JP2015116891A - Transfer device and drive force transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transfer device which inhibits a thrust load acting on a space between an outer ring and an inner ring of a bearing supporting a rotary member and achieves downsizing, and to provide a drive force transmission device.SOLUTION: A transfer device 1 includes: a first output shaft 11; a case member 2 storing the first output shaft 11; a ball bearing 14 rotatably supporting the first output shaft 11 on the case member 2; a cylindrical rotary member 80 which is supported so as to rotate relative to the first output shaft 11 in a coaxial manner; a clutch mechanism 3 which receives a pressing force applied in an axial direction and connects the first output shaft 11 with the cylindrical rotary member 80 so as to transmit torque therebetween; a cam mechanism 4 which applies the pressing force to the clutch mechanism 3; and a pressing force detection part 5 which detects magnitude of the pressing force. The first output shaft 11 includes: a pressing force receiving part 11a which receives the pressing force through the clutch mechanism 3; and a reaction force receiving part 11b which receives a reaction force of the pressing force. The pressing force detection part 5 is disposed at the outer periphery side of the first output shaft 11 in a space between the pressing force receiving part 11a and the reaction force receiving part 11b.

Description

  The present invention relates to a transfer device and a driving force transmission device including a clutch mechanism that transmits a driving force between rotating members.

  2. Description of the Related Art Conventionally, a driving force transmission device that transmits a driving force of a driving source from an input shaft to an output shaft via a clutch is used, for example, in a vehicle driving force transmission system (see, for example, Patent Document 1).

  A driving force transmission device (axial adjusting device) described in Patent Document 1 is used in, for example, a differential device or a driving axle of a vehicle, and includes a housing, a first rotating member (shaft) supported by the housing by a ball bearing, A second rotating member (boss) that is coaxially rotatable with the first rotating member; a multi-plate clutch that connects the first rotating member and the second rotating member so as to transmit torque; and a pressing force applied to the multi-plate clutch. A ball cam mechanism to be generated and an electric motor for operating the ball cam mechanism are provided.

  The ball cam mechanism has a pressing disk and a supporting disk that can rotate relative to each other, and a plurality of cam balls arranged between the pressing disk and the supporting disk, and the pressing disk is supported with respect to the supporting disk by the rotational force of the electric motor. When rotating, a plurality of cam balls roll on the inclined surfaces formed on the end surfaces of the pressing disk and the support disk, thereby generating axial cam thrust on the pressing disk. By this cam thrust, a plurality of clutch friction plates of the multi-plate clutch are pressed and frictionally engaged, and the rotational force is transmitted from the first rotating member to the second rotating member.

  An annular chamber filled with a hydraulic medium is formed in the housing, and the hydraulic medium in the annular chamber is pressed by a support disk that has received a reaction force of the cam thrust. The pressure in the annular chamber is measured by a pressure sensor, and a pressure signal indicating the measured value of the pressure sensor is output to an electronic device (ECU). As a result, the electronic device can detect the pressing force acting on the multi-plate clutch. For example, by adjusting the current supplied to the electric motor, the electronic device can transmit between the first rotating member and the second rotating member. The accuracy of torque to be generated can be increased.

Special table 2007-515600 gazette

  In the driving force transmission device of Patent Document 1, a multi-plate clutch is disposed between a support plate fixed to the second rotating member and a pressing disk, and a plurality of clutch friction plates of the multi-plate clutch generate cam thrust of the ball cam mechanism. It is pressed toward the support plate from the received pressing disk. Thereby, the cam thrust of the ball cam mechanism is transmitted to the second rotating member via the multi-plate clutch and the support plate.

  On the other hand, the reaction force of the cam thrust acting on the support disk of the ball cam mechanism is transmitted from the housing to the ball bearing disposed between the housing and the first rotating member via the thrust bearing. For this reason, a thrust load that moves in the axial direction acts on the outer ring of the ball bearing fitted in the housing with respect to the inner ring fitted in the first rotating member. Therefore, it is necessary to select a ball bearing having a strength that allows this thrust load, which leads to an increase in the size of the ball bearing and, consequently, an increase in the size of the apparatus.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a transfer device and a driving force transmission device capable of suppressing a thrust load acting between an outer ring and an inner ring of a bearing that supports a rotating member and miniaturizing. To do.

  In order to achieve the above object, the present invention provides a shaft-shaped first rotating member that transmits a driving force, a case member that houses at least a part of the first rotating member, and the case member that performs the first rotation. A bearing that rotatably supports the member; a cylindrical second rotating member that is supported coaxially with the first rotating member; and the first rotating member that receives axial pressing force and the first rotating member A clutch mechanism that couples the second rotating member so as to transmit torque; a pressing mechanism that applies the pressing force to the clutch mechanism; and a pressing force detection unit that detects the magnitude of the pressing force. The rotating member has a pressing force receiving portion that receives the pressing force via the clutch mechanism, and a reaction force receiving portion that receives a reaction force of the pressing force, and the pressing force detecting portion is the pressing force receiving portion. And an outer peripheral side of the first rotating member between the reaction force receiving portion It is arranged to provide a transfer device.

  In order to achieve the above object, the present invention provides a first rotating member that is rotatably supported by a case member via a bearing, and a first rotating member that is rotatably supported on the same axis as the first rotating member. A two-rotating member, a clutch mechanism that receives axial pressing force and connects the first rotating member and the second rotating member so as to transmit torque, and a pressing mechanism that applies the pressing force to the clutch mechanism; A pressing force detecting unit that detects the magnitude of the pressing force, and the first rotating member receives a pressing force receiving unit that receives the pressing force via the clutch mechanism, and a reaction that receives a reaction force of the pressing force. A driving force transmission device including a force receiving portion, wherein the pressing force detecting portion is disposed on an outer peripheral side of the first rotating member between the pressing force receiving portion and the reaction force receiving portion. To do.

  ADVANTAGE OF THE INVENTION According to this invention, it becomes possible to suppress the thrust load which acts between the outer ring | wheel and the inner ring | wheel of a bearing which supports a rotation member, and it becomes possible to achieve size reduction of a transfer apparatus and a driving force transmission apparatus.

It is a block diagram which shows the structural example of the four-wheel drive vehicle which concerns on embodiment of this invention. It is sectional drawing which shows the structural example of a transfer apparatus. FIG. 3 is an enlarged view of a main part of FIG. 2. It is a schematic diagram which shows the 1st guide groove and 2nd guide groove which were formed in the drum, the protrusion of a 1st shift fork, and the protrusion of a 2nd shift fork. (A) is a top view of a 1st cam member. FIG. 5B is a plan view of the second cam member and the cam plate.

