JP2011214671A - Transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a transmission device capable of cooling a clutch effectively while suppressing influence on other parts arising from the deformation of a clutch housing.SOLUTION: The transmission device 1 includes: a first shaft I drive-connected with an internal combustion engine; a second shaft M drive-connected with a transmission device TM; a clutch CL provided between the first shaft I and the second shaft M; and a case 2 accommodating these parts. A clutch housing CH is drive-connected so as to rotate integrally with the second shaft M and surrounds and accommodates the clutch CL. The first shaft I entering into the clutch housing CH and having a flange part 11 is supported by the second shaft M from other side in the axial direction via a first bearing 51 and the second shaft M is supported rotatably by the case 2 from the other side in the axial direction. The radially extended part at one side is supported by the flange part 11 from the other side in the axial direction via a second bearing 52.

Description

  The present invention includes a first shaft that is drivingly connected to an internal combustion engine, a second shaft that is disposed coaxially with the first shaft and that is drivingly connected to a speed change mechanism, and a driving force between the first shaft and the second shaft. The present invention relates to a transmission that includes a clutch that can be switched between transmission and disconnection, a first shaft, a second shaft, and a case that houses the clutch.

  Transmission and cut-off of driving force between the first shaft and the second shaft, a first shaft that is drivingly connected to the internal combustion engine, a second shaft that is arranged coaxially with the first shaft and that is drivingly connected to the speed change mechanism, and For example, a device described in Patent Document 1 below is already known as a transmission including a clutch that can be switched, a first shaft, a second shaft, and a case that houses the clutch. As shown in FIG. 2 of the patent document 1, this transmission is drivingly connected so as to rotate integrally with a second shaft (the input shaft 18 of the automatic transmission 16), and a rotor support member (motor support member). 12) and a clutch housing that encloses both sides in the axial direction and radially outside of the clutch (engine clutch 24) and accommodates the clutch. The clutch housing is supported on one side in the axial direction by one side wall portion of the case (motor housing 22) from one side in the axial direction via a ball bearing (support bearing 30) in the axial direction and the radial direction, and the other in the axial direction. On the side, it is supported in the axial direction via a thrust bearing from the other side in the axial direction by an intermediate support wall portion of a case accommodating the oil pump therein.

JP 2009-051484 A

  By the way, if it is intended to support the clutch housing in the axial direction via the thrust bearing by the intermediate support wall, the contact surface for contacting the thrust bearing is placed around the surface of the intermediate support wall on the clutch housing side. It is necessary to form over the entire direction. However, in the configuration in which the oil pump is accommodated inside the intermediate support wall portion as in the device of Patent Document 1, an oil passage through which oil discharged from the oil pump flows is formed in the intermediate support wall portion. For this reason, the weight of the intermediate support wall portion that houses the oil pump increases. That is, while forming an oil passage for oil to flow, it is necessary to form an abutment surface in accordance with the portion that protrudes most toward the clutch housing side in order to form the oil passage, so the intermediate support wall portion It becomes unnecessarily thick and increases in weight, and the weight of the entire transmission increases accordingly.

  Therefore, it is desired to realize a transmission that can appropriately support the clutch housing in the axial direction without increasing the weight of the entire apparatus.

  A first shaft that is drivingly connected to the internal combustion engine according to the present invention, a second shaft that is disposed coaxially with the first shaft and is drivingly connected to the speed change mechanism, and between the first shaft and the second shaft The transmission is provided with a clutch that can be switched between transmission and disconnection of the driving force, the first shaft, the second shaft, and a case that houses the clutch. One side radial extending portion extending in the radial direction and disposed on one side in the axial direction of the clutch, and the other side diameter extending in the radial direction on the other side in the axial direction of the clutch. A clutch housing that accommodates the clutch having a direction extending portion and an axial extending portion that is disposed radially outside the clutch and extends in the axial direction, wherein the first shaft is in the one radial direction The clutch housing passes through the radially inner side of the extension. The first shaft is supported by the second shaft from the other side in the axial direction through the first bearing, and the second shaft is The case is supported by the case in a rotatable state from the other side in the axial direction, and the one side radially extending portion is supported by the flange portion from the other side in the axial direction via a second bearing.

