JP2012162222A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device that facilitates balance adjustment of a rotor of a motor/generator while having a small physical constitution.SOLUTION: A rotor shaft 33 has: a shaft 331 formed at the end of the engine 11 side; a first cylindrical part 332 whose outer wall is fitted to an inner wall of a rotor 32; a second cylindrical part 333 forming a cylindrical space 34 in-between the outer wall of the shaft 331; and an annular part 334 connecting the inner wall of the first cylindrical part 332 and the outer wall of the second cylindrical part 333 to each other. A storage space 35 is formed on the engine 11 side of the annular part 334 between the first cylindrical part 332 and the second cylindrical part 333. At least a part of a clutch 50 is stored in the storage space 35. A housing 20 has a housing cylindrical part 222 cylindrically extending toward the engine 11 side in the space 34. A bearing 23 is provided between the outer wall of the housing cylindrical part 222 and the inner wall of the second cylindrical part 333 in order to bear the rotor shaft 33.

Description

  The present invention relates to a power transmission device that transmits engine power to a transmission, and more particularly to a power transmission device that includes a motor generator and a clutch.

  2. Description of the Related Art Conventionally, there is known a power transmission device for a hybrid vehicle that includes a motor generator and a clutch and transmits engine power or motor generator power to a transmission by operating the clutch. In the power transmission device described in Patent Document 1, the axial size of the power transmission device is reduced by disposing a clutch in a housing space formed on the radially inner side of the rotor of the motor generator, and the power transmission device operates in the housing space. It is trying to cool and lubricate the clutch effectively by supplying oil.

  In the power transmission device of Patent Document 1, since the clutch is disposed on the radially inner side of the rotor, the rotor is configured such that one end portion in the axial direction is supported by a cantilever. Therefore, there is a possibility that problems such as an increase in man-hours for improving the balance adjustment accuracy of the rotor or an increase in inertia mass due to an increase in the diameter of the rotating member for securing shaft rigidity may occur. Further, in the power transmission device of Patent Document 1, since the member that fixes the stator of the motor generator and the member that supports and supports the rotor are formed separately, the gap management accuracy between the stator and the rotor may be reduced. is there.

JP 2010-6190 A

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a power transmission device that is small in size and easy to adjust the balance of a rotor of a motor generator.

  The invention according to claim 1 is a power transmission device for transmitting the driving force of the engine to the transmission, and includes a housing, a motor generator, and a clutch. The motor generator has a stator, a rotor, and a rotor shaft. The stator is formed in a cylindrical shape and is housed and fixed in the housing. A winding is wound around the stator. The rotor is formed in a cylindrical shape and is rotatably provided inside the stator. The rotor shaft is fitted to the inner wall of the rotor, is rotatably supported by the housing, and is connected to the input shaft of the transmission. The clutch is provided between the engine output shaft and the rotor shaft. The clutch can connect the output shaft of the engine and the rotor shaft. Thereby, the driving force output from the output shaft of the engine can be transmitted to the transmission via the rotor shaft.

  In the present invention, the rotor shaft has a cylindrical space between the shaft portion formed at the end on the engine side, the first tube portion provided so that the outer wall is fitted to the inner wall of the rotor, and the outer wall of the shaft portion. It has the 2nd cylinder part to form, and the annular part which connects the inner wall of the 1st cylinder part, and the outer wall of the 2nd cylinder part. Between the 1st cylinder part and the 2nd cylinder part, the cylindrical accommodation space is formed in the engine side of the annular part. At least a part of the clutch is housed in the housing space. The housing has a housing cylindrical portion that extends in a cylindrical shape toward the engine side through the space and into which a shaft portion is inserted. A bearing portion for bearing the rotor shaft is provided between the outer wall of the housing tube portion and the inner wall of the second tube portion. Thereby, it can be set as the structure which arrange | positions a bearing part near the center of the axial direction of a rotor. Therefore, the rotor can be supported by bearings in the vicinity of the center in the axial direction, and the balance of the rotor can be easily adjusted. As a result, man-hours for improving the balance adjustment accuracy of the rotor can be reduced, and there is no need to increase the diameter of the rotating member to ensure shaft rigidity.

  Further, in the present invention, a portion of the housing that fixes the stator and a portion that supports the rotor and the rotor shaft by bearing, that is, a housing cylinder portion are integrally formed. Thereby, the gap management accuracy between the stator and the rotor can be improved. Therefore, the efficiency of the motor can be increased.

  In the present invention, as described above, at least a part of the clutch is housed in the housing space. That is, the clutch and the rotor are arranged so as to partially overlap in the axial direction of the rotor. Thereby, the physique of a power transmission device can be made small.

  Furthermore, in the present invention, for example, when a part of the clutch such as the friction engagement element is accommodated in the accommodation space, the axial size of the power transmission device is not increased even if the friction engagement element is enlarged. Therefore, when the friction engagement element is constituted by a plurality of friction plates, for example, the amount of heat generated by the friction from each friction plate can be reduced by increasing the number of friction plates. Thereby, the abnormal heat generation of the clutch can be prevented without increasing the size of the power transmission device.