[Embodiment]
FIG. 1 is a schematic diagram showing a configuration example of a four-wheel drive vehicle equipped with a driving force transmission device according to a first embodiment of the present invention.

(Configuration of four-wheel drive vehicle)
The four-wheel drive vehicle 9 includes a four-wheel drive state in which the drive force of the drive source 90 mounted on the vehicle body 900 is transmitted to the left and right front wheels 901 and 902 and the left and right rear wheels 903 and 904, and the drive force of the drive source 90. This is a so-called part-time 4WD vehicle capable of switching between a two-wheel drive state transmitted to the left and right rear wheels 903 and 904 and not transmitted to the left and right front wheels 901 and 902. That is, in this embodiment, the left and right rear wheels 903 and 904 function as main drive wheels, and the left and right front wheels 901 and 902 function as auxiliary drive wheels, respectively.

  The four-wheel drive vehicle 9 includes a transfer device 1, a transmission 91, a front differential 92, front wheel side drive shafts 931 and 932, a rear differential 94, and rear wheel side drive shafts 951 and 952. Has a system. The driving force distributed to the left and right front wheels 901 and 902 by the transfer device 1 is transmitted to the front differential 92 via the propeller shaft 96 on the front wheel side. The driving force distributed to the left and right rear wheels 903 and 904 by the transfer device 1 is transmitted to the rear differential 94 via the propeller shaft 97 on the rear wheel side.

  The drive source 90 is an engine that is an internal combustion engine, for example. However, the drive source 90 may be configured by an electric motor or a combination of an engine and an electric motor. Torque as driving force of the four-wheel drive vehicle 9 output from the drive source 90 is shifted by the transmission 91 and output to the input shaft 10 of the transfer device 1.

  The transfer device 1 distributes the torque input from the input shaft 10 to the front wheel side propeller shaft 96 and the rear wheel side propeller shaft 97. The transfer device 1 according to the present embodiment includes a four-wheel drive lock mode in which differential rotation of the front wheel side propeller shaft 96 and the rear wheel side propeller shaft 97 is restricted, and the input shaft 10 and the rear wheel side propeller shaft. 97, the two-wheel drive mode in which the driving force is not transmitted to the front wheel side propeller shaft 96, the differential rotation between the input shaft 10 and the rear wheel side propeller shaft 97 is restricted, and The front wheel side propeller shaft 96 can be switched to a four-wheel drive unlocking mode in which driving force is transmitted via a clutch mechanism described later.

  Further, in the four-wheel drive lock mode, the transfer device 1 interposes a speed reduction mechanism between the input shaft 10 and the rear wheel side propeller shaft 97, so that the rear wheel side propeller shaft 97 and the front wheel are connected from the input shaft 10. It is also possible to select a low-speed four-wheel drive lock mode in which traveling performance is improved by transmitting a reduced driving force to the propeller shaft 96 on the side. Hereinafter, the low-speed four-wheel drive lock mode is abbreviated as L4L mode, the four-wheel drive lock mode is abbreviated as H4L mode, the two-wheel drive mode is abbreviated as H2 mode, and the four-wheel drive unlock mode is abbreviated as H4 mode. .

  The propeller shaft 97 on the rear wheel side transmits torque to the left and right rear wheels 903 and 904 via the rear differential 94. A bevel gear 97 a is provided at one end of the propeller shaft 97 on the rear wheel side, and the bevel gear 97 a meshes with a ring gear 941 fixed to the outer peripheral portion of the differential case 940 of the rear differential 94.

  A pinion shaft 942 is fixed to the differential case 940 so as to be orthogonal to the rotation axis thereof. The differential case 940 accommodates a pair of pinion gears 943 rotatably supported by the pinion shaft 942 and a pair of side gears 944 that mesh with the pair of pinion gears 943 together. Of the pair of side gears 944, one side gear 944 is connected to the left rear wheel 903 via the drive shaft 951, and the other side gear 944 is connected to the right rear wheel 904 via the drive shaft 952.

  The front wheel side propeller shaft 96 transmits torque to the left and right front wheels 901 and 902 via the front differential 92. A bevel gear 96 a is provided at one end of the front-wheel side propeller shaft 96, and the bevel gear 12 a meshes with a ring gear 921 fixed to the outer peripheral portion of the differential case 920 of the front differential 92.

  A pinion shaft 922 is fixed to the differential case 920, and a pair of pinion gears 923 rotatably supported on the pinion shaft 922 and a pair of side gears 924 that mesh with the pair of pinion gears 923 are housed inside the differential case 920. ing. Of the pair of side gears 924, the left front wheel 901 is connected to one side gear 924 via a drive shaft 931, and the right front wheel 902 is connected to the other side gear 924 via a drive shaft 932.

  The transfer device 1 is controlled by the control device 1a. The control device 1a includes information on rotational speeds of the left and right front wheels 901 and 902 and the left and right rear wheels 903 and 904, an acceleration operation amount represented by the amount of depression of the accelerator pedal by the driver, and a drive mode selection switch by the driver. Information such as operation status can be acquired. The control device 1a controls the transfer device 1 based on these pieces of information.

(Configuration of transfer device 1)
FIG. 2 is a cross-sectional view illustrating a configuration example of the transfer device 1. FIG. 3 is an enlarged view of a main part of FIG. The transfer device 1 is relatively non-rotatable to the front wheel side propeller shaft 96 via the mounting flange 11B and the first output shaft 11 connected to the rear wheel side propeller shaft 97 via the mounting flange 11A. The second output shaft 12 is connected. In FIG. 2, the state of the L4L mode is shown above the rotation axis O of the input shaft 10 and the first output shaft 11, and the state of the H2 mode is shown below the rotation axis O. In the following description, the right side in FIG. 2 is referred to as the front side, and the left side is referred to as the rear side.

  The transfer device 1 includes an input shaft 10, a first output shaft 11, a second output shaft 12, a case member 2, and a clutch mechanism 3 that can adjust the driving force output from the second output shaft 12 in the H4 mode. And a cam mechanism 4 as a pressing mechanism for applying a pressing force in the axial direction to the clutch mechanism 3, a pressing force detection unit 5 for detecting the magnitude of the pressing force by the cam mechanism 4, and the rotation of the input shaft 10 is decelerated. Deceleration mechanism 6, switching mechanism 7 for switching each mode, and auxiliary driving force for transmitting a part of the driving force transmitted from input shaft 10 to first output shaft 11 to second output shaft 12 as an auxiliary driving force And a transmission mechanism 8.

