JP2016101877A - Driving device of vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve reduction in the number of components, simplification of a structure and control, and compactification of a driving device by abolishing a dedicated actuator for operating clutch means in the driving device of a vehicle having a motor connected to a driving wheel through the clutch means.SOLUTION: The driving device of a vehicle includes: a planetary gear 60a/60b having an input element 63a, an output element 63b and a reaction force element 62; a motor 51 connected to the input element 63a; clutch means 70 for performing connection or disconnection between the output element 63b and a driving wheel 36; and a cam mechanism 80 connected to the reaction force element 62 for generating axial force by the torque acting on the reaction force element 62 when output of the motor 51 is input in the input element 63a, and fastening the clutch means 70.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a vehicle drive device having a motor coupled to drive wheels via a clutch means, and belongs to the field of vehicle power transmission technology.

  2. Description of the Related Art In recent years, various types of vehicle drive devices have been proposed or put into practical use with the practical application of hybrid vehicles including an engine and a motor as drive sources.

  For example, a vehicle disclosed in Patent Document 1 includes a motor in addition to a front-wheel drive device that includes an engine, a transmission, and a front-wheel differential device that is employed in a general front engine / front drive system (FF system). And a rear wheel drive device having a reduction gear and a rear wheel differential. This rear-wheel drive device includes a clutch mechanism for preventing the rear wheels from being accompanied by the motor when the front-wheel drive traveling by the engine is performed in a state where the drive of the motor is stopped.

  In the drive device for rear wheels of Patent Document 1, the clutch mechanism includes a multi-plate clutch provided between the reduction gear and the rear wheel differential, and an electromagnetic clutch mechanism for fastening the multi-plate clutch. It has. When front-wheel drive running by the engine is performed, the multi-plate clutch is released by turning off the electromagnetic clutch mechanism, and thereby the power transmission between the motor and the rear wheel is cut off, so that the rear wheel This prevents the motor from rotating around. On the other hand, when the electromagnetic clutch mechanism is turned on, the power of the motor is transmitted to the rear wheels via the speed reducer, the multi-plate clutch, and the rear wheel differential, thereby realizing a four-wheel drive state.

  Patent Document 2 discloses a front wheel differential device that transmits power output from an engine via a transmission to a front wheel, a transfer device that extracts power output from the engine via a transmission to a rear wheel, and a transfer device. A propeller shaft extending rearward, a rear wheel differential connected to the rear end of the propeller shaft via an electronic control coupling, a front wheel side clutch provided in the transfer device so as to connect and disconnect between the front wheel and the propeller shaft; There is disclosed a vehicle drive device including a rear wheel side clutch provided on a rear wheel side axle so as to connect and disconnect between a propeller shaft and a rear wheel, and a motor provided on the propeller shaft.

  In the drive device of Patent Document 2, the front wheel side and rear wheel side clutches are electromagnetic clutches that are on / off controlled by an actuator such as a solenoid valve. In the electronically controlled coupling, the fastening force is adjusted steplessly by electronic control. In the four-wheel drive state, the fastening force of the electronically controlled coupling is controlled and transmitted from the engine to the front and rear wheels. Torque distribution is controlled. Generally, this fastening force is controlled by controlling an electromagnetic clutch mechanism or the like.

  Further, in the drive device of Patent Document 2, the rotor of the motor is coupled to the propeller shaft, and when the front wheel side or rear wheel side clutch is fastened, the rotation speed of the propeller shaft is adjusted by driving the motor. It is configured so that smooth fastening is performed. When the front wheel side and rear wheel side clutches and the electronically controlled coupling are in the engaged state, the vehicle is in a four-wheel drive state, and when these are in the released state, the vehicle is in a front wheel drive state.

JP 2003-113874 A JP 2013-116697 A

  However, in the rear wheel drive device disclosed in Patent Document 1, it is necessary to further mount an electromagnetic clutch mechanism in order to engage and disengage the multi-plate clutch that connects and disconnects the rear wheel and the motor. As a result, the number of parts increases, the structure and control become complicated, and the size of the entire drive device increases.

  In addition, the drive device disclosed in Patent Document 2 is equipped with an actuator such as an electromagnetic clutch mechanism in order to control the fastening force of the electronically controlled coupling that switches between the front wheel drive state and the four wheel drive state. A similar problem will arise.

  Therefore, the present invention reduces the number of parts, structure and control by eliminating a dedicated actuator for operating the clutch means in a vehicle drive device having a motor coupled to the drive wheels via the clutch means. It is an object of the present invention to simplify the above and to make the drive device compact.

  In order to solve the above-described problems, a vehicle drive device according to the present invention is configured as follows.

First, a vehicle drive device according to claim 1 of the present application is
A planetary gear mechanism having an input element, an output element and a reaction force element;
A motor coupled to the input element;
Clutch means for connecting and disconnecting between the output element and the drive wheel;
A cam mechanism coupled to the reaction force element and generating an axial force by a torque acting on the reaction force element when the output of the motor is input to the input element, and fastening the clutch means. It is characterized by that.

According to a second aspect of the present invention, there is provided a vehicle drive device according to the first aspect of the present invention.
A drive source connected to the drive wheel is provided separately from the motor.

Furthermore, the vehicle drive device according to the invention of claim 3 is the invention of claim 1,
A drive source different from the motor;
A power transmission device that transmits the output of the drive source to one of the front wheels or the rear wheels;
A drive shaft for transmitting power from the power transmission device to the other of the front wheels or the rear wheels,
The clutch means is provided on the drive shaft.