  In the invention according to claim 2, the bearing portion is provided so as to be positioned within the axial width of the rotor. Thereby, a rotor can be bearing-supported in the position comparatively near from the center of an axial direction. Therefore, balance adjustment of the rotor can be performed more easily.

  In the third aspect of the invention, the housing has an engine side end connected to the engine housing of the engine and a transmission side end connected to the transmission housing of the transmission. Thereby, the axial shift of the output shaft of the engine and the input shaft of the transmission can be suppressed.

The inventions described in claims 4 and 6 more specifically illustrate the configuration and operation of the clutch.
According to a fourth aspect of the invention, the clutch includes a drum having at least a part of the axial direction in the housing space and connected to the output shaft of the engine, the inner wall of the cylindrical part, and the second cylindrical part. The friction engagement element provided to connect to the outer wall, and the friction engagement element provided on the engine side of the friction engagement element between the cylinder portion and the second cylinder portion and pressed against the friction engagement element An annular pressing member that can be engaged is provided. A hydraulic space is formed on the side of the pressing member opposite to the friction engagement element. The rotor shaft is formed with a first oil passage extending in the axial direction of the rotor shaft and a second oil passage extending from the first oil passage outward in the radial direction of the rotor shaft and communicating with the hydraulic space. In this configuration, when the hydraulic oil is supplied to the hydraulic space via the first oil passage and the second oil passage, the pressing member is pressed against the friction engagement element, and the friction engagement element is engaged. The output shaft and the rotor shaft are connected.

  In the invention according to claim 6, the clutch includes a drum part having at least a part in the axial direction located in the housing space and connected to the output shaft of the engine, the inner wall of the cylinder part, and the second cylinder part. A frictional engagement element provided to connect to the outer wall, and a frictional engagement element provided on the transmission side of the frictional engagement element between the cylindrical portion and the second cylindrical portion and pressed against the frictional engagement element It has the annular pressing member which can be engaged. A hydraulic space is formed on the side of the pressing member opposite to the friction engagement element. The rotor shaft is formed with a first oil passage extending in the axial direction of the rotor shaft and a second oil passage extending from the first oil passage outward in the radial direction of the rotor shaft and communicating with the hydraulic space. In this configuration, as in the fourth aspect of the invention, when the hydraulic oil is supplied to the hydraulic space via the first oil passage and the second oil passage, the pressing member is pressed against the friction engagement element. The friction engagement element engages, and the engine output shaft and the rotor shaft are connected.

  As described above, in the inventions according to claims 4 and 6, the rotor shaft is formed with the first oil passage and the second oil passage through which the working oil supplied to the hydraulic space flows. Therefore, the hydraulic oil can be easily introduced into the first oil passage and the second oil passage from the transmission side. Thereby, it becomes easy to divert the hydraulic fluid supplied to the transmission for operating the transmission as the hydraulic fluid for the clutch. Therefore, it is not necessary to form a new hydraulic circuit for operating the clutch, and the cost can be reduced.

  In the invention according to claim 6, since the hydraulic space is formed on the side opposite to the friction engagement element of the pressing member, that is, on the transmission side of the friction engagement element, the second oil passage is connected to the friction engagement element. It can be formed closer to the transmission than the combined element. Thereby, the part inside a friction engagement element can be made hollow among rotor shafts. As a result, the inertia mass of the rotor shaft can be reduced.

  In a fifth aspect of the invention, the second oil passage is formed to extend radially outward of the rotor shaft from the first oil passage so as to be inclined toward the engine side with respect to the first oil passage. As a result, the angle between the first oil passage and the second oil passage formed by the engine-side wall surface forming the first oil passage of the rotor shaft and the engine-side wall surface forming the second oil passage is 180 degrees or more. Can be formed. Therefore, the pressure loss of the hydraulic oil flowing through the first oil passage and the second oil passage at the connection portion between the first oil passage and the second oil passage can be reduced. As a result, the responsiveness regarding the operation of the clutch can be improved.

In the seventh aspect of the invention, the second oil passage is formed to extend radially outward of the rotor shaft from the first oil passage so as to be inclined toward the transmission side with respect to the first oil passage. This configuration can be easily realized by forming the second oil passage from the engine side end face of the rotor shaft, for example, by cutting or the like. Thus, in the present invention, the workability of the second oil passage can be improved.
In addition, in the above, “tubular” means, for example, “hollow cylindrical shape”, and includes a substantially cylindrical shape (substantially cylindrical shape). Further, “annular” means, for example, “annular” and includes a substantially annular shape (substantially annular shape).

The schematic diagram which shows the state which installed the power transmission device by 1st Embodiment of this invention in the vehicle. Sectional drawing which shows the power transmission device by 1st Embodiment of this invention. (A) is a figure for demonstrating arrangement | positioning of the damper of the power transmission device by 1st Embodiment of this invention, The figure which looked at the flywheel, the damper, and the drum of the clutch from the transmission side of the axial direction, (B) is sectional drawing which shows the sealing member of the power transmission device by 1st Embodiment of this invention. Sectional drawing which shows the power transmission device by 2nd Embodiment of this invention. Sectional drawing which shows the power transmission device by 3rd Embodiment of this invention. Sectional drawing which shows the power transmission device by 4th Embodiment of this invention.

