JP6043884B2 - Drive device - Google Patents

Description

  The present invention relates to a drive device applied to a vehicle.

  Conventionally, as a drive device, an engine mounted on a vehicle as a drive source, a first motor generator and a second motor generator mounted on the vehicle as a drive source, and an output of the engine as a first motor generator and an output member A power distribution mechanism that distributes power on the first axis, an intermediate shaft is disposed on a second axis parallel to the first axis, and outputs of the output member and the second motor generator are output from the intermediate shaft to the first axis and the first axis. One that transmits to a differential gear device arranged on a third axis parallel to the two axes is known (see, for example, Patent Document 1).

  In this drive device, a first power transmission device that transmits power between the output member and the intermediate shaft is provided, and a first output that transmits power from the first power transmission device to the drive wheel side via the intermediate shaft. A second power transmission device that transmits power between the system path, the second motor generator, and the intermediate shaft is provided, and the second power transmission device transmits power to the differential gear device side through the intermediate shaft. 2 output paths.

  The first output system path and the second output system path are set with different gear ratios, and energy loss during high-speed cruise is reduced without impairing the climbing performance.

JP 2001-97058 A

  By the way, in the drive device as described above, the first axis that is the axis of the engine shaft and the motor shaft, the second axis that is the center of the intermediate shaft as the clutch shaft, and the differential gear device as the differential shaft. The third axis, which is the axis, was widely arranged in the front-rear direction of the vehicle. For this reason, large mechanisms, such as an engine, a motor generator, and a power transmission mechanism, are widely arranged in the front-rear direction of the vehicle, and the apparatus is increased in size.

  Therefore, an object of the present invention is to provide a drive device that can be miniaturized.

The present invention is a drive device that is driven by an engine and an electric motor, the casing having the engine attached to one side and the electric motor attached to the other side, and the engine housed in the casing and connected to the engine A shaft, a motor shaft housed in the casing and connected to the electric motor and arranged in parallel with the engine shaft, and a driving force is transmitted from the engine shaft via a gear set; and the engine shaft housed in the casing A clutch shaft having an intermeshing portion for interrupting a driving force transmitted from the motor shaft parallel to the engine shaft and spaced from the motor shaft; and a driving force housed in the casing and transmitted from the clutch shaft. A differential shaft distributed in a ring and arranged in parallel with the clutch shaft, and the other side surface side of the casing on the clutch shaft. And an operation section for intermittently operating the intermittent part along with the disposed part comprises an oil pump and a hydraulic circuit, wherein the electric motor and the operating unit, characterized in that it is spaced.

  According to the present invention, it is possible to provide a drive device that can be miniaturized.

(A) is a top view of a vehicle equipped with a drive device according to an embodiment of the present invention. (B) is a side view of a vehicle equipped with a drive device according to an embodiment of the present invention. It is the schematic of the drive device which concerns on embodiment of this invention. It is sectional drawing of the drive device which concerns on embodiment of this invention. It is a side view of the drive device concerning an embodiment of the invention. It is a side view which shows the other example of arrangement | positioning of the park lock mechanism of the drive device which concerns on embodiment of this invention. It is a side view which shows the other example of arrangement | positioning of the motor shaft of the drive device which concerns on embodiment of this invention. It is a side view which shows the other example of arrangement | positioning of the motor shaft of the drive device which concerns on embodiment of this invention. It is a side view which shows the other example of arrangement | positioning of the motor shaft and park lock mechanism of the drive device which concerns on embodiment of this invention.

  First, the outline of the driving apparatus according to the embodiment of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 and 2, the drive device 1 is mounted on the front side in the longitudinal direction of the vehicle and drives the front wheel side. The drive device 1 driven by an engine 3 as a drive source and a motor generator 5 that performs regeneration as a drive source or electric power energy mainly includes an engine shaft 7, a motor shaft 9, a power transmission unit 11, a clutch mechanism. 75 and a differential mechanism 17.

  As shown in FIG. 3, the driving force from the engine 3 (see FIG. 2) is transmitted to an unillustrated intermittent portion such as a dry single-plate clutch, and is transmitted to the engine shaft 7 when the intermittent portion is in a connected state. Is done. The driving force from the motor generator 5 (see FIG. 2) is transmitted to the motor shaft 9 and is transmitted to the engine shaft 7 via the transmission gear set 41. The engine shaft 7 to which driving force is input from the engine 3 and the motor generator 5 has an input gear 85 of the first power transmission unit 77 and a second power transmission unit 79 of the power transmission unit 11 having different speed ratios. An input gear 93 is disposed.