  According to the first aspect of the present invention, the clutch means for connecting / disconnecting the motor and the driving wheel is mechanically released by the fact that no axial force is generated by the cam mechanism when the motor is stopped. At the time of rotation, it is mechanically fastened by the axial force generated by the cam mechanism. In this way, when the motor is turned on or off to start or stop the transmission of power from the motor to the drive wheels, the clutch means is mechanically engaged or disengaged, so that the clutch means is operated. Special actuators such as electromagnetic clutch mechanisms can be eliminated. Therefore, the number of parts can be reduced, the structure and control can be simplified, and the entire drive device can be made compact.

  Further, according to the invention described in claim 2, since the power transmission between the drive wheel and the output element of the planetary gear mechanism is cut off by stopping the driving of the motor, When the vehicle is running with power from a drive source different from the motor, the motor is prevented from being rotated by the drive wheels, thereby preventing the motor from over-rotating. Since the clutch means for preventing such over-rotation is mechanically fastened or released via the cam mechanism when the motor is turned on or off, a dedicated actuator for operating the clutch means can be eliminated. Effects can be obtained.

  According to the third aspect of the present invention, the clutch means is mechanically released so that the power transmission between the front wheels and the rear wheels is cut off while the motor is stopped. The two-wheel drive state in which only the front wheels or only the rear wheels are driven by a different drive source, and the clutch means is mechanically fastened so that the front wheels and the rear wheels are drivingly connected during driving of the motor. Thus, a four-wheel drive state is established. The clutch means that performs the switching function between the two-wheel drive and the four-wheel drive is mechanically fastened or released via the cam mechanism when the motor is turned on or off. The above-described effect can be obtained.

1 is an overall view showing a vehicle drive device according to a first embodiment of the present invention. It is sectional drawing which shows a part of drive device shown in FIG. FIG. 3 is an enlarged view of FIG. 2 showing a main part of the drive device shown in FIG. 1. It is sectional drawing which shows the cam mechanism of the drive device shown in FIG. It is a general view which shows the drive device of the vehicle which concerns on 2nd Embodiment of this invention. It is sectional drawing which shows a part of drive device shown in FIG. It is an enlarged view of FIG. 6 which shows the principal part of the drive device shown in FIG.

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

[First Embodiment]
The vehicle drive device 1 according to the first embodiment will be described with reference to FIGS.

  As shown in FIG. 1, the drive device 1 is mounted on an FF hybrid vehicle. As a vehicle driving source, for example, an engine 2 mounted in an engine room, and a right drive wheel 36, for example. And a motor 51 disposed on a drive shaft 30 connected to the motor. However, the motor 51 may be disposed on the drive shaft 40 connected to the left drive wheel 46.

  The engine 2 is a horizontal type, and a transaxle 3 is arranged in parallel on the left side of the engine 2 in the vehicle width direction, for example. The transaxle 3 includes, for example, a transmission 6 connected to the output shaft of the engine 2 via a torque converter 5 and a differential device 10 that transmits the output of the transmission 6 to the left and right drive shafts 30 and 40. ing.

  The transmission 6 is, for example, a stepped automatic transmission, but may be a manual transmission or a continuously variable transmission. The output gear 7 of the transmission 6 is meshed with a differential ring 14 that is fixed to the differential case 12 of the differential device 10, whereby the output of the engine 2 is transmitted via the transmission 6 to the differential case 12 of the differential device 10. Is transmitted to. The transmission mechanism and the differential device 10 of the transmission 6 are accommodated in the transaxle case 4.

  The differential device 10 and the left and right drive shafts 30, 40 connected thereto are disposed on the vehicle rear side with respect to the engine 2. The differential device 10 is disposed offset to the left side from the center in the vehicle width direction, and the right drive shaft 30 is longer than the left drive shaft 40.

  The drive shafts 30 and 40 include differential shaft members 31 and 41 connected to the differential 10 and intermediate shaft members 32 and 42 connected to the differential shaft members 31 and 41 through universal joints 34 and 44, respectively. And driving wheel side shaft members 33, 43 connected to the intermediate shaft members 32, 42 via universal joints 35, 45 on one end side and connected to driving wheels 36, 46 on the other end side. .

  In the differential device 10, a pair of pinion gears 16, 17 facing each other are rotatably provided on a pinion shaft 15 that penetrates the differential case 12, and the left and right side gears 18, straddle the pinion gears 16, 17. 19 is meshed. The differential case 12 is provided with left and right shaft insertion portions 12 a and 12 b corresponding to the side gears 18 and 19. The differential shaft members 31, 41 of the drive shafts 30, 40 are inserted into the shaft insertion portions 12a, 12b, and the distal ends of the differential shaft members 31, 41 are spline-fitted to the side gears 18, 19. As a result, the power transmitted from the transmission 6 to the differential case 12 of the differential device 10 is transmitted to the left and right drive shafts 30 and 40 so as to have a rotational difference corresponding to the traveling situation.

  On the right differential shaft member 31, 41, a clutch 70, a speed reducer 60, and a motor 51 are disposed in order from the differential 10 side. The motor 51, the speed reducer 60, and the clutch 70 are unitized in a state of being accommodated in the unit case 110, and constitute a motor unit 50. The motor unit 50 is disposed using a space generated behind the engine 2 and on the right side of the differential 10.