  Hereinafter, a power transmission device according to a plurality of embodiments of the present invention will be described with reference to the drawings. Note that, in a plurality of embodiments, substantially the same components are denoted by the same reference numerals, and description thereof is omitted.

(First embodiment)
A power transmission device according to a first embodiment of the present invention is shown in FIGS.
The power transmission device 1 is mounted on a hybrid vehicle using, for example, an engine and a motor as drive sources. In the present embodiment, the power transmission device 1 includes a motor (motor generator) as a drive source.

  As shown in FIG. 1, the power transmission device 1 is installed between a vehicle engine 11 and a transmission 12. The power transmission device 1 transmits the driving force output from the engine 11 as the first driving source to the transmission 12. The driving force transmitted to the transmission 12 is decelerated or increased by the transmission mechanism of the transmission 12 and transmitted to the axle 14 via the differential 13 as a differential device. Thereby, the wheel 15 rotates and the vehicle travels. In the present embodiment, the transmission 12 is a continuously variable transmission (CVT). The transmission mechanism of the transmission 12 is operated by hydraulic oil supplied from the pump 16.

  The power transmission device 1 includes a motor generator 30 as a second drive source. By transmitting the driving force of the motor generator 30 to the transmission 12, the vehicle can be driven by the driving force of the motor generator 30. Further, when the vehicle is driven by the driving force of the engine 11, the driving force of the motor generator 30 can be used as an auxiliary force for driving.

  Furthermore, in the present embodiment, the rotational power of the wheels 15 is transmitted to the motor generator 30 via the axle 14, the differential 13 and the transmission 12, so that the motor generator 30 can generate power. That is, the motor generator 30 generates power by so-called regenerative brake control. The electric power generated by the motor generator 30 is stored in the battery 17 and used for driving the motor generator 30 and for operating other devices and devices. The motor generator 30 is controlled by an electronic control unit (ECU) (not shown). The ECU controls devices and devices mounted on the vehicle based on information from sensors attached to the vehicle. The detailed configuration of the motor generator 30 will be described later.

As shown in FIG. 2, the power transmission device 1 includes a housing 20, a motor generator 30, a flywheel 40, a clutch 50, a damper 60, and the like.
The housing 20 is formed in a cylindrical shape from metal, for example. The housing 20 has one end connected to the engine housing 111 of the engine 11 and the other end connected to the transmission housing 121 of the transmission 12. The housing 20 includes a hollow cylindrical tube portion 21 and a disk-shaped support portion 22 extending radially inward from the inner wall of the tube portion 21. An insertion hole 221 is formed at the center of the support portion 22. The support portion 22 is formed with a housing cylinder portion 222 that extends in a hollow cylindrical shape from the edge of the insertion hole 221 toward the engine 11 side. In the present embodiment, the housing tubular portion 222 extends substantially to the end portion of the tubular portion 21 on the engine 11 side.

  The motor generator 30 is accommodated in the housing 20 so as to be positioned inside the cylindrical portion 21. The motor generator 30 has a stator 31, a rotor 32, and a rotor shaft 33. The stator 31 is formed in a hollow cylindrical shape by laminating silicon steel plates, for example. The stator 31 is accommodated and fixed in the housing 20 by fitting so that the outer wall faces the inner wall of the cylindrical portion 21. A plurality of windings 311 are wound around the stator 31. The winding 311 is wound around a plurality of salient poles that protrude inward in the radial direction of the stator 31.

  The rotor 32 is formed in a hollow cylindrical shape by laminating silicon steel plates, for example, like the stator 31. The rotor 32 is rotatably provided inside the stator 31 so that the outer wall faces the inner wall of the stator 31. A predetermined gap is formed between the outer wall of the rotor 32 and the inner wall of the stator 31.

  The rotor shaft 33 is formed in a substantially cylindrical shape from metal. The rotor shaft 33 includes a shaft portion 331, a first tube portion 332, a second tube portion 333, an annular portion 334, and a connection portion 335. The shaft portion 331 is formed at the end of the rotor shaft 33 on the engine 11 side. The first cylindrical portion 332 is provided so that the outer wall is fitted to the inner wall of the rotor 32. The second cylinder part 333 forms a substantially cylindrical space 34 between the outer wall of the shaft part 331. The annular part 334 connects the inner wall of the first cylinder part 332 and the outer wall of the second cylinder part 333. In the present embodiment, the annular portion 334 connects the transmission 12 side end portion of the first cylindrical portion 332 and the transmission 12 side end portion of the second cylindrical portion 333. The connection part 335 connects the inner wall of the second cylinder part 333 and the outer wall of the shaft part 331. A substantially cylindrical accommodation space 35 is formed between the first cylinder portion 332 and the second cylinder portion 333 on the engine 11 side of the annular portion 334.