  The driving force transmitted to the first power transmission unit 77 composed of the input gear 85 and the output gear 87 is transmitted to the first intermittent part 81, and when the first intermittent part 81 is in the connected state, the clutch shaft 15 is transmitted. The driving force transmitted to the second power transmission unit 79 composed of the input gear 93 and the output gear 95 is transmitted to the second intermittent part 83, and when the second intermittent part 83 is in the connected state, the clutch shaft 15 is transmitted. The power transmission unit 11, the first intermittent part 81, and the second intermittent part 83 constitute a clutch mechanism 75.

  By selectively connecting the first intermittence part 81 and the second intermittence part 83 in the clutch mechanism 75, appropriate use rotations of the engine 3 and the motor generator 5 as drive sources in accordance with the running state of the vehicle. The (driving force) can be appropriately shifted and transmitted to the clutch shaft 15.

  The driving force transmitted to the clutch shaft 15 is transmitted to the differential mechanism 17 via the output unit 13 including the pinion 143 and the ring gear 145. The driving force transmitted to the differential mechanism 17 is distributed to the left and right wheels via shafts 67 and 69 (see FIG. 2) connected to the pair of side gears 55 and 57, respectively. The rotational axis of the differential mechanism 17 is a differential shaft 19.

  In such a vehicle, in the EV mode in which the vehicle is driven only by the motor function of the motor generator 5, the intermittent portion (not shown) is disconnected, and the first intermittent portion 81 or the second intermittent portion 83 is connected. The driving force by the motor function 5 is output from the output unit 13 to the differential mechanism 17 via the power transmission unit 11. The regeneration of electric power by the motor generator 5 in this mode is performed by causing the motor generator 5 to function as a generator with respect to the brake energy of the vehicle such as when the vehicle is decelerated.

  In the parallel mode in which the vehicle is driven by only the engine 3, the motor function of the motor generator 5, or the motor function of the engine 3 and the motor generator 5, an unillustrated intermittent part is connected or released, and the first intermittent part 81 The first power transmission unit 77 or the second power that is selectively connected to the second intermittence unit 83 and the driving force by the motor function of the engine 3 and the motor generator 5 is selected according to the traveling state of the vehicle. The data is output from the output unit 13 to the differential mechanism 17 via the transmission unit 79.

  In the power generation mode in which the battery is charged by the generator function of the motor generator 5, when the vehicle is stopped or when only the engine 3 is running, an intermittent portion (not shown) is connected, and the first intermittent portion 81 and the second intermittent portion 83 are connected. Disconnect (connect any one of the interrupted parts when the engine 3 is running), drive the motor shaft 9 from the engine shaft 7 through the transmission gear set 41, and drive the generator function of the motor generator 5 with the engine 3. Then, it is stored in a battery (not shown). When the vehicle stops, the park lock gear 149 provided on the clutch shaft 15 is locked by the park lock mechanism 21 (see FIG. 4), and the rotation of the clutch shaft 15 is prevented.

  As described above, the vehicle selects the driving source of the engine 3 and the motor generator 5 according to the traveling state, and selectively selects the intermittent portion (not shown) or the intermittent portion of the first intermittent portion 81 and the second intermittent portion 83. By doing so, the first power transmission unit 77 and the second power transmission unit 79 in the power transmission unit 11 are driven by the driving force appropriately shifted.

  Hereinafter, the drive device according to the embodiment of the present invention mounted on such a vehicle will be described with reference to FIGS. 4 to 8, the front-rear direction of the vehicle is the front and rear directions described on the paper, and the vertical direction of the vehicle corresponds to the upper and lower directions described on the paper.

  A drive device 1 according to the present embodiment includes an engine 3 mounted on a vehicle and serving as a drive source, a motor generator 5 mounted on the vehicle and serving as a drive source, an engine shaft 7 that transmits power of the engine 3, and the engine A motor shaft 9 for transmitting the power of the motor generator 5 to the shaft 7, a power transmission unit 11 for transmitting the power transmitted from the engine shaft 7 at different speed ratios, and outputting the power transmitted to the power transmission unit 11 A clutch shaft 15 having an output unit 13 and a differential shaft 19 for transmitting power output from the output unit 13 of the clutch shaft 15 to the differential mechanism 17 are provided.