  As shown in FIG. 2, the unit case 110 includes a plurality of case members 111, 112, 113, and 114 that are coupled to each other. A case member 113 that constitutes an end of the unit case 110 on the outer side in the vehicle width direction is attached to a cylinder block of the engine 2 via a bracket 124.

  Further, the case member 113 includes a support portion 118 formed in a half crack shape so as to cover a half circumference of the differential side shaft member 31. A bracket 120 formed in a half-crack shape so as to cover the remaining half circumference of the differential-side shaft member 31 is opposed to the support portion 118, and the support portion 118 and the bracket 120 are coupled by a bolt 122. Yes. As a result, the end of the differential shaft member 31 on the drive wheel 36 side is supported on the inner peripheral surface of the cylindrical portion formed by the support portion 118 and the bracket 120 via the bearing 108.

  An oil seal 106 interposed between the differential side shaft member 31 and the case member 113 so as to allow relative rotation thereof is disposed at a position adjacent to the differential device 10 side of the bearing 108. .

  The motor unit 50 includes a cylindrical partition member 100 extending in the axial direction so as to partition the clutch 70, the speed reducer 60, the motor 51, and the differential side shaft member 31. The differential side shaft member 31 passes through the partition member 100, and a gap is provided between the inner peripheral surface of the partition member 100 and the outer peripheral surface of the differential side shaft member 31. The end of the partition member 100 on the differential device 10 side is press-fitted into an inner peripheral surface of a sleeve 72a described later via an O-ring 102. Thereby, the partition member 100 rotates integrally with the sleeve 72a. The end of the partition member 100 on the drive wheel 36 side is rotatably supported by the case member 113 via an oil seal 104 that allows relative rotation between the partition member 100 and the case member 113.

  The motor 51 includes a stator 52 fixed to the case member 112, a rotor 53 rotatably provided inside the stator 52, and an output shaft 54 fixed inside the rotor 53 so as to rotate integrally with the rotor 53. It has. The stator 52 is configured by winding a coil around a stator core made of a magnetic material. The rotor 53 is made of a cylindrical magnetic body, and rotates by a magnetic force generated when electric power is supplied to the stator 52. The output shaft 54 is disposed outside the partition member 100 with a gap, supported by the case member 112 via the bearing 55 on the differential device 10 side of the rotor 53, and on the drive wheel 36 side of the rotor 53. Are supported by the case member 113 via a bearing 56.

  The speed reducer 60 is disposed adjacent to the motor 51 in the axial direction with the bearing 55 interposed therebetween, and includes a first planetary gear mechanism 60a and a second planetary gear mechanism 60b disposed on the differential side shaft member 31. . The first planetary gear mechanism 60a and the second planetary gear mechanism 60b are arranged in the axial direction in this order from the motor 51 side.

  The first planetary gear mechanism 60a includes a first sun gear 61a as an input element, a first ring gear 62a as a reaction force element, and a first carrier 63a as an output element. Similarly, the second planetary gear mechanism 60b includes a second sun gear 61b as an input element, a second ring gear 62b as a reaction force element, and a second carrier 63b as an output element.

  The first ring gear 62 a and the second ring gear 62 b are an integral member composed of a common ring gear member 62. The ring gear member 62 is fitted inside the case member 112 without being fixed. The ring gear member 62 is fixed to the case member 111 via a cam mechanism 80 to be described later, and the rotation of the first and second ring gears 62a and 62b is restricted when the cam mechanism 80 operates.

  The first sun gear 61 a and the second sun gear 61 b are disposed outside the partition member 100 with a gap. The first sun gear 61a is provided integrally with the output shaft 54 of the motor 51, whereby the output of the motor 51 is input to the first sun gear 61a. The rotation input to the first sun gear 61a with the first ring gear 62a fixed is decelerated and output from the first carrier 63a.

  The second sun gear 61b is provided integrally with the first carrier 63a, whereby the output of the motor 51 decelerated by the first planetary gear mechanism 60a is input to the second sun gear 61b. The rotation input to the second sun gear 61b with the second ring gear 62b fixed is decelerated and output from the second carrier 63b.

  As described above, the output of the motor 51 is decelerated by the first planetary gear mechanism 60 a, and the decelerated output is further decelerated by the second planetary gear mechanism 60 b, and the differential case of the differential device 10 via the clutch 70. 12 is transmitted. By such two-stage deceleration, the torque transmitted from the motor 51 to the differential case 12 is sufficiently increased, so that the motor 51 can be reduced in size, thereby improving the onboard property of the motor unit 50. .

  By the way, in order to quickly and surely transmit power from the first sun gear 61a that is the input portion of the speed reducer 60 to the second carrier 63b that is the output portion, when the output of the motor 51 is input to the speed reducer 60. In addition, a reaction force needs to be generated in any of the rotating elements of the speed reducer 60.

  In this regard, since the ring gear member 62 is not connected to any member other than the first carrier 63a and the second carrier 63b when the cam mechanism 80 described later is not operated, the output of the motor 51 is the first sun gear. When input to 61a, no reaction force is generated in the first ring gear 62a and the second ring gear 62b. Further, in the released state of the clutch 70, the second carrier 63b, which is the output part of the speed reducer 60, is not connected to any member located on the output side, so the output of the motor 51 is input to the first sun gear 61a. At this time, no reaction force is generated in the second carrier 63b and the second sun gear 61b, the first carrier 63a and the first sun gear 61a located on the input side thereof.