  The housing cylindrical portion 222 described above extends in a hollow cylindrical shape through the space 34 toward the engine 11 side, and a shaft portion 331 is inserted inside. Between the outer wall of the housing cylindrical portion 222 and the inner wall of the second cylindrical portion 333 of the rotor shaft 33, a bearing 23 is provided as a bearing portion. The bearings 23 are formed in an annular shape, and two bearings 23 are provided at a predetermined distance in the axial direction of the shaft portion 331. One of the two bearings 23 is provided to be positioned closer to the axial transmission 12 than the end of the rotor 32 on the engine 11 side. The other of the two bearings 23 is provided so as to be positioned closer to the axial engine 11 side than the transmission 12 side end of the rotor 32. That is, the two bearings 23 are provided so as to be positioned within the axial width of the rotor 32.

  As described above, the second cylinder portion 333 of the rotor shaft 33 is rotatably supported by the housing cylinder portion 222 of the housing 20 via the bearing 23. Thereby, the rotor 32 is rotatably supported by the housing 20 via the rotor shaft 33 and the bearing 23. As described above, the rotor shaft 33 is fitted to the inner wall of the rotor 32 and is rotatably supported by the housing 20. The end of the rotor shaft 33 opposite to the shaft 331 is connected to the input shaft 122 of the transmission 12.

The flywheel 40 is formed in a substantially disc shape by metal, for example, and is connected to the output shaft 112 of the engine 11 by a bolt 18.
The clutch 50 is provided between the output shaft 112 of the engine 11 and the rotor shaft 33, more specifically, between the flywheel 40 and the rotor shaft 33. The clutch 50 includes a drum 51, a friction engagement element 52, a pressing member 53, and an urging member 54. The drum 51 has a substantially cylindrical tube portion 511 in which at least a part in the axial direction is located in the accommodation space 35.
The friction engagement element 52 includes a plurality of friction plates 521 and a plurality of friction plates 522. The plurality of friction plates 521 are formed in an annular shape, and are provided at predetermined intervals so that the outer edge portion is connected to the inner wall of the cylindrical portion 511. The plurality of friction plates 522 are formed in an annular shape having a smaller diameter than the friction plates 521, and are provided between the plurality of friction plates 521 so that the inner edge portion is connected to the outer wall of the second cylindrical portion 333 of the rotor shaft 33. Yes.

The pressing member 53 is formed in a substantially annular shape, and is provided on the engine 11 side of the friction engagement element 52. Here, the pressing member 53 can contact the friction plate 521 located closest to the engine 11 among the plurality of friction plates 521.
One end of the urging member 54 is accommodated in an accommodation groove 513 formed on the cylinder 11 511 of the drum 51 on the engine 11 side. The other end of the urging member 54 is in contact with the pressing member 53. The biasing member 54 is a coil spring in this embodiment, and has a force extending in the axial direction. Thereby, the urging member 54 urges the pressing member 53 toward the engine 11.

  A substantially disc-shaped plate member 55 is attached to the end surface of the rotor shaft 33 on the engine 11 side. The plate member 55 closes the engine 11 side opening of the cylindrical portion 511. Thereby, a substantially annular hydraulic space 56 is formed between the plate member 55 and the pressing member 53. That is, the hydraulic space 56 is formed on the side of the pressing member 53 opposite to the friction engagement element 52.

  In the present embodiment, a first oil passage 336 extending in the axial direction of the rotor shaft 33 and a radially outer side of the rotor shaft 33 extending from the first oil passage 336 to the hydraulic space 56 are communicated with the rotor shaft 33. A second oil passage 337 is formed. The hydraulic oil discharged from the pump 16 is supplied to the transmission mechanism of the transmission 12 and is controlled by a control valve (not shown) to be supplied to the hydraulic space 56 via the first oil passage 336 and the second oil passage 337. The When hydraulic oil is supplied to the hydraulic space 56, the pressure in the hydraulic space 56 increases. Then, the pressing member 53 moves to the transmission 12 side against the urging force of the urging member 54 and is pressed against the friction plate 521 located closest to the engine 11 side. Accordingly, the plurality of friction plates 521 connected to the cylindrical portion 511 of the drum 51 are pushed and moved together with the cylindrical portion 511 to the transmission 12 side, and are connected to the second cylindrical portion 333 of the rotor shaft 33. Engages with a plurality of friction plates 522. As a result, the flywheel 40 (output shaft 112) and the rotor shaft 33 are connected via the clutch 50.

  Thus, the clutch 50 has the friction engagement element 52, and the output shaft 112 and the rotor shaft 33 can be connected by engaging the friction engagement element 52. Thereby, the driving force output from the output shaft 112 of the engine 11 can be transmitted to the transmission 12 via the rotor shaft 33.

  The damper 60 is a coil spring in this embodiment, and can be elastically deformed in the axial direction. The damper 60 connects the flywheel 40 and the clutch 50. More specifically, as shown in FIG. 3A, five dampers 60 are provided along the circumferential direction of the flywheel 40 between the flywheel 40 and the drum 51 of the clutch 50. The flywheel 40 and the drum 51 are relatively rotatable. When the flywheel 40 and the drum 51 rotate relative to each other, the damper 60 is elastically deformed.