  The clutch shaft 15 is disposed between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle.

  The motor shaft 9 is disposed between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle.

  Further, the clutch shaft 15 is disposed below the motor shaft 9 in the vertical direction of the vehicle.

  The motor shaft 9 is disposed at a height equal to or higher than the engine shaft 7 in the vertical direction of the vehicle.

  Further, a park lock mechanism 21 that prevents rotation of the clutch shaft 15 is disposed in front of the clutch shaft 15 in the front-rear direction of the vehicle.

  As shown in FIG. 3, in the drive device 1, an engine shaft 7, a motor shaft 9, a clutch shaft 15, and a differential shaft 19 that is a rotation axis of the differential mechanism 17 are arranged in parallel.

  The engine shaft 7 is rotatably supported on the casing 27 via a pair of bearings 23 and 25 on both sides in the axial direction. Further, a coupling portion 29 is formed on the outer periphery of the end portion of the engine shaft 7, and a clutch member constituting an intermittent portion (not shown) is coupled so as to be integrally rotatable. Further, between the radial direction of the engine shaft 7 and the casing 27, a seal member 31 that partitions the inside and the outside of the casing 27 is disposed.

  A driving force from the engine 3 (see FIG. 2) is input to the engine shaft 7 through an intermittent portion (not shown), and a motor generator 5 (see FIG. 2) is connected through the transmission gear set 41 and the motor shaft 9. The driving force by the motor function (see) is input. When the motor generator 5 functions as a generator, the driving force input to the engine shaft 7 is output to the motor generator 5 via the transmission gear set 41 and the motor shaft 9.

  The motor shaft 9 is formed in a hollow shape and is rotatably supported on the casing 27 via a pair of bearings 33 and 35 on both sides in the axial direction. Further, a connecting portion 37 is formed on the inner periphery of the end portion of the motor shaft 9, and the output shaft of the motor generator 5 is connected so as to be integrally rotatable. In addition, a small-diameter gear portion 39 that meshes with the large-diameter input gear 85 of the first power transmission portion 77 formed so as to be able to rotate integrally with the engine shaft 7 is formed in the central portion of the motor shaft 9. The gear portion 39 and the input gear 85 are arranged in parallel to each other and constitute a transmission gear set 41. The transmission gear set 41 may be configured by meshing the gear portion 39 of the motor shaft 9 with the input gear 93 of the second power transmission portion 79. A seal member 43 that partitions the inside and the outside of the casing 27 is disposed between the motor shaft 9 and the casing 27 in the radial direction.

  When the motor generator 5 functions as a motor, the driving force from the motor generator 5 is input to the motor shaft 9 and is output to the engine shaft 7 via the transmission gear set 41. Further, when the motor generator 5 functions as a generator, the driving force from the engine shaft 7 input via the transmission gear set 41 is output to the motor generator 5. The driving force generated by the motor functions of the engine 3 and the motor generator 5 is output to the clutch shaft 15 via the engine shaft 7.

  The clutch shaft 15 is rotatably supported on the casing 27 via a pair of bearings 45 and 47 on both sides in the axial direction. A driving force is input to the clutch shaft 15 from the engine shaft 7 side via the first intermittent portion 81 and the second intermittent portion 83 and is output to the differential mechanism 17 via the output portion 13.

  The differential mechanism 17 includes a differential case 49, a pinion shaft 51, a pinion 53, and a pair of side gears 55 and 57. The differential case 49 is rotatably supported by the casing 27 via bearings 59 and 61 at boss portions formed on both sides in the axial direction. The differential case 49 is rotationally driven about the differential shaft 19 as a rotational axis by transmitting a driving force via the output unit 13. In such a differential case 49, a pinion shaft 51, a pinion 53, and a pair of side gears 55 and 57 are accommodated.

  The pinion shaft 51 is engaged with the differential case 49 at its end and is prevented from coming off by a pin, and is rotated integrally with the differential case 49. A pinion 53 is supported on the pinion shaft 51.