  The first output shaft 11 transmits a driving force between the input shaft 10 and the propeller shaft 97 on the rear wheel side, and at least a part of the first output shaft 11 is accommodated in the case member 2. In the present embodiment, the rear end of the first output shaft 11 is exposed from the case member 2, and the mounting flange 11A is fixed to the exposed end. The second output shaft 12 is arranged in parallel with the first output shaft 11, the front end is exposed from the case member 2, and the mounting flange 11 </ b> B is fixed to the exposed end.

  The auxiliary driving force transmission mechanism 8 includes a cylindrical rotating member 80 that is coaxially supported with the first output shaft 11 and is rotatably supported. The cylindrical rotating member 80 is torqued to the first output shaft 11 by the clutch mechanism 3. Connected as possible. A first spline engaging portion 80a is formed on the outer peripheral surface of the front end portion of the cylindrical rotating member 80, and a second spline engaging portion 80b is formed on the outer peripheral surface of the rear end portion of the cylindrical rotating member 80. Is formed. Here, the first output shaft 11 is an aspect of the first rotating member of the present invention, and the cylindrical rotating member 80 is an aspect of the second rotating member of the present invention.

  Among the components of the transfer device 1, the first output shaft 11, the clutch mechanism 3, the cam mechanism 4, the pressing force detection unit 5, and the cylindrical rotating member 80 are auxiliary to the left and right front wheels 901 and 902 that are auxiliary driving wheels. A driving force transmission device 1A that transmits the driving force is configured.

  The case member 2 has a first case member 21 disposed on the front side and a second case member 22 disposed on the rear side, and the first case member 21 and the second case member 22 are coupled by a bolt 200. ing. The case member 2 includes a first lid member 23 disposed so as to cover the opening 210 into which the input shaft 10 is inserted in the first case member 21, and the first output shaft 11 is inserted in the second case member 22. And a second lid member 24 arranged so as to cover the opening 220. The first lid member 23 is fixed to the first case member 21 by bolts 201, and the second lid member 24 is fixed to the second case member 22 by bolts 203. Lubricating oil (not shown) is accommodated in the case member 2.

  The input shaft 10 and the first output shaft 11 are supported so as to be relatively rotatable on the same rotation axis O. The input shaft 10 has a cylindrical portion 100 at the end accommodated in the case member 2, and is between the outer peripheral surface of the first output shaft 11 inserted into the cylindrical portion 100 and the inner peripheral surface of the cylindrical portion 100. Needle roller bearings 13 are arranged on the top. Further, an outer peripheral spline engaging portion 101 a is formed on the outer peripheral surface of the tip portion 101 of the cylindrical portion 100.

  The first output shaft 11 is rotatably supported by the case member 2 by a ball bearing 14 fitted to the inner surface 220 a of the opening 220 in the second case member 22. As shown in FIG. 3, the ball bearing 14 has an outer ring 141 fitted to the inner surface 220 a of the opening 220 and an inner ring 142 fitted to the first output shaft 11. A plurality of spherical balls 143 are arranged between the outer ring 141 and the inner ring 142 so as to be able to roll. The axial movement of the outer ring 141 relative to the case member 2 is restricted by a snap ring 144 sandwiched between the second case member 22 and the second lid member 24.

  The first output shaft 11 includes a first cylindrical portion 111 having a first spline engaging portion 111a formed on the outer peripheral surface, a second cylindrical portion 112 having a second spline engaging portion 112a formed on the outer peripheral surface, It has the 3rd cylindrical part 113 in which the track surface 113a where the rolling element of the needle roller bearing 15 rolls was formed in the outer peripheral surface. The first cylindrical portion 111 is formed on the front side of the third cylindrical portion 113, and the second cylindrical portion 112 is formed on the rear side of the third cylindrical portion 113. The first cylindrical portion 111 is formed with a larger diameter than the second cylindrical portion 112 and the third cylindrical portion 113. A step surface 111b (shown in FIG. 3) is formed at the end of the first cylindrical portion 111 on the third cylindrical portion 113 side.

(Configuration of deceleration mechanism 6)
The speed reduction mechanism 6 includes a planetary gear mechanism, and includes a plurality of planetary gears 61 that mesh with gear teeth 100a formed on the outer peripheral surface of the cylindrical portion 100 of the input shaft 10, and a support member 62 that rotatably supports the planetary gear 61. And an internal gear 63 fixed to the first case member 21. The support member 62 includes a plurality of support shafts 621 that are respectively inserted through the central portions of the plurality of planetary gears 61, a first annular support member 622 that supports the plurality of support shafts 621 on the front side, and a plurality of support shafts 621. The second annular support member 623 is supported on the opposite side (rear side) to the first annular support member 622. The first support annular member 622 is rotatably supported by the case member 2 by a ball bearing 60. The speed reduction mechanism 6 decelerates the rotation of the input shaft 10 and outputs it from the second annular support member 623.

(Configuration of switching mechanism 7)
The switching mechanism 7 is formed on the drum 72, an electric motor 70, a positioning rod 71 that is rotationally driven by the electric motor 70, a cylindrical drum 72 that is externally fitted to the positioning rod 71, and rotates together with the positioning rod 71. A first shift fork 73 having a protrusion 73a engaging with the first guide groove 72a, a second shift fork 74 having a protrusion 74a engaging with a second guide groove 72b formed on the drum 72, and a first shift fork 73, a first switching sleeve 75 that moves forward and backward along the rotational axis O together with 73, a second switching sleeve 76 that moves forward and backward along the rotational axis O together with the second shift fork 74, and a second annular support member 623 of the speed reduction mechanism 6. And a connecting member 77 connected so as not to be relatively rotatable.

  A worm 701 is formed on the output shaft 700 of the electric motor 70, and the worm 701 meshes with the worm wheel 702. The worm wheel 702 is connected to one end portion of the reduction gear 703 so as not to be relatively rotatable, and the other end portion of the reduction gear 703 meshes with the input gear 710 of the positioning rod 71. The positioning rod 71 has a front end rotatably supported on the first case member 21 by a ball bearing 151, and a rear end supported rotatably on the second case member 22 by a ball bearing 152. .