In the present embodiment, as shown in FIG. 2, a substantially annular seal member 57 is provided between the outer edge portion of the plate member 55 attached to the rotor shaft 33 and the drum 51. Thereby, the space between the plate member 55 and the drum 51 is kept liquid-tight.
A more detailed configuration of the seal member 57 is shown in FIG. The seal member 57 is accommodated in an accommodation groove 512 formed in the drum 51. The seal member 57 includes a metal part 571, a rubber part 572, and a spring 573. The metal portion 571 is formed in a substantially annular shape from metal, and is provided so that the outer wall is fitted to the wall surface 513 of the accommodation groove 512. The rubber part 572 is formed in a substantially annular shape from rubber and is provided so as to be connected to the inside in the radial direction of the metal part 571. The inner edge portion 574 of the rubber portion 572 is in contact with the outer wall of the plate member 55. The spring 573 is formed in an annular shape by connecting both ends of a coil spring, for example, and is provided on the radially outer side of the inner edge portion 574 of the rubber portion 572. The spring 573 has a force of contracting radially inward in a state of being provided radially outward of the inner edge portion 574. As a result, the inner edge portion 574 comes into close contact with the plate member 55, and the space between the inner edge portion 574 and the outer wall of the plate member 55 is kept liquid-tight. The inner edge portion 574 is formed such that the surface facing the outer wall of the plate member 55 has an inversely tapered shape on the engine 11 side and the transmission 12 side. Therefore, the contact area between the inner edge portion 574 and the outer wall of the plate member 55 is relatively small. As a result, the inner edge portion 574 can slide smoothly with the plate member 55 while being kept fluid-tight with the plate member 55.

In the present embodiment, as shown in FIG. 2, a substantially annular seal member 58 is provided between the outer wall of the second cylindrical portion 333 of the rotor shaft 33 and the inner edge portion of the pressing member 53. The seal member 58 is different from the seal member 57 only in diameter, and the configuration itself is the same as the configuration of the seal member 57, and thus the description thereof is omitted. The seal member 58 can slide smoothly with the second cylinder portion 333 while keeping the liquid tightness between the second cylinder portion 333 and the pressing member 53.
In the present embodiment, the seal member 57 and the seal member 58 keep liquid tightness between the inside and the outside of the hydraulic space 56.

Next, an example of the operation of the power transmission device 1 according to the present embodiment will be described with reference to FIGS.
When the engine 11 is driven, the output shaft 112 rotates. Thereby, the flywheel 40 connected to the output shaft 112 and the clutch 50 connected by the flywheel 40 and the damper 60 rotate. At this time, since the output shaft 112 and the rotor shaft 33 are not connected, the driving force of the engine 11 is not transmitted to the rotor shaft 33.

  When hydraulic fluid is supplied from the pump 16 via the control valve, the first oil passage 336 and the second oil passage 337 to the hydraulic space 56, the pressure in the hydraulic space 56 increases, and the pressing member 53 moves to the friction engagement element 52. The plurality of friction plates 521 and the plurality of friction plates 522 of the friction engagement element 52 are engaged with each other. As a result, the flywheel 40 (output shaft 112) and the rotor shaft 33 are connected. As a result, the driving force of the engine 11 is transmitted to the input shaft 122 of the transmission 12 via the rotor shaft 33. The driving force of the engine 11 transmitted to the input shaft 122 is transmitted to the wheel 15 via the differential 13 and the axle 14. Thereby, the vehicle travels.

  When the motor generator 30 is driven with the clutch 50 connecting the output shaft 112 and the rotor shaft 33, the driving force of the motor generator 30 passes through the rotor shaft 33 together with the driving force of the engine 11. It is transmitted to the input shaft 122. As described above, when the vehicle is driven by the driving force of the engine 11, the driving force of the motor generator 30 can be used as an auxiliary force for driving.

When the supply of hydraulic oil from the pump 16 to the hydraulic space 56 is stopped, the pressure in the hydraulic space 56 decreases. Therefore, the pressing member 53 moves to the engine 11 side by the urging force of the urging member 54. Accordingly, the engagement between the plurality of friction plates 521 and the plurality of friction plates 522 is released, and the connection between the output shaft 112 and the rotor shaft 33 is released. When the motor generator 30 is driven in this state, that is, when the output shaft 112 and the rotor shaft 33 are not connected, only the driving force of the motor generator 30 passes through the rotor shaft 33 and the input shaft of the transmission 12. 122. As described above, in the present embodiment, the vehicle can be driven only by the driving force of the motor generator 30.
Further, when the vehicle occupant performs a brake operation, regenerative brake control is performed by the ECU. Thereby, the motor generator 30 generates electric power, and the electric power generated by the electric power generation is accumulated in the battery 17.