  The pinion 53 is supported by the pinion shaft 51 and revolves as the differential case 49 rotates. The pinion 53 transmits a driving force to the pair of side gears 55 and 57, and is rotatably supported on the pinion shaft 51 so as to be driven to rotate when a differential rotation occurs between the pair of side gears 55 and 57 engaged with each other. ing.

  The pair of side gears 55 and 57 is supported by the differential case 49 so as to be relatively rotatable, and meshes with the pinion 53. The pair of side gears 55 and 57 are provided with spline-shaped connecting portions 63 and 65 on the inner peripheral side, and shafts 67 and 69 (see FIG. 2) connected to the left and right wheels can rotate integrally with the side gears 55 and 57. It is connected to. Further, between the radial directions of the shafts 67 and 69 and the casing 27, seal members 71 and 73 that partition the inside and the outside of the casing 27 are arranged. Thus, the pair of side gears 55 and 57 outputs the driving force input to the differential case 49 to the left and right wheels via the shafts 67 and 69.

  The engine shaft 7, the motor shaft 9, the clutch shaft 15, and the differential shaft 19 are arranged so as to be able to transmit power via the clutch mechanism 75. The clutch mechanism 75 includes a first power transmission unit 77 and a second power transmission unit 79 that constitute the power transmission unit 11, a first intermittent unit 81, a second intermittent unit 83, and the output unit 13. It has.

  The first power transmission unit 77 includes an input gear 85 and an output gear 87 that are arranged in parallel to each other. The input gear 85 is formed as one member continuous to the engine shaft 7 and is rotated integrally with the engine shaft 7. The input gear 85 has a larger diameter than the output gear 87 and meshes with the output gear 87. The output gear 87 is disposed on the clutch shaft 15 so as to be rotatable relative to the clutch shaft 15 via needle bearings 89 and 91.

  The first power transmission unit 77 transmits the power transmitted from the unillustrated intermittent part via the engine shaft 7 to the first intermittent part 81 at the first speed ratio. Specifically, when the intermittent portion (not shown) is in the connected state, the driving force from the engine 3 is transmitted to the first intermittent portion 81 at the first speed ratio. When the intermittent portion (not shown) is in the disconnected state, the driving force by the motor function of the motor generator 5 is transmitted from the motor shaft 9 to the engine shaft 7 via the transmission gear set 41, and the first speed ratio is the first speed ratio. It transmits to the intermittent part 81. A second power transmission unit 79 is disposed adjacent to the first power transmission unit 77 in the axial direction.

  The second power transmission unit 79 includes an input gear 93 and an output gear 95 arranged in parallel to each other. The input gear 93 is coupled to the engine shaft 7 via the coupling portion 97 so as to be rotatable together with the engine shaft 7. The input gear 93 has a larger diameter than the output gear 95 and a smaller diameter than the input gear 85, and meshes with the output gear 95. The output gear 95 has a larger diameter than the output gear 87 and is disposed on the outer periphery of the output gear 87 via a needle bearing 99 so as to be rotatable relative to the output gear 87 and the clutch shaft 15.

  The second power transmission unit 79 transmits power transmitted from an unillustrated intermittent part via the engine shaft 7 to the second intermittent part 83 at a second speed ratio. Specifically, when the intermittent portion (not shown) is in the connected state, the driving force from the engine 3 is transmitted to the second intermittent portion 83 at the second speed ratio. When the unillustrated intermittent portion is in the disconnected state, the driving force by the motor function of the motor generator 5 is transmitted from the motor shaft 9 to the engine shaft 7 via the transmission gear set 41, and the second speed ratio is the second speed ratio. It transmits to the intermittent part 83.

  The driving force transmitted from the power transmission unit 11 is transmitted to the first interrupting unit 81 and the second interrupting unit 83 at the first speed ratio and the second speed ratio, respectively. It is transmitted to the clutch shaft 15 by the connection of the intermittent portion 81 and the second intermittent portion 83.

  The first intermittent portion 81 is moved in the axial direction to the first clutch housing 103 coupled to the output gear 87 and the coupling portion 101 so as to be integrally rotatable, and to the inner periphery of the first clutch housing 103 and the outer periphery of the clutch shaft 15. It consists of a plurality of clutch plates that are connected so as to be rotatable together. When connected, the first interrupting portion 81 transmits the driving force shifted to the first speed ratio by the first power transmission portion 77 to the clutch shaft 15. A second intermittent portion 83 is disposed on the outer diameter side of the first intermittent portion 81 so as to overlap in the radial direction.