  The first switching sleeve 75 has an inner peripheral spline engaging portion 75a on the inner peripheral surface and an outer peripheral spline engaging portion 75b on the outer peripheral surface. The second switching sleeve 76 has an inner peripheral spline engaging portion 76a on the inner peripheral surface. The first switching sleeve 75 and the second switching sleeve 76 have a cylindrical shape that is externally fitted to the first output shaft 11.

  FIG. 4 is a schematic diagram showing the first guide groove 72 a and the second guide groove 72 b formed in the drum 72, and the protrusion 73 a of the first shift fork 73 and the protrusion 74 a of the second shift fork 74. In FIG. 4, the horizontal direction indicates a direction parallel to the rotation axis O, and the vertical direction indicates the circumferential direction of the drum 72.

  When the drum 72 rotates, the projection 73a of the first shift fork 73 is guided by the first guide groove 72a, and the first shift fork 73 moves in the axial direction along the rotation axis O, and accordingly, the first switching sleeve. 75 also moves in the axial direction. Further, the projection 74a of the second shift fork 74 is guided by the second guide groove 72b, and the second shift fork 74 moves in the axial direction along the rotation axis O, and accordingly, the second switching sleeve 76 is similarly moved to the shaft. Move in the direction.

  When the relative position between the drum 72 and the protrusion 73 a of the first shift fork 73 is the position A shown in FIG. 4, the inner peripheral spline engaging portion 75 a of the first switching sleeve 75 is the first cylinder of the first output shaft 11. The outer peripheral spline engaging portion 75 b is engaged with the spline engaging portion 771 of the connecting member 77. Thereby, the connection member 77 and the 1st output shaft 11 are connected so that relative rotation is impossible.

  Further, when the relative position between the drum 72 and the projection 73a of the first shift fork 73 is the position B or C shown in FIG. 4, the relationship between the outer peripheral spline engaging portion 75b and the spline engaging portion 771 of the connecting member 77. The engagement is released, and the inner peripheral spline engaging portion 75 a of the first switching sleeve 75 is engaged with the first spline engaging portion 111 a of the first output shaft 11 and the outer peripheral spline engaging portion 101 a of the input shaft 10. Thereby, the input shaft 10 and the 1st output shaft 11 are connected so that relative rotation is impossible.

  Further, when the relative position between the drum 72 and the protrusion 74a of the second shift fork 74 is the position A or B shown in FIG. 4, the inner peripheral spline engaging portion 76a of the second switching sleeve 76 has the first output shaft. 11 first spline engaging portions 111 a and the first spline engaging portion 80 a of the cylindrical rotating member 80. Thereby, the 1st output shaft 11 and the cylindrical rotation member 80 are connected so that relative rotation is impossible.

  Further, when the relative position between the drum 72 and the protrusion 74a of the second shift fork 74 is the position C shown in FIG. 4, the inner peripheral spline engaging portion 76a of the second switching sleeve 76 and the first rotation of the cylindrical rotating member 80 are arranged. The engagement with the 1 spline engaging portion 80 a is released, and the inner peripheral spline engaging portion 76 a of the second switching sleeve 76 engages only with the first spline engaging portion 111 a of the first output shaft 11. Thereby, relative rotation between the first output shaft 11 and the cylindrical rotating member 80 becomes possible.

  When the relative positions of the drum 72 and the projection 73a of the first shift fork 73 and the projection 74a of the second shift fork 74 are the positions A shown in FIG. 4, the transfer device 1 is in the L4L mode and is decelerated by the reduction mechanism 6. The driving force of the input shaft 10 is transmitted to the first output shaft 11 and the cylindrical rotating member 80.

  When the relative position between the drum 72 and the projection 73a of the first shift fork 73 and the projection 74a of the second shift fork 74 is the position B shown in FIG. 4, the transfer device 1 is in the H4L mode, and the input shaft 10 is in the first position. The output shaft 11 and the cylindrical rotating member 80 are connected so as not to rotate relative to each other.

  When the relative position between the drum 72 and the projection 73a of the first shift fork 73 and the projection 74a of the second shift fork 74 is the position C shown in FIG. 4, the transfer device 1 is in the H2 mode or H4 mode, and the input shaft 10 And the first output shaft 11 are connected so as not to rotate relative to each other, and in the H4 mode, driving force is distributed from the first output shaft 11 to the cylindrical rotating member 80 via the clutch mechanism 3.

(Configuration of clutch mechanism 3)
As shown in FIG. 3, the clutch mechanism 3 includes a clutch drum 31, a multi-plate clutch 32 disposed between the clutch drum 31 and the cylindrical rotating member 80, and an annular pressing plate that presses the multi-plate clutch 32. 34 and an urging member 35 that urges the pressing plate 34 in a direction in which the pressing plate 34 is separated from the multi-plate clutch 32.

  The multi-plate clutch 32 includes a plurality of outer clutch plates 321 engaged with the clutch drum 31 so as not to rotate relative to the clutch drum 31 and movable in the axial direction, and a plurality of clutches engaged with the cylindrical rotating member 80 so as not to rotate relative to the cylinder drum 80 and movable in the axial direction. The outer clutch plate 322 and the inner clutch plate 322 are alternately arranged.

  The clutch drum 31 includes an annular engagement portion 311 that engages with the first output shaft 11 in a relatively non-rotatable manner, a disk portion 312 that projects radially outward from the engagement portion 311, and an outer peripheral side of the disk portion 312. A cylindrical cylindrical portion 313 extending from the end portion in parallel to the rotation axis O is provided. An inner peripheral spline engaging portion 311 a that engages with the second spline engaging portion 112 a of the second cylindrical portion 112 in the first output shaft 11 is formed on the inner periphery of the engaging portion 311.

  On the inner periphery of the cylindrical portion 313, an inner peripheral spline engaging portion 311a is formed in which the outer peripheral end of the outer clutch plate 321 is engaged so as not to be relatively rotatable. An inner circumferential end of the inner clutch plate 322 is engaged with the second spline engaging portion 80b of the cylindrical rotating member 80 so as not to be relatively rotatable.