  Therefore, in the present embodiment, the friction member 66 that is always in contact with the first carrier 63a is attached to the case member 112, so that when the output of the motor 51 is input to the first sun gear 61a, the first carrier 63a. Reaction force can be generated. A plurality of friction members 66 are provided at intervals in the circumferential direction. Each friction member 66 is disposed so as to contact the side surface of the first carrier 63a on the motor 51 side and is axially moved toward the differential device 10 by an elastic member 67 provided in the wall portion 112a of the case member 112. It is energized. However, in order to suppress the rotational resistance of the first carrier 63a, it is preferable that the pressing force of the friction member 66 against the first carrier 63a is a minimum force that can generate a required reaction force on the first carrier 63a. .

  The clutch 70 is disposed adjacent to the speed reducer 60 in the axial direction with a cam mechanism 80 described later interposed therebetween. The clutch 70 includes a hub 71 provided integrally with the second carrier 63b so as to extend in the axial direction from the inner peripheral end of the second carrier 63b of the second planetary gear mechanism 60b toward the differential device 10, and an outer side of the hub 71. And a drum 72 disposed on the surface.

  As shown in FIG. 3, between the hub 71 and the drum 72, a plurality of friction plates 73 that are alternately engaged with these are disposed substantially perpendicular to the axial direction. A pressing member 76 that fastens these friction plates 73 is disposed on the reduction gear 60 side of these friction plates 73. The pressing member 76 is a disk-shaped member disposed substantially perpendicular to the axial direction. The outer peripheral end of the pressing member 76 is splined to the drum 72. A sleeve 72 a that extends in the axial direction toward the differential device 10 is provided at the inner peripheral end of the drum 72. The distal end of the sleeve 72 a extends toward the differential device 10 rather than the distal end of the case member 114 so as to protrude to the outside of the unit case 110.

  The outer peripheral surface at the tip of the sleeve 72 a is spline-fitted to the inner peripheral surface of the right shaft insertion portion 12 a in the differential case 12 of the differential device 10. Thereby, the sleeve 72a rotates integrally with the differential case 12. When the clutch 70 is engaged and the second carrier 63b, which is the output part of the speed reducer 60, and the differential case 12 are connected, the power of the motor 51 is transmitted to the differential case 12 via the speed reducer 60. It is like that. As a result, the power of the engine 2 and the power of the motor 51 are combined in the differential case 12, and the combined power is transmitted to the drive wheels 36 and 46 via the drive shafts 30 and 40.

  In the unit case 110, a gear type oil pump 90 is disposed on the differential device 10 side of the clutch 70. The oil pump 90 is disposed on the sleeve 72a, and is positioned in the axial direction by being sandwiched by the two case members 111 and 114 from both sides in the axial direction. The oil pump 90 is driven by the rotation of the sleeve 72a. The oil discharged from the oil pump 90 is supplied to the space outside the partition member 100 and inside the unit case 110, whereby the motor 51 can be cooled and the speed reducer 60 and the clutch 70 can be lubricated. Yes.

  The configuration of the cam mechanism 80 will be described with reference to FIGS. 3 and 4. 4 is a cross-sectional view of a part of the cam mechanism 80 as viewed from the radial direction. More specifically, FIG. 4 (a) is a non-operating state of the cam mechanism 80, and FIG. 4 (b) is a cam mechanism. 80 operating states are shown respectively.

  The cam mechanism 80 includes a pilot cam 81 integrally provided at an end portion of the ring gear member 62 on the differential device 10 side, a main cam 83 disposed to face the pilot cam 81, and between the pilot cam 81 and the main cam 83. A ball cam mechanism including a plurality of intervening balls 86.

  The pilot cam 81 is provided in a ring shape over the entire circumference of the end portion of the ring gear member 62 on the differential device 10 side. The pilot cam 81 is disposed on the radially outer side of the second carrier 63b so as to overlap the second carrier 63b in the axial direction. The pilot cam 81 is provided with a cam groove 82 opened to the differential device 10 side. The cam grooves 82 are, for example, triangular grooves extending in the radial direction, and a plurality of cam grooves 82 are provided at intervals in the circumferential direction.

  The main cam 83 is a disk-shaped member disposed substantially perpendicular to the axial direction, and faces the pilot cam 81 over the entire circumference. The main cam 83 is disposed between the pressing member 76 and the pilot cam 81 in the axial direction. The inner diameter of the main cam 83 is smaller than the inner diameter of the pilot cam 81, and the outer diameter of the main cam 83 is larger than the outer diameter of the pilot cam 81. A cam groove 84 opened to the pilot cam 81 side is provided at each portion of the main cam 83 that faces the cam groove 82 of the pilot cam 81. The cam groove 84 is, for example, a groove having a triangular cross section that extends in the radial direction.

  The outer peripheral end portion of the main cam 83 is spline-fitted to the inner peripheral surface of the case member 111, so that the main cam 83 is fixed to the unit case 110 so as not to rotate but to move in the axial direction. A thrust bearing 78 is interposed between the main cam 83 and the pressing member 76, so that relative rotation between the main cam 83 and the pressing member 76 is allowed. The thrust bearing 78 is disposed opposite to the radially inner portion of the main cam 83 with respect to the cam groove 84.

  Balls 86 are provided at opposing portions between the cam grooves 82 and 84 of the pilot cam 81 and the main cam 83. Each ball 86 is held between the pilot cam 81 and the main cam 83 in a state of being fitted into the cam groove 82 of the pilot cam 81 and the cam groove 84 of the main cam 83.