  The second intermittent portion 83 includes a second clutch hub 105 fixed to the output gear 95 and a bolt so as to be integrally rotatable, and a second clutch housing 107 fixed to the clutch shaft 15 by a fixing means such as welding. And a plurality of clutch plates connected to the outer periphery of the second clutch hub 105 and the inner periphery of the second clutch housing 107 so as to be axially movable and integrally rotatable. When connected, the second interrupting portion 83 transmits the driving force shifted to the second speed ratio by the second power transmission portion 79 to the clutch shaft 15.

  The first intermittent portion 81 and the second intermittent portion 83 are intermittently operated by the operation portion 109 disposed at the end of the clutch shaft 15.

  The operation unit 109 is provided coaxially with the pinion 143 and includes a hydraulic mechanism 111, a first pressing member 113, and a second pressing member 115, and the hydraulic mechanism 111 and the oil pump 119 are coaxial with the clutch shaft 15. Connected arrangement. A hydraulic mechanism 111 serving as a control mechanism that controls the operation of the operation unit 109 is disposed in a valve body 117 that is divided into two interior types and disposed inside the casing 27, and is driven by a small electric motor (not shown). An oil pump 119 and a hydraulic circuit 121 provided in the valve body 117 are provided.

  The oil pump 119 is a gear pump in which two pump gears are combined. The oil pump 119 is disposed on the end side of the clutch shaft 15 in the valve body 117. The oil pump 119 sucks oil stored in an oil reservoir in the casing 27 through an oil strainer that filters foreign matters, applies oil pressure to the oil, and causes the oil pressure circuit 121 to circulate.

  The hydraulic circuit 121 is provided in the valve body 117, is formed by a plurality of oil passages, etc., and a specified hydraulic pressure is stored in the hydraulic chamber 123 by an oil pump 119 driven by a small electric motor (not shown). Oil whose hydraulic pressure is controlled by the solenoid valve is supplied from the radial holes 125 and 127 to the first hydraulic cylinder 137 and the second hydraulic cylinder 139 through the axial holes 129 and 131 and the radial holes 133 and 135, and The first pressing member 113 and the second pressing member 115 are moved.

  The first pressing member 113 and the second pressing member 115 are disposed on the clutch shaft 15 so as to be axially movable relative to each other. The first pressing member 113 has an axial position fixed by a fixing means such as a snap ring, and is disposed to face the plurality of clutch plates of the first intermittent portion 81 in the axial direction. The second pressing member 115 is fixed in the axial direction by the second clutch housing 107 and is disposed opposite to the plurality of clutch plates of the second intermittent portion 83 in the axial direction. The first pressing member 113 and the second pressing member 115 are each provided with a return spring 141 that urges the first and second intermittent portions 81 and 83 in the connection release direction.

  The first pressing member 113 is axially moved in the connecting direction of the first intermittent portion 81 when oil whose hydraulic pressure is controlled is supplied from the hydraulic mechanism 111 to the first hydraulic cylinder 137. By the axial movement of the first pressing member 113, the first intermittent portion 81 is pressed and connected. Due to the connection of the first interrupting portion 81, the driving force shifted to the first speed ratio from the engine shaft 7 via the first power transmission portion 77 is transmitted to the clutch shaft 15.

  The second pressing member 115 is axially moved in the connecting direction of the second intermittent portion 83 when oil whose hydraulic pressure is controlled is supplied from the hydraulic mechanism 111 to the second hydraulic cylinder 139. By the movement of the second pressing member 115 in the axial direction, the second intermittent portion 83 is pressed and connected. Due to the connection of the second intermittent portion 83, the driving force shifted from the engine shaft 7 to the second speed ratio via the second power transmission portion 79 is transmitted to the clutch shaft 15.

  Thus, the driving force transmitted to the clutch shaft 15 via the first intermittent portion 81 and the second intermittent portion 83 is output from the output portion 13 to the differential mechanism 17 side having the differential shaft 19 as the rotational axis. Is done. Although the first hydraulic cylinder 137 and the second hydraulic cylinder 139 are arranged coaxially with the clutch shaft 15, the first hydraulic cylinder 137 and the second hydraulic cylinder 139 are formed on the casing 27 side, and the rod and bearing The intermittent control of the first intermittent part 81 and the second intermittent part 83 can also be performed via relative rotation absorbing means such as.