  As described above, in the present embodiment, the rotor shaft 33 includes the shaft portion 331 formed at the end on the engine 11 side, the first tube portion 332 provided so that the outer wall is fitted to the inner wall of the rotor 32, and the shaft. A second cylindrical part 333 that forms a substantially cylindrical space 34 between the outer wall of the part 331 and an annular part 334 that connects the inner wall of the first cylindrical part 332 and the outer wall of the second cylindrical part 333 are provided. The housing 20 has a housing cylindrical portion 222 that extends in a hollow cylindrical shape through the space 34 toward the engine 11 and into which the shaft portion 331 of the rotor shaft 33 is inserted. Between the outer wall of the housing cylinder part 222 and the inner wall of the second cylinder part 333 of the rotor shaft 33, a bearing 23 for bearing the rotor shaft 33 is provided. Thereby, it can be set as the structure which arrange | positions the bearing 23 to the axial center vicinity of the rotor 32. FIG. Therefore, the rotor 32 can be supported by bearings in the vicinity of the center in the axial direction, and balance adjustment of the rotor 32 becomes easy. As a result, the number of steps for improving the balance adjustment accuracy of the rotor 32 can be reduced, and there is no need to increase the diameter of the rotating member to ensure shaft rigidity.

  In the present embodiment, a portion of the housing 20 that fixes the stator 31 (tubular portion 21) and a portion that supports and supports the rotor 32 and the rotor shaft 33 (housing cylindrical portion 222) are integrally formed. Thereby, the gap management accuracy between the stator 31 and the rotor 32 can be improved. Therefore, the efficiency of the motor can be increased.

  In the present embodiment, a substantially cylindrical accommodation space 35 is formed on the engine 11 side of the annular portion 334 between the first cylinder portion 332 and the second cylinder portion 333 of the rotor shaft 33. At least a part of the clutch 50 (such as the cylinder portion 511 of the drum 51 and the friction engagement element 52) is accommodated in the accommodation space 35. That is, the clutch 50 and the rotor 32 are arranged so as to partially overlap in the axial direction of the rotor 32. Thereby, the physique of the power transmission device 1 can be made small.

  Further, in this embodiment, since a part of the clutch 50 (the cylinder portion 511 of the drum 51 and the friction engagement element 52 and the like) is accommodated in the accommodation space 35, power transmission is performed even if the friction engagement element 52 is enlarged. The size of the apparatus 1 in the axial direction is not increased. Therefore, the amount of heat generated from each friction plate 521 and each friction plate 522 can be reduced by increasing the number of friction plates 521 and friction plates 522 of the friction engagement element 52. Thereby, abnormal heating of the clutch 50 can be prevented without increasing the size of the power transmission device 1.

  In the present embodiment, the bearing 23 is provided so as to be positioned within the axial width of the rotor 32. Thereby, the rotor 32 can be supported by bearings at a position relatively close to the center in the axial direction. Therefore, balance adjustment of the rotor 32 can be performed more easily.

  In the present embodiment, the housing 20 has an end on the engine 11 side connected to the engine housing 111 of the engine 11, and an end on the transmission 12 side connected to the transmission housing 121 of the transmission 12. Thereby, the axial shift of the output shaft 112 of the engine 11 and the input shaft 122 of the transmission 12 can be suppressed.

  Furthermore, in the present embodiment, the rotor shaft 33 is formed with a first oil passage 336 and a second oil passage 337 through which hydraulic oil supplied to the hydraulic space 56 flows. Therefore, the hydraulic oil can be easily introduced into the first oil passage 336 and the second oil passage 337 from the transmission 12 side. Thereby, it becomes easy to divert the hydraulic oil supplied to the transmission 12 to operate the transmission 12 as the hydraulic oil of the clutch 50. Therefore, it is not necessary to form a new hydraulic circuit for operating the clutch 50, and the cost can be reduced.

(Second Embodiment)
A power transmission device according to a second embodiment of the present invention is shown in FIG. The second embodiment differs from the first embodiment in the arrangement of the clutch with respect to the rotor.

  In the second embodiment, the annular portion 334 of the rotor shaft 33 includes the vicinity of the axial center of the inner wall of the first cylindrical portion 332 and the vicinity of the end portion on the transmission 12 side in the axial direction of the outer wall of the second cylindrical portion 333. And connected. That is, in the second embodiment, compared to the first embodiment, the annular portion 334, the end portion of the second cylinder portion 333 on the transmission 12 side, and the accommodation space 35 are located closer to the engine 11 side. Accordingly, the base portion of the housing cylindrical portion 222 is formed thicker than that in the first embodiment. The two bearings 23 are provided near the center in the axial direction of the rotor 32 so as to be adjacent to each other.

In the present embodiment, the second oil passage 337 is formed to extend from the first oil passage 336 to the outer side in the radial direction of the rotor shaft 33 so as to be inclined toward the engine 11 with respect to the first oil passage 336. Here, the first oil passage 336 and the second oil passage 337 are formed by a wall surface on the engine 11 side that forms the first oil passage 336 of the rotor shaft 33 and a wall surface on the engine 11 side that forms the second oil passage 337. The angle is formed to be 180 degrees.
The points other than the above-described configuration of the second embodiment are the same as those of the first embodiment.