  As described above, the main cam 83 cannot rotate with respect to the unit case 110, whereas the ring gear member 62 integrated with the pilot cam 81 can rotate with respect to the unit case 110. Therefore, as shown in FIG. 4B, when the output of the motor 51 is input to the speed reducer 60, the torque of the first sun gear 61a acts on the ring gear member 62 via the first carrier 63a. The power in the circumferential direction A acting on the pilot cam 81 integrated with the member 62 is converted into power in the axial direction B via the ball 86 and transmitted to the main cam 83. As a result, the main cam 83 moves slightly in the axial direction so as to move away from the pilot cam 81, and the pressing member 76 of the clutch 70 is pressed toward the differential device 10 in the axial direction by the main cam 83. A plurality of friction plates 73 arranged in the axial direction on the differential device 10 side of 76 are fastened.

  When the clutch 70 is thus engaged, the power transmission state is established between the speed reducer 60 and the differential case 12, and the power of the motor 51 can be transmitted to the drive shafts 30 and 40 via the differential case 12. Therefore, when the vehicle is running with the power of the engine 2, the torque transmitted to the drive shafts 30 and 40 can be increased by further driving the motor 51.

  On the other hand, when the motor 51 is stopped, as shown in FIG. 4A, no torque is generated in the ring gear member 62 and the pilot cam 81, so that no axial force is generated in the main cam 83. The clutch 70 is released. Therefore, when the driving of the motor 51 is stopped and the vehicle is running only with the power of the engine 2, the power transmission between the differential case 12 and the speed reducer 60 is cut off by the release of the clutch 70. 46, the rotation of the motor 51 is prevented, and the rotation transmitted from the drive wheels 36, 46 is accelerated by the speed reducer 60 and input to the motor 51, thereby preventing the motor 51 from over-rotating. Is done.

  As described above, the clutch 70 is connected to the speed reducer 60 via the cam mechanism 80 having the simple configuration as described above, so that when the motor 51 is driven, the clutch 70 is mechanically driven by the axial force of the cam mechanism 80. When the motor 51 is stopped, the cam mechanism 80 is not operated and is mechanically released. Therefore, it is not necessary to provide a dedicated actuator such as an electromagnetic clutch mechanism or to control the operation of the actuator in order to engage or disengage the clutch 70. Thus, the clutch 70 is engaged or released.

  The cam mechanism 80 includes a ring-shaped pilot cam 81 provided integrally with the ring gear member 62 of the speed reducer 60, a disk-shaped main cam 83 disposed to face the pilot cam 81, and the pilot cam 81 and the main cam 83. It has a simple and compact structure consisting of balls 86 interposed therebetween.

  Therefore, a simple and compact cam mechanism 80 is used in place of an actuator having a large and complicated structure as provided for the operation of a clutch for preventing the motor from rotating in a conventional hybrid vehicle. As a result, the number of parts can be reduced, the structure and control can be simplified, and the entire driving device 1 can be made compact.

[Second Embodiment]
A vehicle drive device 201 according to the second embodiment will be described with reference to FIGS.

  As shown in FIG. 5, the drive device 201 is mounted on a hybrid vehicle that can be switched between a front-wheel drive state and a four-wheel drive state, and is mounted on, for example, an engine room as a vehicle drive source. The engine 202 and a motor 251 disposed on the propeller shaft 220 are provided.

  The engine 202 is a horizontal type, and a transmission 206 is connected to an output shaft of the engine 202 via, for example, a torque converter 205. The transmission 206 is, for example, a stepped automatic transmission, but may be a manual transmission or a continuously variable transmission. The transmission 206 constitutes a power transmission device for the front wheels 215 and 216 together with the front wheel differential device 210. Specifically, the output of the engine 202 is transmitted to the front wheel differential device 210 via the transmission 206, and the power transmitted to the front wheel differential device 210 has a rotational difference corresponding to the traveling state. It is transmitted to the left and right drive shafts 213 and 214 connected to the front wheels 215 and 216.

  On one drive shaft 213, a transfer device 212 for taking out the output of the engine 202 transmitted to the front wheel differential device 210 via the transmission 206 to the rear wheels 235, 236 side is disposed. The transfer device 212 is connected to the front wheel differential device 210 on the input side, and is connected to the propeller shaft 220 via the universal joint 224 on the output side.

  The propeller shaft 220 transmits the power extracted by the transfer device 212 to the rear wheels 235 and 236, and includes a front shaft 221 extending rearward from the universal joint 224 and a rear shaft 221 via the universal joint 225. And a rear shaft 222 connected to the end portion.

  A clutch 270 is provided on the rear shaft 222 of the propeller shaft 220. The rear shaft 222 is divided into a first rear shaft 222a that extends forward from the clutch 270 and a second rear shaft 222b that extends rearward from the clutch 270. Has been. Power transmission between the first rear shaft 222a and the second rear shaft 222b is connected or disconnected by fastening or releasing of the clutch 270. On the second rear shaft 222b, the motor 251 and a speed reducer 260 that decelerates the output of the motor 251 and transmits it to the propeller shaft 220 are disposed.

  The clutch 270, the speed reducer 260, and the motor 251 are arranged side by side in this order on the propeller shaft 220 from the front side of the vehicle. It is composed.