  The output unit 13 includes a pinion 143 and a ring gear 145 that are arranged in parallel to each other. The pinion 143 is coupled to the end of the clutch shaft 15 on the opposite side of the clutch shaft 15 where the operation unit 109 is disposed, via the coupling portion 147 so as to be integrally rotatable. The pinion 143 is disposed adjacent to the output gear 87 of the first power transmission unit 77 in the axial direction. The pinion 143 has a smaller diameter than the ring gear 145, meshes with the ring gear 145, and forms a reduction gear mechanism as an output system path to the wheel side.

  The ring gear 145 is fixed to the differential case 49 of the differential mechanism 17 and fixing means such as a bolt so as to be integrally rotatable. The ring gear 145 uses the differential shaft 19, which is the rotational axis of the differential mechanism 17, as the rotational axis, and transmits the driving force transmitted to the clutch shaft 15 to the differential mechanism 17 via the pinion 143.

  The output unit 13 outputs the driving force transmitted to the clutch shaft 15 to the differential mechanism 17. The driving force transmitted to the differential mechanism 17 is output to the left and right wheels through shafts 67 and 69 (see FIG. 2) connected to the pair of side gears 55 and 57. A parking lock gear 149 is provided on the pinion 143 of the output unit 13 so as to be integrally rotatable. The parking lock gear 149 is locked by the parking lock mechanism 21 when the vehicle is stopped, and the clutch shaft 15 rotates. To prevent.

  As shown in FIGS. 4 and 5, the park lock mechanism 21 includes an actuator 151, a rotating member 153, a biasing member 155, a moving member 157, an operation member 159, and a lock member 161. . The actuator 151 includes an electric motor, is fixed to a stationary member such as a body frame, and is operated when a user such as a driver switches the shift range. The actuator 151 rotates the rotating shaft 163 by the operation to rotate the rotating member 153.

  The rotation member 153 is made of a thin plate, and the rotation shaft 163 of the actuator 151 is inserted into the rotation center so as to be integrally rotatable. The rotation of the actuator 151 rotates about the axis of the rotation shaft 163. The rotating member 153 releases the lock position where the lock member 161 prevents the rotation of the clutch shaft 15 by the forward and reverse rotation of the rotation shaft 163, that is, the actuator 151, and the prevention of the rotation of the clutch shaft 15 by the lock member 161. It is rotated between the unlocked position. The rotation of the rotation member 153 at this time is regulated by contacting the regulating members 165 and 167. The rotating member 153 is applied with an urging force stepwise by the urging member 155.

  The biasing member 155 includes a leaf spring, is fixed to the stationary system member with a bolt, and has one end engaged with the rotating member 153. One end of the urging member 155 is a roller and constitutes two concave portions formed in the rotating member 153 and an engaging portion 169. The engaging portion 169 is engaged with any one of the two concave portions formed in the rotating member 153 by the rotation of the rotating member 153.

  Specifically, the engaging portion 169 is engaged with one of the recesses when the rotating member 153 is positioned at the locked position, and is engaged with the other recess when the rotating member 153 is positioned at the unlocking position. The At this time, the urging member 155 applies an urging force to the rotating member 153 in two stages of the lock position or the lock release position. A moving member 157 is engaged with such a rotating member 153.

  The moving member 157 is formed of a long rod, and one end side is engaged with the rotating member 153 via the connecting portion 171 and is moved in the axial direction by the rotation of the rotating member 153. An operation member 159 is inserted through the other end side of the moving member 157.

  The operation member 159 is positioned at an axial position of the operation member 159 relative to the moving member 157 by a fixing means such as welding. The operation member 159 is formed with a cam surface that contacts the lock member 161 and operates the lock member 161. The operating member 159 is in contact with a waiting spring 173 that is inserted into the moving member 157 and serves as a waiting mechanism for the locking member 161 when the locking member 161 prevents the clutch shaft 15 from rotating.

  The operation member 159 is disposed so as to be axially movable in a sleeve 175 fixed to the stationary system member with a bolt, and the cam surface is brought into contact with the lock member 161 by the axial movement through an opening provided in the sleeve 175. The lock member 161 is operated by contacting or releasing the contact.