  The pressing plate 34 is formed with a circumferential groove 34 a that is fitted to the tip of the cylindrical portion 313 of the clutch drum 31. The pressing plate 34 can move back and forth in the direction of the rotation axis O in a state where the concave groove 34 a is fitted to the tip of the cylindrical portion 313. The pressing plate 34 moves to the disk portion 312 side (rear side) of the clutch drum 31 to sandwich the multi-plate clutch 32 between the pressing plate 34 and the plurality of outer clutch plates 321 and the plurality of inner clutch plates 322. And press. As a result, a frictional force is generated between the plurality of outer clutch plates 321 and the plurality of inner clutch plates 322, and torque is transmitted from the clutch drum 31 to the cylindrical rotating member 80 by this frictional force.

  Further, the pressing plate 34 is urged to the opposite side (front side) from the disk portion 312 by the urging member 35. In the present embodiment, the urging member 35 is formed of a coil spring and is disposed on the outer periphery of the cylindrical portion 313. The urging member 35 has one end on the rear side in contact with a stepped surface 313 b formed on the outer peripheral surface of the cylindrical portion 313, and the other end on the front side is in contact with an end surface on the rear side of the pressing plate 34. The urging member 35 is disposed between the step surface 313b of the cylindrical portion 313 and the end surface of the pressing plate 34 in a state of being compressed in the axial direction, and elastically presses the pressing plate 34 toward the front side by its restoring force. Yes.

(Configuration of cam mechanism 4)
The cam mechanism 4 includes a first cam member 41 whose rotation with respect to the case member 2 is restricted, a second cam member 42 that moves toward the clutch mechanism 3 by rotating with respect to the first cam member 41, and a first cam A plurality of spherical rolling elements 43 disposed between the member 41 and the second cam member 42 are provided.

  FIG. 5A is a plan view showing a state in which the first cam member 41 is viewed from the rear side toward the front side. FIG. 5B is a plan view showing a state in which the second cam member 42 and the cam plate 44 for rotating the second cam member 42 with the rotation axis O as the rotation center are viewed from the front side toward the rear side. It is.

  The first cam member 41 includes an annular portion 411 in which an insertion hole 41a through which the cylindrical rotating member 80 is inserted is formed at the center, an annular piston pressing portion 412 formed on the outer periphery of the annular portion 411, and a piston pressing It integrally has a rod-shaped detent 413 protruding outward from a part of the outer peripheral surface of the portion 412. A plurality of cam grooves 411 a for rolling the rolling elements 43 are formed on the surface of the annular portion 411 facing the second cam member 42. The cam groove 411 a is formed in an arc shape in a predetermined angle range along the circumferential direction of the annular portion 411. The cam groove 411a is formed so that the groove depth in the axial direction of the annular portion 411 gradually changes in the circumferential direction.

  The piston pressing part 412 faces the piston 50 of the pressing force detection part 5 described later and presses the piston 50. The front end of the rotation stopper 413 comes into contact with the positioning rod 71. The rotation of the first cam member 41 with respect to the case member 2 is restricted by the rotation preventing portion 413 coming into contact with the positioning rod 71.

  The second cam member 42 includes an annular portion 421 in which an insertion hole 42 a for inserting the cylindrical rotating member 80 is formed in the center portion, and a flange portion 422 that extends outward from the outer peripheral surface of the annular portion 421. The roller 423 is provided so as to be able to roll at the front end of the flange 422. A sliding bearing 16 (shown in FIG. 3) is disposed between the annular portion 421 and the cylindrical rotating member 80.

  A plurality of cam grooves 421 a for rolling the rolling elements 43 are formed on the surface of the annular portion 421 facing the first cam member 41. The cam groove 421a is formed in an arc shape in a predetermined angle range along the circumferential direction of the annular portion 421, and the groove depth in the axial direction of the annular portion 421 is formed so as to gradually change in the circumferential direction. Thereby, when the 2nd cam member 42 rotates with respect to the 1st cam member 41, the rolling element 43 rolls cam groove 411a, 421a, and the 2nd cam member 42 moves to the clutch mechanism 3 side.

The second cam member 42 rotates around the rotation axis O by the rotation of the cam plate 44 that rotates together with the positioning rod 71. The cam plate 44 is formed so that the distance from the positioning rod 71 of the outer peripheral surface 44a gradually changes, and the annular portion 421 is rotated through the flange portion 422 by pressing the roller 423 that contacts the outer peripheral surface 44a. Let For example, when the cam plate 44 is rotated in the R ₁ direction in FIG. 5, the second cam member 42 is rotated in R ₂ direction around the rotational axis O, the rolling element 43 due to the relative rotation between the first cam member 41 It moves to the clutch mechanism 3 side by rolling.

  A needle roller bearing 17 is arranged between the second cam member 42 and the pressing plate 34 of the clutch mechanism 3 as shown in FIG. The second cam member 42 presses the multi-plate clutch 32 (the plurality of outer clutch plates 321 and the plurality of inner clutch plates 322) in the direction of the rotation axis O via the needle roller bearing 17 and the pressing plate 34.

(Configuration of pressing force detection unit 5)
The pressing force detector 5 receives the reaction force of the pressing force that presses the clutch mechanism 3 from the first cam member 41 of the cam mechanism 4 and detects the magnitude of the pressing force applied to the clutch mechanism 3 by this reaction force. . The pressing force detection unit 5 includes an annular piston 50 that is pressed along the rotation axis O direction by the piston pressing unit 412 of the first cam member 41, and a cylinder member 51 in which a pressure chamber 51a that accommodates the piston 50 is formed. And a pressure sensor 52 for measuring the pressure of the liquid L filled in the pressure chamber 51a. The liquid L is made of, for example, mineral oil and receives pressure from the piston 50.

  The pressure chamber 51a opens to the rear side (cam mechanism 4 side), accommodates a part of the piston 50, and is formed in an annular shape. The rear end surface of the piston 50 exposed from the pressure chamber 51 a is in contact with the first cam member 41 of the cam mechanism 4. Accordingly, the piston 50 moves in the axial direction together with the first cam member 41. Seal members 501 and 502 are disposed on the outer peripheral surface and inner peripheral surface of the piston 50 to seal between the inner surface of the pressure chamber 51a.

  The cylinder member 51 is formed with a communication passage 51b that allows the pressure chamber 51a and the pressure sensor 52 to communicate with each other. A part of the cylinder member 51 protrudes from the opening 211 formed in the first case member 21 to the outside of the case member 2, and the pressure sensor 52 is fixed to the protruding portion. The pressure sensor 52 is, for example, a diaphragm type pressure sensor, and measures the pressure of the liquid L in the pressure chamber 51a of the liquid L. The pressure sensor 52 outputs an electrical signal corresponding to the pressure measurement result to the control device 1a.

