outer periphery of the shaft portion 73b of the second sprocket 73 and the clearance Cb2 between the outer periphery of the outer race 76b of the bearing 76 and the inner periphery of the support portion 64 of the pump case 62 are greater. However, the clearances Co1 and Co2 and the clearances Cb1 and Cb2 may be approximately the same.

  In the power transmission device 20 described above, in the first rotation transmission mechanism 70, the inner race 75a of the one-way clutch 75 is formed integrally with the pump shaft 61 of the oil pump 60, and the outer race 75b is the shaft portion 73b of the second sprocket 73. In the second rotation transmission mechanism 80, the inner race 85a of the one-way clutch 85 is formed integrally with the pump shaft 61 of the oil pump 60 and the outer race 85b is the inner circumference of the shaft portion 83b of the driven gear 83. It was supposed to be press-fitted into. However, as shown in the power transmission device 120 of FIG. 3, in the first rotation transmission mechanism 170, the inner race 175a of the one-way clutch 175 is press-fitted into the outer periphery of the pump shaft 161 of the oil pump 160 and the outer race 175b is the second. In the second rotation transmission mechanism 180, the inner race 185 a of the one-way clutch 185 is press-fitted into the outer periphery of the pump shaft 161 of the oil pump 160 and the outer race 185 b is the shaft of the driven gear 183. It may be formed integrally with the portion 183b. Further, the present invention is not limited to the combination of the first rotation transmission mechanism 70 and the second rotation transmission mechanism 80 of the power transmission device 20 or the combination of the first rotation transmission mechanism 170 and the second rotation transmission mechanism 180 of the power transmission device 120. The first rotation transmission mechanism 70 and the second rotation transmission mechanism 180 may be combined, or the first rotation transmission mechanism 170 and the second rotation transmission mechanism 80 may be combined. Further, in the first rotation transmission mechanism 70, the inner race 75a of the one-way clutch 75 is formed integrally with the pump shaft 61 of the oil pump 60, and the outer race 75b is formed integrally with the shaft portion 73b of the second sprocket 73. It may be a thing. Similarly, in the second rotation transmission mechanism 80, the inner race 85a of the one-way clutch 85 is formed integrally with the pump shaft 61 of the oil pump 60, and the outer race 85b is formed integrally with the shaft portion 83b of the driven gear 83. It is good. In addition, in the first rotation transmission mechanism 70, the inner race 75a of the one-way clutch 75 is press-fitted into the outer periphery of the pump shaft 61 of the oil pump 60, and the outer race 75b is press-fitted into the inner periphery of the shaft portion 73b of the second sprocket 73. It is good also as what is done. Similarly, in the second rotation transmission mechanism 80, the inner race 85a of the one-way clutch 85 is press-fitted into the outer periphery of the pump shaft 61 of the oil pump 60, and the outer race 85b is press-fitted into the inner periphery of the shaft portion 83b of the driven gear 83. It may be a thing. Even in these cases, there is no need to provide a separate member for restricting the axial movement of the inner races 75a, 85a, 175a, 185a and the outer races 75b, 85b, 175b, 185b. , 185 can be shortened.

  In the power transmission device 20 described above, in the first rotation transmission mechanism 70, the inner race 75a of the one-way clutch 75 is formed integrally with the pump shaft 61 of the oil pump 60, and the outer race 75b is the shaft portion 73b of the second sprocket 73. In the second rotation transmission mechanism 80, the inner race 85a of the one-way clutch 85 is formed integrally with the pump shaft 61 of the oil pump 60 and the outer race 85b is the inner circumference of the shaft portion 83b of the driven gear 83. It was supposed to be press-fitted into. However, some of these may be fitted by spline fitting or the like instead of press-fitting or integral formation, and movement in the axial direction may be restricted by another member.

  In the power transmission device 20 described above, in the first rotation transmission mechanism 70, the shaft portion 73b of the second sprocket 73 is rotatably supported by the support portion 64 of the pump case 62 via the bearing 76. 22, the shaft portion 73b of the second sprocket 73 may be rotatably supported via a bearing 76. In the second rotation transmission mechanism 80, the shaft portion 83b of the driven gear 83 is rotatably supported by the support portion 65 of the pump case 62 via the bearing 86. However, the shaft portion 83b of the driven gear 83 is supported by the transmission case 22. It is good also as what supports rotatably via the bearing 86. FIG.

  In the power transmission device 20 described above, the one-way clutches 75 and 85 are configured as sprag type one-way clutches having inner races 75a and 85a, outer races 75b and 85b, and sprags 75c and 85c. However, at least one of the one-way clutches 75 and 85 may be configured as a rotor-type one-way clutch provided with a roller instead of a sprag.