  The lock member 161 is assembled to a stationary member so as to be rotatable by a shaft support portion 177, and includes a contact portion 179 and a lock portion 181. The contact portion 179 is provided on one end side of the lock member 161, and is disposed inside the sleeve 175 when the lock member 161 is unlocked. The cam surface of the operation member 159 contacts the lock member 161 at the lock position. Thus, the lock member 161 is rotated in a direction that prevents the clutch shaft 15 from rotating. The lock portion 181 is provided on the other end side of the lock member 161, and a park lock provided so as to rotate integrally with the clutch shaft 15 when the lock member 161 is rotated in a direction to prevent the clutch shaft 15 from rotating. Engage with the gear 149 to prevent the clutch shaft 15 from rotating.

  The shaft support 177 that supports the lock member 161 is provided with a return spring 183 that is a winding spring. One end is engaged with the stationary member and the other end is in contact with the lock member 161. The return spring 183 biases the lock member 161 in the direction in which the lock portion 181 and the park lock gear 149 are disengaged to define the initial position of the lock member 161.

  In such a park lock mechanism 21, when the rotation member 153 is rotated to the lock position by the operation of the actuator 151, the moving member 157 is moved to the lock member 161 side, and the operation member 159 is the contact portion of the lock member 161. 179 abuts. At this time, the cam surface of the operation member 159 presses the contact portion 179 of the lock member 161 against the urging force of the return spring 183. As a result, the lock portion 181 of the lock member 161 is rotated about the shaft support portion 177 and meshed with the park lock gear 149, thereby preventing the clutch shaft 15 from rotating. When the lock portion 181 is located on the tooth surface of the park lock gear 149 and is not engaged with the park lock gear 149, the lock portion 181 is directed toward the tooth bottom of the park lock gear 149 by the wait spring 173 as a wait mechanism. The lock portion 181 is engaged with the park lock gear 149 when the lock portion 181 is positioned at the mesh position with the park lock gear 149.

  When the rotation member 153 is rotated to the unlocked position by the operation of the actuator 151 from the locked state of the lock member 161, the moving member 157 is moved to the rotation member 153 side, and the contact between the operation member 159 and the lock member 161 is performed. The contact with the part 179 is released. At this time, the contact portion 179 of the lock member 161 is accommodated in the sleeve 175 by the biasing force of the return spring 183. As a result, the lock portion 181 of the lock member 161 is rotated with the shaft support portion 177 as a fulcrum, and the meshing with the park lock gear 149 is released, and the prevention of the rotation of the clutch shaft 15 is released.

  The engine shaft 7, the motor shaft 9, the clutch shaft 15, and the differential shaft 19 in the driving apparatus 1 are positioned so that their arrangements are made compact. Specifically, the clutch shaft 15 is disposed between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle. The motor shaft 9 is disposed between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle. With this arrangement, the clutch mechanism 75 having the power transmission unit 11, the first intermittent part 81 and the second intermittent part 83, the output part 13, and the like, and the motor flange 185 indicating the outer diameter of the motor generator 5 are connected to the engine 3. The engine flange 187 indicating the outer diameter is not disposed on the front side of the vehicle. For this reason, the arrangement space which arrange | positions the parking lock mechanism 21 in the front side of a vehicle can be ensured, arrangement | positioning of the parking lock mechanism 21 as shown in FIG. 4, arrangement | positioning of the parking lock mechanism 21 as shown in FIG. The degree of freedom of the layout of the park lock mechanism 21 can be improved.

  The clutch shaft 15 is disposed below the motor shaft 9 in the vertical direction of the vehicle. With this arrangement, the motor generator 5 is arranged above the clutch mechanism 75 in the vertical direction of the vehicle, and the minimum ground height in the vertical direction of the vehicle of the motor generator 5 can be ensured.

  The motor shaft 9 is disposed at a height equal to or higher than the engine shaft 7 in the vertical direction of the vehicle. In this arrangement, the motor shaft 9 is not arranged between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle. For example, the motor shaft 9 is arranged as shown in FIGS. Also good. If the motor shaft 9 as shown in FIG. 6 is positioned above the engine shaft 7, a space on the front side of the vehicle can be secured, and the motor shaft 9 as shown in FIG. If it is arrangement | positioning located in, the space above a vehicle can be ensured. Further, as shown in FIG. 8, by changing the arrangement of the park lock mechanism 21, interference with other mechanisms can be prevented. With such an arrangement, it is possible to secure the space above and above the vehicle while securing the minimum ground height in the vertical direction of the vehicle of the motor generator 5 and to improve the degree of freedom of the layout of the peripheral members. it can.