  As described above, in the present embodiment, the base portion of the housing cylindrical portion 222 is formed thick. Thereby, the strength and rigidity of the housing cylindrical portion 222 are improved, and the bearings of the rotor 32 and the rotor shaft 33 by the housing 20 can be kept stable and highly accurate.

  In the present embodiment, the second oil passage 337 is formed to extend from the first oil passage 336 to the outer side in the radial direction of the rotor shaft 33 so as to be inclined toward the engine 11 with respect to the first oil passage 336. Further, the first oil passage 336 and the second oil passage 337 are angles formed by the engine 11 side wall surface that forms the first oil passage 336 of the rotor shaft 33 and the engine 11 side wall surface that forms the second oil passage 337. Is formed to be 180 degrees. Thereby, the pressure loss in the connection part of the 1st oil path 336 and the 2nd oil path 337 of the hydraulic oil which flows through the 1st oil path 336 and the 2nd oil path 337 can be reduced. As a result, the responsiveness regarding the operation of the clutch 50 can be improved.

(Third embodiment)
A power transmission device according to a third embodiment of the present invention is shown in FIG. The third embodiment differs from the first embodiment in the arrangement of the pressing member and the hydraulic space with respect to the friction engagement element.

  In the third embodiment, the annular portion 334 of the rotor shaft 33 is slightly closer to the transmission 12 than the axial center of the inner wall of the first cylindrical portion 332 and the axial center of the outer wall of the second cylindrical portion 333. The neighborhood is connected. Further, the connection portion 335 of the rotor shaft 33 connects the vicinity of the center in the axial direction of the inner wall of the second cylindrical portion 333 and the end portion on the engine 11 side of the outer wall of the shaft portion 331. Accordingly, the two bearings 23 are provided so as to be adjacent to each other and slightly closer to the transmission 12 from the axial center of the rotor 32.

  In the third embodiment, the pressing member 53 is provided on the transmission 12 side of the friction engagement element 52, unlike the first embodiment. Accordingly, the hydraulic space 56 is also formed on the transmission 12 side with respect to the friction engagement element 52. The urging member 54 is accommodated in an accommodation groove 613 formed on the transmission 12 side of the cylinder portion 611 of the drum 51, and is provided to urge the pressing member 53 toward the transmission 12 side.

  In the third embodiment, the plate member 55 of the first embodiment is not provided, and the seal member 57 and the seal member 58 are provided on the transmission 12 side with respect to the friction engagement element 52. The seal member 57 keeps the space between the annular portion 334 and the drum 51 of the clutch 50 liquid-tight. Further, the seal member 58 keeps a liquid-tight space between the second cylinder portion 333 and the pressing member 53. Thereby, the space between the inside and the outside of the hydraulic space 56 is kept liquid-tight.

  In the present embodiment, the second oil passage 337 is formed closer to the transmission 12 than the friction engagement element 52. Further, the rotor shaft 33 is formed so that the inner part of the friction engagement element 52 is hollow. That is, in this embodiment, the axial length of the shaft portion 331 is shorter than that in the first embodiment.

In the present embodiment, when hydraulic oil is supplied to the hydraulic space 56, the pressing member 53 comes into contact with and is pressed against the friction plate 521 located closest to the transmission 12 among the plurality of friction plates 521, thereby causing the drum 51. The cylinder portion 611 moves to the engine 11 side. Thereby, the friction engagement element 52 is engaged, and the output shaft 112 of the engine 11 and the rotor shaft 33 are connected.
Points other than the above-described configuration of the third embodiment are the same as those of the first embodiment.

  As described above, in the present embodiment, the hydraulic space 56 is formed on the transmission 12 side of the friction engagement element 52. Therefore, the second oil passage 337 can be formed closer to the transmission 12 than the friction engagement element 52. Thereby, the part inside the friction engagement element 52 of the rotor shaft 33 can be made hollow. As a result, the inertia mass of the rotor shaft 33 can be reduced.

(Fourth embodiment)
A power transmission device according to a fourth embodiment of the present invention is shown in FIG. The fourth embodiment differs from the third embodiment in the arrangement of the clutch with respect to the rotor, the shape of the second oil passage, and the like.

In the fourth embodiment, the clutch 50 is disposed slightly closer to the transmission 12 than in the third embodiment. In the present embodiment, the second oil passage 337 is formed to extend radially outward of the rotor shaft 33 from the first oil passage 336 so as to be inclined toward the transmission 12 with respect to the first oil passage 336. . A plate member 338 is provided on the inner side of the second cylindrical portion 333 on the end surface of the rotor shaft 33 on the engine 11 side. The plate member 338 closes the opening of the first oil passage 336 of the rotor shaft 33.
The points other than the above-described configuration of the fourth embodiment are the same as those of the third embodiment.

  As described above, in the present embodiment, the second oil passage 337 extends from the first oil passage 336 to the radially outer side of the rotor shaft 33 so as to be inclined toward the transmission 12 with respect to the first oil passage 336. Is formed. This configuration can be easily realized by forming the second oil passage 337 from the end surface of the rotor shaft 33 on the engine 11 side by, for example, cutting. Thus, in this embodiment, the workability of the second oil passage 337 can be improved.