  The rear end portion of the second rear shaft 222b of the propeller shaft 220 is connected to the rear wheel differential device 230. Thus, when the clutch 270 is engaged, the power of the engine 2 taken out from the transfer device 212 is transmitted to the rear wheel differential device 230 via the propeller shaft 220 and is transmitted to the rear wheel differential device 230. The power is transmitted to the left and right drive shafts 233 and 234 connected to the rear wheels 235 and 236 so as to have a rotation difference according to the traveling state.

  According to the vehicle drive device 201 configured as described above, the four-wheel drive state is established when the clutch 270 is engaged, and the front wheel drive state is established when the clutch 270 is released.

  The configuration of the motor unit 250 will be described with reference to FIGS. 6 and 7.

  As shown in FIG. 6, the unit case 310 includes a plurality of case members 311, 312, 313, and 314 coupled to each other. The case member 113 constituting the end portion of the unit case 310 on the vehicle rear side is coupled to the housing 231 of the rear wheel differential device 230.

  The motor 251 includes a stator 252 fixed to the case member 312, a rotor 253 rotatably provided inside the stator 252, and an output shaft 254 fixed inside the rotor 253 so as to rotate integrally with the rotor 253. It has. The stator 252 is configured by winding a coil around a stator core made of a magnetic material. The rotor 253 is formed of a cylindrical magnetic body and rotates by a magnetic force generated when electric power is supplied to the stator 252. The output shaft 254 is supported by the case member 312 via the bearing 255 on the vehicle front side of the rotor 253, and is supported by the case member 313 via the bearing 256 on the vehicle rear side of the rotor 253.

  The reduction device 260 is configured by, for example, one planetary gear mechanism that is disposed adjacent to the motor 251 in the axial direction with the bearing 255 interposed therebetween. The reduction gear 260 includes a sun gear 261 as an input element, a ring gear 262 as a reaction force element, and a carrier 263 as an output element.

  The ring gear 262 is fitted inside the case member 312 without being fixed. The ring gear 262 is fixed to the case member 311 via a cam mechanism 280 described later, and the rotation of the ring gear 262 is restricted by the operation of the cam mechanism 280.

  The sun gear 261 is provided integrally with the output shaft 254 of the motor 251, whereby the output of the motor 251 is input to the sun gear 261. The rotation input to the sun gear 261 with the ring gear 262 fixed is decelerated and output from the carrier 263.

  The clutch 270 is disposed adjacent to the speed reducer 260 in the axial direction with a cam mechanism 280 described later interposed therebetween. The clutch 270 includes a hub 271 provided integrally with the carrier 263 so as to extend in the axial direction from the inner peripheral end of the carrier 263 of the speed reducer 260 to the vehicle front side, and a drum 272 disposed outside the hub 271. I have.

  As shown in FIG. 7, between the hub 271 and the drum 272, a plurality of friction plates 273 that are alternately engaged with these are disposed substantially perpendicular to the axial direction. A pressing member 276 for fastening the friction plates 273 is disposed on the reduction gear 260 side of the friction plates 273. The pressing member 276 is a disk-shaped member that is disposed substantially perpendicular to the axial direction. The outer peripheral end of the pressing member 276 is spline fitted to the drum 272.

  A cylindrical portion 272 a extending in the axial direction toward the vehicle front side is provided at the inner peripheral end of the drum 272. A gear type oil pump 290 is disposed on the cylindrical portion 272a. The oil pump 290 is disposed in the unit case 310 on the vehicle front side of the clutch 270. The oil pump 290 is positioned in the axial direction by being sandwiched between the two case members 311 and 314 from both sides in the axial direction. The oil pump 290 is driven by the rotation of the cylindrical portion 272a. The oil discharged from the oil pump 290 is supplied to the space inside the unit case 310, whereby the motor 251 can be cooled and the speed reducer 260 and the clutch 270 can be lubricated.

  As shown in FIG. 6, an outer peripheral portion of a columnar base portion 272b having a diameter substantially the same as that of the cylindrical portion 272a is integrally provided at the front end portion of the cylindrical portion 272a. A shaft portion 272c constituting the first rear shaft 222a is provided at the center portion of the base portion 272b so as to extend integrally in the axial direction toward the vehicle front side.

  The shaft portion 272c has a smaller diameter than the cylindrical portion 272a and the base portion 272b. The tip of the shaft portion 272c extends to the front side of the vehicle so as to protrude to the outside of the unit case 310. A cylindrical connecting member 302 coupled to the universal joint 225 by a bolt 304 is spline fitted to the outer peripheral surface of the shaft portion 272c. The coupling member 302 is positioned in the axial direction with respect to the shaft portion 272c by being sandwiched from both sides in the vehicle front-rear direction by a nut 306 and a base portion 272b that are screwed into the front end portion of the shaft portion 272c. The shaft portion 272c is coupled to the universal joint 225 via the coupling member 302 coupled in this manner.

  The first rear shaft 222a including the shaft portion 272c configured as described above rotates integrally with the drum 272 of the clutch 270.

  On the other hand, the second rear shaft 222b includes a cylindrical member 320 extending in the axial direction and a shaft member 324 connected to the rear end portion of the cylindrical member 320.

  The cylindrical member 320 is disposed with a gap inward in the radial direction of the output shaft 254 of the motor 251 and the sun gear 261 of the speed reducer 260, protrudes forward from the front end portion of the sun gear 261, and the rear end of the output shaft 254 It protrudes backward from the part. The front end portion of the cylindrical member 320 is spline-fitted to the inner peripheral surface of the hub 271 of the clutch 270, so that the cylindrical member 320 rotates integrally with the hub 271 and the carrier 263. The rear end portion of the tubular member 320 is rotatably supported by the case member 313 via an oil seal 322 that allows relative rotation between the tubular member 320 and the case member 313.