  The cylinder member 51 is restricted from moving forward along the rotational axis O by a needle roller bearing 18 disposed between the cylinder member 51 and the sprocket 81 of the auxiliary driving force transmission mechanism 8. The reaction force of the pressing force generated by the cam mechanism 4 is transmitted to the sprocket 81 via the piston 50, the cylinder member 51, and the needle roller bearing 18.

(Configuration of auxiliary driving force transmission mechanism 8)
The auxiliary driving force transmission mechanism 8 includes a cylindrical rotating member 80, a sprocket 81, and a chain 82 (shown by a two-dot chain line in FIG. 2) that transmits a driving force from the sprocket 81 to the second output shaft 12. Yes. An inner peripheral spline engaging portion 81 a is formed on the inner peripheral surface of the sprocket 81, and the inner peripheral spline engaging portion 81 a is engaged with the first spline engaging portion 80 a of the cylindrical rotating member 80. Thereby, the sprocket 81 rotates integrally with the cylindrical rotating member 80. Gear teeth 81 b that mesh with the chain 82 are formed on the outer peripheral surface of the sprocket 81.

  The axial movement of the sprocket 81 toward the front side with respect to the cylindrical rotating member 80 is restricted by a snap ring 83 fitted to the cylindrical rotating member 80. The snap ring 83 is disposed at a position that divides the first spline engaging portion 80a into the front side and the rear side. The first spline engaging portion 80a on the rear side of the snap ring 83 is engaged with the inner peripheral spline of the sprocket 81. The portion 81 a is engaged, and the inner spline engaging portion 76 a of the second switching sleeve 76 is engaged with the first spline engaging portion 80 a on the front side of the snap ring 83.

  The second output shaft 12 integrally has a shaft portion 121 supported by the case member 2 by ball bearings 191 and 192 and a gear portion 122 in which gear teeth 122a meshing with the chain 82 are formed on the outer peripheral surface. . The chain 82 meshes with the gear teeth 81b of the sprocket 81 and the gear teeth 122a of the gear portion 122 of the second output shaft 12, thereby providing auxiliary driving force from the sprocket 81 to the second output shaft 12 toward the left and right front wheels 901, 902. introduce.

(Reaction force receiving structure in the first output shaft 11)
Next, in the first output shaft 11, a structure that receives the pressing force applied to the clutch mechanism 3 by the cam mechanism 4 and the reaction force thereof will be described. The first output shaft 11 has a pressing force receiving portion 11a that receives the pressing force of the cam mechanism 4 via the clutch mechanism 3, and a reaction force receiving portion 11b that receives a reaction force of the pressing force. Hereinafter, the pressing force receiving portion 11a and the reaction force receiving portion 11b will be specifically described.

  In the clutch drum 31 of the clutch mechanism 3, as described above, the inner peripheral spline engaging portion 311 a formed on the inner periphery of the engaging portion 311 engages with the second spline engaging portion 112 a of the first output shaft 11. Thus, the first output shaft 11 is connected so as not to rotate relative to the first output shaft 11 and to be movable in the axial direction. The axial movement of the clutch drum 31 toward the rear side is restricted by a snap ring 114 fitted to the first output shaft 11. The first output shaft 11 receives the pressing force generated by the cam mechanism 4 via the pressing plate 34, the multi-plate clutch 32, the clutch drum 31, and the snap ring 114 of the clutch mechanism 3.

  The snap ring 114 is partially accommodated in an annular groove 112 b formed at the end of the second spline engaging portion 112 a in the second cylindrical portion 112 of the first output shaft 11, and the first output shaft 11. It is fixed so that it cannot move in the axial direction. In the first output shaft 11, the portion where the annular groove 112 b is formed is a pressing force receiving portion 11 a that receives the pressing force of the cam mechanism 4. The first output shaft 11 receives a pressing force applied to the clutch mechanism 3 by the cam mechanism 4 at the pressing force receiving portion 11a.

  On the other hand, the reaction force of the pressing force generated by the cam mechanism 4 is transmitted to the sprocket 81 via the piston 50, the cylinder member 51, and the needle roller bearing 18 as described above. The reaction force transmitted to the sprocket 81 is further transmitted to the cylindrical rotating member 80 via the snap ring 83, and transmitted from the cylindrical rotating member 80 to the first output shaft 11 via the needle thrust roller bearing 115. Is done. The needle-shaped thrust roller bearing 115 is between the step surface 111b between the first cylindrical portion 111 and the third cylindrical portion 113 of the first output shaft 11 and the axial end surface 80c on the front side of the cylindrical rotating member 80. Is arranged.

  In the first output shaft 11, the portion where the step surface 111 b is formed is a reaction force receiving portion 11 b that receives the reaction force of the pressing force of the cam mechanism 4. The first output shaft 11 receives a pressing force applied to the clutch mechanism 3 by the cam mechanism 4 at the pressing force receiving portion 11a.

  Moreover, in this Embodiment, the pressing force detection part 5 is arrange | positioned at the outer peripheral side of the 1st output shaft 11 between the pressing force receiving part 11a and the reaction force receiving part 11b. That is, the pressing force detection unit 5 is disposed on the front side of the pressing force receiving unit 11 a in the direction of the rotation axis O and on the rear side of the reaction force receiving unit 11 b and on the outer peripheral side of the first output shaft 11. . More specifically, the pressing force detection unit 5 is disposed on the outer peripheral side of the cylindrical rotating member 80, and the cylindrical rotating member 80 is opposite to the pressing force receiving unit 11 a in the direction of the rotation axis O of the first output shaft 11. It arrange | positions between the force receiving parts 11b.

(Operation of transfer device 1 in H4 mode)
Next, the operation of the transfer device 1 in the H4 mode will be described.

  In the H4 mode, as described above, by the operation of the switching mechanism 7 by the rotation of the electric motor 70, the input shaft 10 and the first output shaft 11 are connected by the second switching sleeve 76 so as not to be relatively rotatable, and the first output shaft The driving force is transmitted from 11 to the left and right rear wheels 903 and 904 through the propeller shaft 97 on the rear wheel side. When the electric motor 70 further rotates in this state, the rotation of the cam plate 44 causes the second cam member 42 to rotate with respect to the first cam member 41, and the rolling element 43 rolls on the cam grooves 411a and 421a. The second cam member 42 moves to the clutch mechanism 3 side. The moving force generated in the second cam member 42 becomes a pressing force for pressing the clutch mechanism 3.