(Other embodiments)
In the above-described embodiment, the example in which the friction engagement element is configured by a plurality of friction plates has been described. On the other hand, in another embodiment of the present invention, the friction engagement element may be constituted by a single friction plate.

In another embodiment of the present invention, the clutch may operate by being supplied with hydraulic oil from a pump other than a pump that supplies hydraulic oil for the transmission.
The power transmission device according to the present invention can also be applied to a vehicle equipped with a transmission other than CVT (for example, AT).

  Thus, the present invention is not limited to the above-described embodiments, and can be applied to various forms without departing from the gist thereof.

DESCRIPTION OF SYMBOLS 1 ... Power transmission device 11 ... Engine 112 ... Output shaft 12 ... Transmission 122 ... Input shaft 20 ... Housing 222 ... Housing cylinder part 23 ... ..Bearings (bearing parts)
30 ... Motor generator 31 ... Stator 311 ... Winding 32 ... Rotor 33 ... Rotor shaft 331 ... Shaft portion 332 ... First tube portion 333 ... Second cylindrical portion 334 ... annular portion 34 ... space 35 ... housing space 50 ... clutch

Claims (7)

A power transmission device for transmitting engine driving force to a transmission,
A housing;
A cylindrical stator that is housed and fixed in the housing and wound with a winding, a cylindrical rotor that is rotatably provided inside the stator, and an inner wall of the rotor that fits and can rotate on the housing A motor generator having a rotor shaft supported by and connected to the input shaft of the transmission;
A clutch provided between the output shaft of the engine and the rotor shaft, and capable of connecting the output shaft and the rotor shaft;
The rotor shaft is
A shaft formed at the end of the engine,
A first cylindrical portion provided so that an outer wall is fitted to the inner wall of the rotor;
A second cylindrical portion that forms a cylindrical space with the outer wall of the shaft portion; and
An annular portion connecting the inner wall of the first tube portion and the outer wall of the second tube portion;
Between the first cylinder part and the second cylinder part, a cylindrical accommodation space is formed on the engine side of the annular part,
At least a part of the clutch is housed in the housing space,
The housing has a housing cylinder portion that extends in a cylindrical shape toward the engine side through the space and into which the shaft portion is inserted.
Between the outer wall of the said housing cylinder part and the inner wall of the said 2nd cylinder part, the bearing part which bears the said rotor shaft is provided, The power transmission device characterized by the above-mentioned.   The power transmission device according to claim 1, wherein the bearing portion is provided so as to be positioned within an axial width of the rotor.   The said housing is connected to the engine housing of the engine, and the transmission side end is connected to the transmission housing of the transmission. Power transmission device. The clutch is
A drum having at least a part in the axial direction and having a cylindrical portion located in the accommodation space, connected to the output shaft;
A frictional engagement element provided to connect to the inner wall of the cylindrical portion and the outer wall of the second cylindrical portion; and
An annulus provided on the engine side of the friction engagement element between the cylinder part and the second cylinder part and capable of engaging the friction engagement element by being pressed against the friction engagement element Having a pressing member,
On the opposite side of the pressing member from the friction engagement element, a hydraulic space is formed,
The rotor shaft is formed with a first oil passage extending in the axial direction of the rotor shaft and a second oil passage extending from the first oil passage outward in the radial direction of the rotor shaft and communicating with the hydraulic space. ,
When the hydraulic oil is supplied to the hydraulic space via the first oil path and the second oil path, the pressing member is pressed against the friction engagement element, so that the friction engagement element is engaged. The power transmission device according to any one of claims 1 to 3, wherein the output shaft and the rotor shaft are connected to each other.   The said 2nd oil path is formed so that it may extend in the radial direction outer side of the said rotor shaft from the said 1st oil path so that it may incline to the said engine side with respect to the said 1st oil path. The power transmission device described in 1. The clutch is
A drum having at least a part in the axial direction and having a cylindrical portion located in the accommodation space, connected to the output shaft;
A frictional engagement element provided to connect to the inner wall of the cylindrical portion and the outer wall of the second cylindrical portion; and
It is provided on the transmission side of the friction engagement element between the cylinder part and the second cylinder part, and can be engaged with the friction engagement element by being pressed against the friction engagement element. Having an annular pressing member,
On the opposite side of the pressing member from the friction engagement element, a hydraulic space is formed,
The rotor shaft is formed with a first oil passage extending in the axial direction of the rotor shaft and a second oil passage extending from the first oil passage outward in the radial direction of the rotor shaft and communicating with the hydraulic space. ,
When the hydraulic oil is supplied to the hydraulic space via the first oil path and the second oil path, the pressing member is pressed against the friction engagement element, so that the friction engagement element is engaged. The power transmission device according to any one of claims 1 to 3, wherein the output shaft and the rotor shaft are connected to each other.   The said 2nd oil path is extended and formed in the radial direction outer side of the said rotor shaft from the said 1st oil path so that it may incline to the said transmission side with respect to the said 1st oil path. 6. The power transmission device according to 6.

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