According to the above characteristic configuration, the second shaft is supported by the case in a rotatable state from the other side in the axial direction, the first shaft is supported by the second shaft from the other side in the axial direction via the first bearing, A radially extending portion on one side of the clutch housing is supported by a flange portion of the first shaft from the other side in the axial direction via a second bearing. That is, the radially extending portion on one side of the clutch housing is supported by the case through the second bearing, the flange portion, the first shaft, the first bearing, and the second shaft so as to be rotatable from the other side in the axial direction. The Therefore, the entire clutch housing can be appropriately supported in the axial direction from the other side in the axial direction by the case. Accordingly, it is possible to employ a configuration in which a bearing for receiving an axial load is omitted on the other axial side of the clutch housing. In this case, it is not necessary to determine the shape of the component arranged on the other side in the axial direction with respect to the clutch housing in consideration of the bearing for receiving the axial load. Therefore, as long as the function of the part can be ensured, the part can be reduced in weight, and the weight of the entire apparatus is hardly increased.
Therefore, according to said characteristic structure, the transmission which can support a clutch housing in an axial direction appropriately can be provided, without increasing the weight of the whole apparatus.

  Here, the case includes a support wall portion that is disposed on the other side in the axial direction with respect to the clutch housing and accommodates an oil pump therein, and the other-side radial extension portion and the support wall portion include It is preferable to adopt a configuration in which a predetermined interval is provided in the axial direction without any other member interposed therebetween.

The characteristic configuration of the present application can be suitably applied to a transmission having a configuration in which an oil pump is accommodated in a support wall portion disposed on the other axial side with respect to the clutch housing.
That is, according to the above configuration, even if the oil passage through which oil discharged by the oil pump flows is formed in the support wall portion, the shaft of the support wall portion is considered in consideration of the existence of the oil passage. It is not necessary to form a contact surface for contacting the thrust bearing on the surface on the clutch housing side that is one side in the direction. Therefore, it is sufficient to determine the shape of the support wall portion so that at least the oil passage can be appropriately formed, so that the support wall portion is formed thinner than in the case of forming the contact surface as described above. The weight of the support wall can be reduced.
Further, for example, compared to a case where a bearing that receives an axial load is disposed between the other-side radial extending portion and the support wall portion, the manufacturing cost of the transmission is reduced by the amount that such a bearing is omitted. Can be reduced.

  Further, it is preferable that an oil chamber filled with oil is formed inside the clutch housing.

According to this configuration, since the oil chamber formed in the clutch housing is filled with oil, the clutch housed in the clutch housing can be effectively cooled by a large amount of oil.
In this configuration, when the clutch housing rotates integrally with the second shaft, the clutch housing may be deformed so as to expand in the axial direction due to the centrifugal force acting on the oil filled in the clutch housing. There is. However, in the present application, as described above, a bearing for receiving an axial load can be omitted on the other axial side of the clutch housing. Therefore, even if the clutch housing is deformed so as to expand in the axial direction due to the centrifugal force acting on the oil filled in the clutch housing when the clutch housing rotates integrally with the second shaft, it is omitted. The axial movement of the other axial part of the clutch housing is allowed by the amount of the bearing. Therefore, there is almost no influence on other parts arranged in the vicinity of the clutch housing.
Therefore, according to said structure, a clutch can be cooled effectively, suppressing the influence on other components resulting from a deformation | transformation of a clutch housing.

  Further, the case includes a support wall portion that is disposed on the other axial side with respect to the clutch housing and accommodates an oil pump therein, and the other-side radial extending portion and the support wall portion include: It is arranged at a predetermined interval in the axial direction without any other member in between, and the axial separation distance between the other-side radial extending portion and the supporting wall portion is such that the clutch housing From the maximum value of the distance that the clutch housing is deformed by the influence of centrifugal force acting on the oil filled therein when it rotates and the other side radially extending portion can move toward the other side in the axial direction Is preferably set to a large value.

  According to this configuration, even if the other-side radial extending portion moves to the maximum extent in the other axial direction due to deformation of the clutch housing, the other-side radial extending portion axially moves the support wall portion. Can be prevented from being pressed. Therefore, it is possible to prevent a decrease in the rotation efficiency of the oil pump accommodated inside the support wall portion.

  In this case, the axial separation distance between the other radial extension portion and the support wall portion is affected by the centrifugal force acting on the oil filled therein when the clutch housing rotates. The clutch housing is deformed so that the maximum distance that the other side radially extending portion can move toward the other side in the axial direction and one that is provided to support the second shaft with respect to the case. Or it is more suitable if it is set as the structure set to the larger value than the sum total of the support clearance of two or more bearings.