  In such a drive device 1, the clutch shaft 15 is disposed between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle, so that the power transmission unit 11 and the output unit 13 are connected to the engine 3 and the differential mechanism. 17 between the two.

  Therefore, in such a drive device 1, a large mechanism is disposed in a compact manner in the front-rear direction of the vehicle, and the size can be reduced. In addition, since it is mounted compactly in the front-rear direction of the vehicle, the degree of freedom in designing the arrangement of the peripheral members can be improved.

  In addition, since the motor shaft 9 is disposed between the engine shaft 7 and the differential shaft 19 in the longitudinal direction of the vehicle, a space can be secured on the front side of the vehicle, and the degree of freedom in designing the layout of the peripheral members is increased. Can be improved.

  Furthermore, since the clutch shaft 15 is disposed below the motor shaft 9 in the vertical direction of the vehicle, the motor generator 5 is disposed above the power transmission unit 11 and the output unit 13 in the vertical direction of the vehicle. Thus, the minimum ground height in the vertical direction of the vehicle of the motor generator 5 can be ensured.

  Further, since the motor shaft 9 is disposed at a height equal to or higher than the height of the engine shaft 7 in the vertical direction of the vehicle, the space above the vehicle is secured while ensuring the minimum ground height of the motor generator 5 in the vertical direction of the vehicle. Therefore, the degree of freedom in designing the arrangement of the peripheral members can be improved.

  Further, since the park lock mechanism 21 for preventing the rotation of the clutch shaft 15 is disposed on the front side of the clutch shaft 15 in the front-rear direction of the vehicle, the park lock mechanism 21 is disposed on the front side of the vehicle where a space is secured. Therefore, the degree of freedom in the layout design of the park lock mechanism 21 can be improved.

  In the driving device according to the embodiment of the present invention, the driving device is applied to the front side of the vehicle. However, the driving device is not limited to this, and the driving device may be applied to the rear side of the vehicle. Also in this case, the rear side of the vehicle is made compact, and the degree of freedom in designing the arrangement of the peripheral members can be improved.

  The drive device according to the embodiment of the present invention may be applied to a rear wheel drive vehicle (MR vehicle) mounted between the front and rear axles, a rear wheel drive vehicle (RR vehicle) mounted rearward of the rear axle, and the like.

  Furthermore, the drive device according to the embodiment of the present invention can be made compact in the same manner as described above even when mounted in a vehicle with the front-rear direction reversed.

DESCRIPTION OF SYMBOLS 1 ... Drive device 3 ... Engine 5 ... Motor generator 7 ... Engine shaft 9 ... Motor shaft 11 ... Power transmission part 13 ... Output part 15 ... Clutch shaft 17 ... Differential mechanism 19 ... Differential shaft 21 ... Park lock mechanism

Claims (3)

A driving device driven by an engine and an electric motor,
A casing having the engine attached to one side and the electric motor attached to the other side;
An engine shaft housed in the casing and connected to the engine;
A motor shaft that is accommodated in the casing and connected to the electric motor and arranged in parallel with the engine shaft, and a driving force is transmitted from the engine shaft via a gear set;
A clutch shaft disposed in the casing and having an interrupting portion for interrupting a driving force transmitted from the engine shaft, and arranged in parallel with the engine shaft and spaced apart from the motor shaft ;
A differential shaft disposed in parallel to the clutch shaft that distributes the driving force received in the casing and transmitted from the clutch shaft to left and right wheels;
An operation portion that is disposed at an end portion of the casing on the other side surface of the clutch shaft and includes an oil pump and a hydraulic circuit and intermittently operates the intermittent portion;
The drive device, wherein the electric motor and the operation unit are spaced apart from each other. The drive device according to claim 1,
The operating device is disposed below the differential shaft in the vertical direction of the vehicle . The drive device according to claim 1 or 2,
The operating device is disposed between the engine shaft and the differential shaft in the front-rear direction of the vehicle .

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