  The clutch mechanism 3 receives the axial pressing force of the cam mechanism 4 and the plurality of outer clutch plates 321 and the plurality of inner clutch plates 322 of the multi-plate clutch 32 frictionally slide, and the first output shaft is generated by the friction force. The driving force is transmitted from 11 to the cylindrical rotating member 80. The driving force transmitted to the cylindrical rotating member 80 is further transmitted to the second output shaft 12 via the sprocket 81 and the chain 82. As a result, the driving force is transmitted to the left and right front wheels 901 and 902 via the propeller shaft 96 on the front wheel side.

  The torque transmitted to the cylindrical rotating member 80 via the clutch mechanism 3 can be adjusted by controlling the electric motor 70. That is, the distance between the first cam member 41 and the second cam member 42 (the amount of movement of the second cam member 42 toward the clutch mechanism 3) is such that the rolling element 43 is located at the deepest part of the cam grooves 411a and 421a. It changes according to the rotation angle of the second cam member 42 from the neutral state, and the rotation angle of the second cam member 42 changes according to the rotation position of the cam plate 44. Therefore, by controlling the control of the electric motor 70, the rotational position of the cam plate 44 is changed, the pressing force applied to the clutch mechanism 3 is increased or decreased, and is transmitted to the cylindrical rotating member 80 via the clutch mechanism 3. Torque can be adjusted.

However, the present inventors have determined that the pressing force applied to the clutch mechanism 3 is not necessarily determined only by the distance between the first cam member 41 and the second cam member 42 but varies depending on the rotation direction of the electric motor 70. It has been confirmed. For example, the torque cam plate 44 and the case to rotate the R ₁ direction shown in FIG. 5, in the case of rotating in the reverse direction, even in the rotational position of the cam plate 44 is the same, that is transmitted by the clutch mechanism 3 There will be a difference. This may be due to the hysteresis of the reduction mechanism of the output of the electric motor 70 by the worm 701, the worm wheel 702, and the reduction gear 703.

  Therefore, in the present embodiment, the reaction force of the pressing force applied to the clutch mechanism 3 is detected by the pressing force detection unit 5, and the electric motor 70 is controlled based on the detection result, so that the clutch mechanism 3 is interposed. Thus, the accuracy of the auxiliary driving force transmitted to the second output shaft 12 is increased. That is, the control device 1 a that controls the electric motor 70 can obtain information on the pressing force actually applied to the clutch mechanism 3 based on the electric signal from the pressing force detection unit 5, and based on this information By controlling the motor current supplied to the electric motor 70 in a feedback manner, the pressing force applied to the clutch mechanism 3 can be adjusted with high accuracy. Thereby, the accuracy of the auxiliary driving force transmitted to the second output shaft 12 is increased, and the running stability of the four-wheel drive vehicle 9 can be improved.

(Operation and effect of the embodiment)
According to the transfer device 1 and the driving force transmission device 1A according to the embodiment described above, the following operations and effects can be obtained.

(1) Since the first output shaft 11 has the pressing force receiving portion 11a and the reaction force receiving portion 11b, the first output shaft 11 is pivoted by the pressing force generated by the cam mechanism 4 or the reaction force thereof. Movement in the direction (direction of the rotation axis O) is suppressed. Thereby, the ball bearing (ball bearing 14) which has arrange | positioned the spherical rolling element between the inner ring | wheel and the outer ring | wheel as a bearing which supports the 1st output shaft 11 to the case member 2 is employable. That is, if the first output shaft 11 receives only one of the pressing force generated by the cam mechanism 4 and the reaction force thereof, the first output shaft 11 is supported against the axial thrust load in order to support the first output shaft 11. A tapered roller bearing having a high yield strength (tapered roller bearing) or a very large ball bearing must be used. On the other hand, in the present embodiment, since the first output shaft 11 has the pressing force receiving portion 11a and the reaction force receiving portion 11b, the rear side that the first output shaft 11 receives at the pressing force receiving portion 11a. The thrust load on the front side and the thrust load on the front side received by the reaction force receiving portion 11b are offset, and the first output shaft 11 can be supported by the relatively small ball bearing 14, and the transfer device 1 can be downsized. And it can contribute to cost reduction.

(2) Since the pressing force detection unit 5 is disposed on the outer peripheral side of the first output shaft 11 between the pressing force receiving unit 11a and the reaction force receiving unit 11b, transfer by providing the pressing force detection unit 5 is performed. The enlargement of the apparatus 1 is suppressed. In addition, by arranging the pressing force detection unit 5 in this way, the pressing force detection unit 5 can be appropriately interposed in the path of the pressing force and reaction force from the pressing force receiving unit 11a to the reaction force receiving unit 11b. It is possible to increase the detection accuracy of the pressing force.

(3) The pressing force detector 5 receives the reaction force of the pressing force of the cam mechanism 4 from the first cam member 41 whose rotation with respect to the case member 2 is restricted, and detects the magnitude of the pressing force. That is, since the reaction force of the pressing force is received from the non-rotating member with respect to the case member 2, it is not necessary to interpose a bearing between the piston 50 and the cam mechanism 4, for example. Thereby, the increase in a number of parts can be suppressed and it can contribute to size reduction and cost reduction of the transfer apparatus 1.

(4) The pressing force detection unit 5 measures the pressure in the pressure chamber 51 a of the liquid L that receives the pressure from the piston 50 moving in the axial direction together with the first cam member 41, so that the pressure L is detected via the piston 50 and the cylinder member 51. While transmitting the reaction force of the pressing force of the cam mechanism 4 from the first cam member 41 to the sprocket 81, the reaction force can be accurately detected. In addition, since the cylinder member 51 is parallel to the sprocket 81 whose position is regulated by the snap ring 83 in the axial direction via the needle roller bearing 18, the support structure is simple, and the transfer device 1 can be reduced in size. Cost reduction can be achieved.

  As described above, the transfer device and the driving force transmission device of the present invention have been described based on the above embodiment, but the present invention is not limited to the above embodiment and can be variously modified without departing from the scope of the present invention. It is possible to implement.