  The front end portion of the shaft member 324 is spline-fitted to the inner peripheral surface of the cylindrical member 320, whereby the shaft member 324 and the cylindrical member 320 rotate together. The rear end side of the shaft member 324 is connected to an input portion (not shown) of the rear wheel differential device 230. The shaft member 324 is rotatably supported by the housing 231 of the rear wheel differential device 230 via a bearing 326, and a nut that supports the bearing 326 from the front side of the vehicle is provided on the outer periphery of the shaft member 324. 330 is screwed together.

  The second rear shaft 222b is always connected to the output shaft 254 of the motor 251 through the hub 271 and the speed reducer 260 of the clutch 270. Therefore, when the motor 251 is driven, the power of the motor 251 is transmitted to the rear wheels 235 and 236 via the speed reducer 260, the second rear shaft 222b, and the rear wheel differential device 230 regardless of whether the clutch 270 is engaged or disengaged. To the side.

  Further, when the clutch 270 is engaged, the power of the motor 251 is transmitted to the front wheels 215 and 216 via the speed reducer 260, the clutch 270, the first rear shaft 222 a, the front shaft 221, the transfer device 212, and the front wheel differential device 210. To the four-wheel drive state.

  The output of the motor 251 is decelerated by the speed reducer 260 and is also decelerated between the second rear shaft 222b and the rear wheel differential device 230. In the four-wheel drive state, the output of the motor 251 is also decelerated between the front shaft 221 and the transfer device 212. By performing such deceleration, the torque transmitted from the motor 251 to the drive wheel side is increased, so that the motor 251 or the motor unit 250 can be downsized. Improves.

  In addition, since the carrier 263 of the speed reducer 260 is always connected to the rear wheels 235 and 236 via the second rear shaft 222b, the carrier 263 is always connected when the output of the motor 251 is input to the speed reducer 260. Reaction force is generated. Therefore, in the second embodiment, power transmission from the sun gear 261 serving as the input unit to the carrier 263 serving as the output unit is performed quickly and reliably without providing the friction member 66 (see FIG. 3) in the first embodiment. be able to.

  As shown in FIG. 7, the cam mechanism 280 is a ball cam mechanism similar to the cam mechanism 80 of the first embodiment, and is disposed opposite to the pilot cam 281 and a pilot cam 281 that are integrally provided at the front end of the ring gear 262. The main cam 283 and a plurality of balls 286 interposed between the pilot cam 281 and the main cam 283 are provided.

  The pilot cam 281 is provided in a ring shape over the entire circumference of the front end portion of the ring gear 262. The pilot cam 281 is provided with a cam groove 282 opened to the front side of the vehicle. The cam grooves 282 are, for example, triangular grooves extending in the radial direction, and a plurality of cam grooves 282 are provided at intervals in the circumferential direction.

  The main cam 283 is a disk-shaped member disposed substantially perpendicular to the axial direction, and faces the pilot cam 281 over the entire circumference. In the axial direction, the main cam 283 is disposed between the pressing member 276 and the pilot cam 281. The inner diameter of the main cam 283 is smaller than the inner diameter of the pilot cam 281, and the outer diameter of the main cam 283 is larger than the outer diameter of the pilot cam 281. A cam groove 284 that opens to the pilot cam 281 side is provided at each portion of the main cam 283 that faces the cam groove 282 of the pilot cam 281. The cam groove 284 is a groove having, for example, a triangular cross section extending in the radial direction.

  The outer peripheral end of the main cam 283 is spline-fitted to the inner peripheral surface of the case member 311, whereby the main cam 283 is fixed to the unit case 310 so as not to rotate but to move in the axial direction. A thrust bearing 278 is interposed between the main cam 283 and the pressing member 276 so that relative rotation between the main cam 283 and the pressing member 276 is allowed. The thrust bearing 278 is disposed opposite to the radially inner portion of the main cam 283 with respect to the cam groove 284.

  Balls 286 are provided at opposing portions between the cam grooves 282 and 284 of the pilot cam 281 and the main cam 283. Each ball 286 is held between the pilot cam 281 and the main cam 283 in a state of being fitted into the cam groove 282 of the pilot cam 281 and the cam groove 284 of the main cam 283.

  As described above, the main cam 283 cannot rotate with respect to the unit case 310, whereas the ring gear 262 integrated with the pilot cam 281 can rotate with respect to the unit case 310. Therefore, in the cam mechanism 280, when the output of the motor 251 is input to the speed reducer 260 and the torque of the sun gear 261 acts on the ring gear 262 via the carrier 263, the first embodiment shown in FIG. The operation is the same as the operation of the cam mechanism 80.

  That is, at this time, circumferential power acting on the pilot cam 281 integrated with the ring gear 262 is converted into axial power via the ball 286 and transmitted to the main cam 283. Thus, the main cam 283 moves slightly in the axial direction so as to move away from the pilot cam 281, and the pressing member 276 of the clutch 270 is pressed toward the vehicle front side by the main cam 283, whereby the vehicle front side of the pressing member 276 is A plurality of friction plates 273 arranged in the axial direction are fastened.