  In the power transmission device 20 described above, the inner race 76a of the bearing 76 is restricted from moving in the axial direction by the stepped portion 73c of the second sprocket 73 and the snap ring 77. However, the shaft portion of the second sprocket 73 is used. It is good also as what is press-fitted in the outer periphery of 73b. The outer race 76b of the bearing 76 is restricted from moving in the axial direction by the snap ring 78, but may be press-fitted into the inner periphery of the support portion 64 of the pump case 62. Furthermore, although the inner race 86a of the bearing 86 is restricted from moving in the axial direction by the stepped portion 83c of the driven gear 83 and the snap ring 87, the inner race 86a may be press-fitted into the outer periphery of the shaft portion 83b of the driven gear 83. Good. Further, the outer race 86b of the bearing 86 is restricted from moving in the axial direction by the snap ring 88, but may be press-fitted into the inner periphery of the support portion 65 of the pump case 62.

  In the power transmission device 20 described above, the first rotation transmission mechanism 70 includes a winding transmission mechanism having a first sprocket 72, a second sprocket 73, and a chain 74, and the second rotation transmission mechanism 80 includes a drive gear 82, A gear transmission mechanism having a driven gear 83 and an idler gear 84 is provided. However, the first rotation transmission mechanism 70 may include a gear transmission mechanism instead of the winding transmission mechanism. Further, the second rotation transmission mechanism 80 may include a winding transmission mechanism instead of the gear transmission mechanism.

  In the power transmission device 20 described above, the first sprocket 72 of the first rotation transmission mechanism 70 is attached to the rotary shaft 23ps connected to the pump impeller 23p, but is assumed to be attached to the crankshaft 12 of the engine 11. Also good. The drive gear 82 of the second rotation transmission mechanism 80 is attached to the primary shaft 42 of the CVT 40. However, the drive gear 82 may be attached to the secondary shaft 44 or attached to the counter shaft 52 of the gear mechanism 50 or the like. It may be a thing.

  In the above-described embodiment, the clutch C1 of the forward / reverse switching mechanism 30 connects the sun gear 31s and the carrier 31c of the planetary gear mechanism 31 to each other and releases the connection between them. However, the present invention is not limited to this. Instead, any two of the three rotating elements of the planetary gear mechanism 31 may be connected to each other and the connection between them may be released. Further, the forward / reverse switching mechanism 30 has the double pinion planetary gear mechanism 31, but may instead have a single pinion planetary gear mechanism.

  The power transmission device 20 described above includes the forward / reverse switching mechanism 30 and the CVT 40, and the clutch C1 of the forward / reverse switching mechanism 30 corresponds to the disconnection mechanism, but instead includes a stepped transmission. An engagement element (for example, an engagement element to be engaged when starting) provided in the stepped transmission may correspond to the connection release mechanism.

  As described above, the power transmission device according to the present disclosure is mounted on a vehicle, and includes a connection release mechanism (C1) that connects and disconnects the drive source (11) and the axle (59), and the pump shaft (61). , 161) and an oil pump (60, 160) driven by the rotation of the pump shaft (61, 161) and the rotation of the first rotating shaft closer to the drive source (11) than the connection release mechanism (C1). Rotation of the second rotation shaft closer to the axle (59) than the connection release mechanism (C1) can be transmitted to the pump shaft (61, 161). A second rotation transmission mechanism (80, 180), a power transmission device (20, 120) comprising the first rotation transmission mechanism (70, 170) and / or the second rotation transmission mechanism (80, 180). 180) the pump shaft (61 161) and a gear-like member (73, 83, 173, 183) which is arranged coaxially with the bearing (76, 86) and is rotatably supported by the case (62), and the gear-like member (73, 83, 173, 183) transmits the rotation to the pump shaft (61, 161) but cuts off the transmission of rotation from the pump shaft (61, 161) to the gear-like member (73, 83, 173, 183). A clutch (75, 85, 175, 185), and the one-way clutch (75, 85, 175, 185) and the bearing (76, 86) are at least partially in the axial direction when viewed from the radial direction. The gist is that they overlap.

  In the power transmission device according to the present disclosure, the connection release mechanism that connects and disconnects the drive source and the axle, the oil pump that is driven by the rotation of the pump shaft, and the first rotation closer to the drive source than the connection release mechanism. A first rotation transmission mechanism capable of transmitting the rotation of the shaft to the pump shaft; and a second rotation transmission mechanism capable of transmitting the rotation of the second rotation shaft closer to the axle than the connection release mechanism to the pump shaft. The first rotation transmission mechanism and / or the second rotation transmission mechanism is arranged coaxially with the pump shaft and is rotatably supported by the case by a bearing, and rotates from the gear-shaped member to the pump shaft. A one-way clutch that transmits but interrupts transmission of rotation from the pump shaft to the gear-like member. Furthermore, the one-way clutch and the bearing at least partially overlap in the axial direction when viewed from the radial direction. Thereby, the axial length of the first rotation transmission mechanism and / or the second rotation transmission mechanism can be shortened. As a result, the axial length of the power output device can be shortened. Here, the “gear-like member” includes a sprocket in the winding transmission mechanism and a gear in the gear mechanism.