DESCRIPTION OF SYMBOLS 1 ... Transfer apparatus, 1a ... Control apparatus, 1A ... Driving force transmission device, 2 ... Case member, 3 ... Clutch mechanism, 4 ... Cam mechanism, 5 ... Pressing force detection part, 6 ... Deceleration mechanism, 7 ... Switching mechanism, 8 Auxiliary driving force transmission mechanism, 9 ... four-wheel drive vehicle, 10 ... input shaft, 11 ... first output shaft, 11A, 11B ... mounting flange, 11a ... pressing force receiving portion, 11b ... reaction force receiving portion, 12 ... first 2 output shafts, 12a ... bevel gears, 13 ... needle roller bearings, 14 ... ball bearings, 15 ... needle roller bearings, 16 ... sliding bearings, 17, 18 ... needle roller bearings, 21 ... first case member, 22 ... second case member, 23 ... first lid member, 24 ... second lid member, 31 ... clutch drum, 32 ... multi-plate clutch, 34 ... pressing plate, 34a ... concave groove, 35 ... biasing member, 41 ... first 1 cam member, 41a ... insertion hole, 42 ... second cam member, 42a ... insertion hole, 43 Rolling element, 44 ... cam plate, 44a ... outer peripheral surface, 50 ... piston, 51 ... cylinder member, 51a ... pressure chamber, 51b ... communication path, 52 ... pressure sensor, 60 ... ball bearing, 61 ... planet gear, 62 ... support 63, internal gear, 70 ... electric motor, 71 ... positioning rod, 72 ... drum, 72a ... first guide groove, 72b ... second guide groove, 73 ... first shift fork, 73a ... projection, 74 ... first 2-shift fork, 74a ... protrusion, 75 ... first switching sleeve, 75a ... inner peripheral spline engaging portion, 75b ... outer peripheral spline engaging portion, 76 ... second switching sleeve, 76a ... inner peripheral spline engaging portion, 77 ... Connecting member, 80 ... cylindrical rotating member, 80a ... first spline engaging portion, 80b ... second spline engaging portion, 80c ... end surface in the axial direction, 81 ... sprocket, 81a ... inner peripheral splatter Engagement portion, 81b ... gear teeth, 82 ... chain, 83 ... snap ring, 90 ... drive source, 91 ... transmission, 92 ... front differential, 94 ... rear differential, 96 ... propeller shaft on the front wheel side, 96a ... bevel gear 97 ... rear wheel side propeller shaft, 97a ... bevel gear, 100 ... cylindrical part, 100a ... gear teeth, 101 ... tip part, 101a ... outer peripheral spline engaging part, 111 ... cylindrical part, 111a ... first spline engaging 111b ... step surface, 112 ... second cylindrical portion, 112a ... second spline engaging portion, 112b ... annular groove, 113 ... third cylindrical portion, 113a ... track surface, 114 ... snap ring, 115 ... acicular thrust Roller bearing, 121 ... shaft, 122 ... gear, 122a ... gear, 141 ... outer ring, 142 ... inner ring, 143 ... ball, 144 ... Snap ring, 151,152 ... Ball bearing, 191,192 ... Ball bearing, 200,201,203 ... Bolt, 210 ... Opening, 211 ... Opening, 220 ... Opening, 311 ... Engagement part, 311a ... Inner circumference spline Joint part, 312 ... disk part, 313 ... cylindrical part, 313b ... step surface, 321 ... outer clutch plate, 322 ... inner clutch plate, 411 ... annular part, 411a ... cam groove, 412 ... piston pressing part, 413 ... non-rotating 421 ... annular part, 421a ... cam groove, 422 ... collar part, 423 ... roller, 501 and 502 ... seal member, 621 ... support shaft, 622 ... first annular support member, 623 ... second annular support member, 700 ... Output shaft, 701 ... Worm, 702 ... Worm wheel, 703 ... Reduction gear, 710 ... Input gear, 771 ... Spline engaging part, 90 Car body, 901 ... Left front wheel, 902 ... Right front wheel, 903 ... Left rear wheel, 904 ... Right rear wheel, 920 ... Differential case, 921 ... Ring gear, 922 ... Pinion shaft, 923 ... Pinion gear, 924 ... Side gear, 931, 932 ... Drive shaft, 940 ... differential case, 941 ... ring gear, 942 ... pinion shaft, 943 ... pinion gear, 944 ... side gear, 951, 952 ... drive shaft, L ... liquid

Claims (4)

A shaft-shaped first rotating member for transmitting a driving force;
A case member that houses at least a part of the first rotating member;
A bearing that rotatably supports the first rotating member on the case member;
A cylindrical second rotating member supported coaxially with the first rotating member so as to be relatively rotatable;
A clutch mechanism for receiving a pressing force in the axial direction and coupling the first rotating member and the second rotating member so as to transmit torque;
A pressing mechanism for applying the pressing force to the clutch mechanism;
A pressing force detection unit for detecting the magnitude of the pressing force;
The first rotating member has a pressing force receiving portion that receives the pressing force via the clutch mechanism, and a reaction force receiving portion that receives a reaction force of the pressing force,
The pressing force detection unit is disposed on the outer peripheral side of the first rotating member between the pressing force receiving unit and the reaction force receiving unit.
Transfer device. The pressing mechanism includes a first cam member whose rotation with respect to the case member is restricted, and a second cam member that moves toward the clutch mechanism by rotating with respect to the first cam member,
The pressing force detector receives a reaction force of the pressing force from the first cam member and detects the magnitude of the pressing force;
The transfer device according to claim 1. The pressing force detection unit includes a piston that moves in the axial direction together with the first cam member, a cylinder member in which a pressure chamber in which liquid that receives pressure from the piston is sealed is formed, and the liquid in the pressure chamber. A pressure sensor for measuring pressure,
The transfer device according to claim 1 or 2. A first rotating member rotatably supported by a case member via a bearing;
A second rotating member supported coaxially with the first rotating member so as to be relatively rotatable;
A clutch mechanism for receiving a pressing force in the axial direction and coupling the first rotating member and the second rotating member so as to transmit torque;
A pressing mechanism for applying the pressing force to the clutch mechanism;
A pressing force detection unit for detecting the magnitude of the pressing force;
The first rotating member has a pressing force receiving portion that receives the pressing force via the clutch mechanism, and a reaction force receiving portion that receives a reaction force of the pressing force,
The pressing force detection unit is disposed on the outer peripheral side of the first rotating member between the pressing force receiving unit and the reaction force receiving unit.
Driving force transmission device.

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