  As described above, the clutch 270 is fastened via the cam mechanism 280 when the motor 251 is driven, and is released because the cam mechanism 280 does not operate when the motor 251 is not driven. Therefore, when the motor 251 is driven, the first rear shaft 222a and the second rear shaft 222b are fastened by fastening the clutch 270, whereby the front wheels 215, 216 and the rear wheels 235, 236 are connected to each other. The four-wheel drive state is established. At this time, in addition to the power of the engine 202, the power of the motor 251 is transmitted to the front wheels 215, 216 and the rear wheels 235, 236, respectively, and torque assist by the motor 251 is performed.

  However, when the motor 251 is driven with the minimum output necessary for engaging the clutch 270, a four-wheel drive state using only the power of the engine 202 is realized.

  On the other hand, when the motor 251 is not driven, the first rear shaft 222a and the second rear shaft 222b are separated by the clutch 270 being in a disengaged state, and a front wheel traveling state is achieved by the power of the engine 202.

  According to the above configuration, the clutch 270 is connected to the speed reducer 260 via the cam mechanism 280 having the simple configuration as described above, so that the axial force of the cam mechanism 280 is driven when the motor 251 is driven. When the motor 251 is stopped mechanically, the cam mechanism 280 is not actuated so that the motor 251 is mechanically released. Therefore, it is not necessary to provide a dedicated actuator such as an electromagnetic clutch mechanism or to control the operation of the actuator in order to fasten or release the clutch 270.

  The cam mechanism 280 includes a ring-shaped pilot cam 281 provided integrally with the ring gear 262 of the speed reducer 260, a disk-shaped main cam 283 disposed opposite to the pilot cam 281, and the pilot cam 281 and the main cam 283. It has a simple and compact structure consisting of balls 286 interposed therebetween.

  Thus, in this embodiment, the conventional hybrid vehicle has a large and complicated structure that is provided for the operation of the clutch for performing the switching function between the two-wheel drive and the four-wheel drive. Since the clutch 270 is operated using a simple and compact cam mechanism 280 instead of the actuator, the number of parts is reduced, the structure and control are simplified, and the entire drive device 201 is made compact. Can do.

  While the present invention has been described with reference to the above-described embodiments, the present invention is not limited to the above-described embodiments.

  For example, in the first embodiment described above, an example in which a reduction gear is configured with two planetary gear mechanisms, and in the second embodiment, an example in which a reduction gear is configured with one planetary gear mechanism has been described. One or three or more planetary gear mechanisms may constitute a reduction gear, or in the second embodiment, two or more planetary gear mechanisms may constitute a reduction gear.

  In the above-described embodiment, an example in which the reaction force element of the reduction gear is a ring gear has been described. However, in the present invention, the reaction force element of the reduction gear may be a sun gear or a carrier.

  Furthermore, in the above-described embodiment, an example in which the cam mechanism is a ball cam mechanism has been described. However, in the present invention, any mechanism may be used as the cam mechanism as long as it converts rotational power in the axial direction. Can do.

  As described above, according to the present invention, in a vehicle drive device having a motor connected to drive wheels via a clutch means, the dedicated actuator for operating the clutch means is eliminated, thereby reducing the number of parts. Since reduction, simplification of structure and control, and downsizing of the drive device can be achieved, there is a possibility that this type of drive device and a vehicle equipped with this type of drive device may be suitably used.

DESCRIPTION OF SYMBOLS 1 Drive device 2 Engine 3 Transaxle 4 Transaxle case 5 Torque converter 6 Transmission 10 Differential device 12 Differential case 30, 40 Drive shaft (drive shaft)
31, 41 Differential side shaft member 32, 42 Intermediate shaft member 33, 43 Drive wheel side shaft member 50 Motor unit 51 Motor 52 Stator 53 Rotor 54 Output shaft 60 Reducer 60a First planetary gear mechanism 60b Second planetary gear mechanism 61a First sun gear 61b Second sun gear 62 Ring gear member 62a First ring gear 62b Second ring gear 63a First carrier 63b Second carrier 66 Friction member 70 Clutch 71 Hub 72 Drum 73 Friction plate 76 Press member 78 Thrust bearing 80 Cam mechanism 81 Pilot cam 83 Main cam 86 Ball 201 Drive device 202 Engine 205 Torque converter 206 Transmission 210 Differential device for front wheel 212 Transfer device 220 Propeller shaft (drive shaft)
221 Front shaft 222 Rear shaft 222a First rear shaft 222b Second rear shaft 230 Rear wheel differential device 250 Motor unit 251 Motor 252 Stator 253 Rotor 254 Output shaft 260 Reducer 261 Sun gear 262 Ring gear 263 Carrier 270 Clutch 271 Hub 272 Drum 273 Friction plate 276 Pressing member 278 Thrust bearing 280 Cam mechanism 281 Pilot cam 283 Main cam 286 Ball

Claims (3)

A planetary gear mechanism having an input element, an output element and a reaction force element;
A motor coupled to the input element;
Clutch means for connecting and disconnecting between the output element and the drive wheel;
A cam mechanism coupled to the reaction force element and generating an axial force by a torque acting on the reaction force element when the output of the motor is input to the input element, and fastening the clutch means. A vehicle drive device characterized by that.   The vehicle drive device according to claim 1, further comprising a drive source connected to the drive wheel, separately from the motor. A drive source different from the motor;
A power transmission device that transmits the output of the drive source to one of the front wheels or the rear wheels;
A drive shaft for transmitting power from the power transmission device to the other of the front wheels or the rear wheels,
The vehicle drive device according to claim 1, wherein the clutch means is provided on the drive shaft.

Images