  In the power transmission device according to the present disclosure, the case (62) includes support portions (64, 65) extending in the axial direction, and the gear-shaped members (73, 83, 173, 183) have external teeth on the outer periphery. An annular main body portion (73a, 83a) and a cylindrical shaft portion (73b, 83b, 173b, 183b) extending in the axial direction from the inner periphery of the main body portion (73a, 83a), The shaft portion (73b, 83b, 173b, 183b) is disposed inside the support portion (64, 65), and the pump shaft (61, 161) is disposed on the shaft portion (73b, 83b, 173b, 183b). The bearings (76, 86) are disposed inside, and are interposed between the shaft portions (73b, 83b, 173b, 183b) and the support portions (64, 65), and the one-way clutches (75, 5, 175, 185), the bearing (76, 86), the support portion (64, 65), the shaft portion (73b, 83b, 173b, 183b) and the pump shaft (61, 161) It is good also as what overlaps at least one part to an axial direction seeing from.

  In this case, the one-way clutch (75, 175) rotates integrally with the first inner race (75a, 175a) rotating integrally with the pump shaft (61, 161) and the shaft portion (73b, 173b). A first outer race (75b, 175b), a sprag (75c) or a roller disposed between the first inner race (75a, 175a) and the first outer race (75b, 175b); The bearing (76) includes a second inner race (76a) attached to the shaft portion (73b, 173b), a second outer race (76b) attached to the support portion (64), and the second inner race. (76a) and a rolling element (76c) disposed between the second outer race (76b) and the first inner The clearance between the race (75a, 175a) and the sprag (75c) or the roller and the clearance between the first outer race (75b, 175b) and the sprag (75c) or the roller are determined by the second inner race (76a). ) And the shaft portion (73b, 173b) and the clearance between the second outer race (76b) and the support portion (64). Thereby, the load which acts on a one-way clutch can be reduced. Here, the first rotation transmission mechanism and / or the second rotation transmission mechanism includes a first sprocket attached to the first rotation shaft or the second rotation shaft, a second sprocket as the gear-shaped member, A chain spanning the first sprocket and the second sprocket may be included.

In this case, the one-way clutch (75, 85, 175, 185) includes an inner race (75a, 85a, 175a, 185a) that rotates integrally with the pump shaft (61, 161), and the shaft portion (73b). , 83b, 173b, 183b), outer races (75b, 85b, 175b, 185b), the inner races (75a, 85a, 175a, 185a) and the outer races (75b, 85b, 175b, 185b) And a sprag (75c, 85c) or roller disposed between
The inner race (75a, 85a, 175a, 185a) is press-fitted into the pump shaft (61, 161) or formed integrally with the pump shaft (61, 161), and the outer race (75b, 85b, 175b, 185b) may be press-fitted into the shaft portion (73b, 83b, 173b, 183b) or formed integrally with the shaft portion (73b, 83b, 173b, 183b). By doing so, it is not necessary to provide a separate member for restricting the movement of the inner race and the outer race in the axial direction, so that the axial length of the one-way clutch can be shortened.

  In the power transmission device according to the present disclosure, the case (62) may be a pump case (62) that houses the oil pump (60, 160).

  In the power transmission device according to the present disclosure, a continuously variable transmission (40) that continuously transmits and transmits power between a primary shaft (42) and a secondary shaft (44), the drive source (11), and the A forward / reverse switching mechanism (30) connected to the primary shaft (42), and the forward / backward switching mechanism (30) includes a first rotating element (31s) connected to the drive source (11). A planetary gear mechanism (31) having a second rotating element (31r) and a third rotating element (31c) connected to the primary shaft (42), the first rotating element (31s), and the second rotating element The clutch (C1) serving as the connection release mechanism (C1) for connecting any two of (31r) and the third rotation element (31c) to each other and releasing the connection between them, and the second rotation Element (31 ) May be used as one having a brake (B1) for releasing the securing together non-rotatably fixed relative to the second case (22).

  In the power transmission device according to the present disclosure, the pump shaft (61, 161) may be a shaft different from the drive shaft (12) of the drive source (11).

  As mentioned above, although the form for implementing this indication was demonstrated, this indication is not limited to such embodiment at all, and can be implemented with various forms within the range which does not deviate from the gist of this indication. Of course.

  The present disclosure can be used in the manufacturing industry of power transmission devices.

  11 Engine, 12 Crankshaft, 20, 120 Power transmission device, 22 Transmission case, 23 Starting device, 23f Front cover, 23o One-way clutch, 23p Pump impeller, 23ps Rotating shaft, 23s Stator, 23t Turbine runner, 24 Damper mechanism, 25 Lockup clutch, 30 forward / reverse switching mechanism, 31 planetary gear mechanism, 31c carrier, 31pa, 31pb pinion gear, 31r ring gear, 31s sun gear, 36 input shaft, 40 continuously variable transmission (CVT), 42 primary shaft, 43 primary pulley, 43a, 45a Fixed sheave, 43b, 45b Movable sheave, 44 Secondary shaft, 45 Secondary pulley, 46 Transmission belt, 47 Primary cylinder, 4 8 Secondary cylinder, 49 Return spring, 50 gear mechanism, 51 Counter drive gear, 52 Counter shaft, 53 Counter driven gear, 54 Drive pinion gear, 57 Differential gear, 59 Drive shaft, 60, 160 Oil pump, 61, 161 Pump shaft, 62 Pump case, 63 case main body, 64, 65 support portion, 70, 170 first rotation transmission mechanism, 72 first sprocket, 73, 173 second sprocket, 73a, 83a main body portion, 73b, 83b, 173b, 183b shaft portion, 73c, 83c Stepped portion, 74 chain, 75, 85, 175, 185 One-way clutch, 75a, 76a, 85a, 86a, 175a, 185a Inner race, 75b, 76b, 85b, 86b , 175b, 185b Outer race, 75c, 85c Sprag, 76, 86 Bearing, 76c, 86c Rolling element, 77, 78, 87, 88 Snap ring, 80, 180 Second rotation transmission mechanism, 82 Drive gear, 83, 183 Driven gear , 184 idler gear, B1 brake, C1 clutch.

Claims (6)

Mounted on the vehicle,
A connection release mechanism for connecting and releasing the connection between the drive source and the axle;
An oil pump driven by rotation of the pump shaft;
A first rotation transmission mechanism capable of transmitting the rotation of the first rotation shaft closer to the drive source than the connection release mechanism to the pump shaft;
A second rotation transmission mechanism capable of transmitting the rotation of the second rotation shaft closer to the axle than the connection release mechanism to the pump shaft;
A power transmission device comprising:
The first rotation transmission mechanism and / or the second rotation transmission mechanism are arranged coaxially with the pump shaft and are rotatably supported by a case by a bearing, and the gear shaft and the pump shaft. A one-way clutch that transmits the rotation to the gear-shaped member, but transmits the rotation to the gear-shaped member.
The one-way clutch and the bearing at least partially overlap in the axial direction when viewed from the radial direction.
Power transmission device. The power transmission device according to claim 1,
The case has a support portion extending in the axial direction,
The gear-shaped member has an annular main body having outer teeth on the outer periphery, and a cylindrical shaft extending in the axial direction from the inner periphery of the main body,
The shaft portion is disposed inside the support portion,
The pump shaft is disposed inside the shaft portion;
The bearing is interposed between the shaft portion and the support portion,
The one-way clutch, the bearing, the support portion, the shaft portion, and the pump shaft at least partially overlap in the axial direction when viewed from the radial direction.
Power transmission device. The power transmission device according to claim 2,
The one-way clutch is disposed between a first inner race that rotates integrally with the pump shaft, a first outer race that rotates integrally with the shaft portion, and the first inner race and the first outer race. A sprag or roller
The bearing includes: a second inner race attached to the shaft portion; a second outer race attached to the support portion; and a rolling element disposed between the second inner race and the second outer race. Have
The clearance between the first inner race and the sprag or the roller and the clearance between the first outer race and the sprag or the roller are the clearance between the second inner race and the shaft portion and the second outer race. Greater than the clearance with the support,
Power transmission device. The power transmission device according to any one of claims 1 to 3,
The case is a pump case that houses the oil pump.
Power transmission device. The power transmission device according to any one of claims 1 to 4,
A continuously variable transmission that continuously transmits and transmits power between the primary shaft and the secondary shaft;
A forward / reverse switching mechanism connected to the drive source and the primary shaft;
With
The forward / reverse switching mechanism includes a planetary gear mechanism having a first rotating element connected to the drive source, a second rotating element, and a third rotating element connected to the primary shaft; the first rotating element; A clutch as the connection release mechanism for connecting any two of the second rotating element and the third rotating element to each other and releasing the connection between them, and the second rotating element with respect to the second case Having a brake that is fixed to be non-rotatable and releases the fixation;
Power transmission device. A power transmission device according to any one of claims 1 to 5,
The pump shaft is a separate shaft from the drive shaft of the drive source,
Power transmission device.