  The “bearing support clearance” means a clearance required for two members arranged on both sides of the bearing in the support direction to be supported in a relatively rotatable state.

  According to this configuration, all the bearing clearances of the respective bearings provided in the transmission are clogged, and the other-side radial extending portion moves to the maximum in the axial direction due to deformation of the clutch housing. However, it can prevent that the other side radial direction extension part presses a support wall part to an axial direction. Therefore, in consideration of the support clearance of each bearing, it is possible to almost certainly prevent a decrease in the rotational efficiency of the oil pump accommodated inside the support wall.

  In addition, it is preferable that the end of the clutch housing on the other side in the axial direction is splined so as to be relatively displaceable in the axial direction with respect to the second shaft.

  According to this configuration, the configuration in which the movement of the clutch housing on the other side in the axial direction of the clutch housing is allowed while appropriately realizing the configuration in which the clutch housing is driven and connected so as to rotate integrally with the second shaft. It can be realized appropriately.

  Further, on the other side in the axial direction of the flange portion, the other side radially extending portion and the flange portion are arranged at a predetermined interval in the axial direction without any other member interposed therebetween. It is preferable.

In the present invention, the entire clutch housing is supported by supporting the one side radially extending portion in the axial direction by the case via the second bearing, the flange portion, the first shaft, the first bearing, and the second shaft. It is supported in the axial direction by the case. Therefore, on the other axial side of the flange portion, a special support structure for supporting the portion on the other axial side of the clutch housing in the axial direction with respect to the flange portion is not necessarily required.
According to this configuration, for example, compared to the case where a bearing that receives an axial load is disposed between the flange portion and the other axial portion of the clutch housing, the amount of such a bearing is omitted. The shaft length of the transmission can be shortened and the manufacturing cost can be reduced.

  Alternatively, on the other axial side of the flange portion, it is preferable that the other radial extension portion is supported by the flange portion from one axial side through a third bearing.

  According to this configuration, the portion on the other axial side of the clutch housing and the flange portion can be appropriately and smoothly relatively rotated. Further, when the third bearing is fitted and disposed on both the axially other side portion of the clutch housing and the flange portion, the clutch housing is filled with the sliding resistance of the fitting portion. The axial deformation of the clutch housing due to the influence of centrifugal force acting on the oil can be suppressed.

  In the configuration described so far, an oil chamber filled with oil is formed inside the clutch housing, and the second shaft opens to an end surface on one axial side of the inner diameter portion and flows out of the oil chamber. The first bearing is formed in an annular plate shape and communicates at least between the outer peripheral surface and the inner peripheral surface in the radial direction. It is preferable to have a configuration having parts.

  According to this configuration, the first shaft receives the first shaft and the second shaft on both sides in the axial direction of the first bearing formed in an annular plate shape, so that the first shaft is connected to the second shaft via the first bearing. Thus, a structure supported in the axial direction can be appropriately realized. In addition, since the first bearing has a communication portion that communicates at least between the outer peripheral surface and the inner peripheral surface in the radial direction, the first bearing flows out from the oil chamber formed inside the clutch housing and is disposed on the outer peripheral side of the first bearing. The reaching oil can be guided to the inner peripheral side through the communication portion, and further appropriately discharged through the in-shaft oil passage formed in the inner diameter portion of the second shaft.

It is a schematic diagram which shows schematic structure of the hybrid drive device which concerns on 1st embodiment. It is a fragmentary sectional view showing the whole hybrid drive unit composition concerning a first embodiment. It is principal part sectional drawing of the hybrid drive device which concerns on 1st embodiment. It is a perspective view of the 1st bearing with which the hybrid drive device concerning a first embodiment is equipped. It is principal part sectional drawing of the hybrid drive device which concerns on 2nd embodiment.

1. First Embodiment A first embodiment of the present invention will be described with reference to the drawings. In this embodiment, a case where the transmission according to the present invention is applied to a drive device 1 for a hybrid vehicle (hereinafter referred to as “hybrid drive device 1”) will be described as an example. The hybrid drive device 1 is a drive device for a hybrid vehicle that uses one or both of the internal combustion engine E and the rotating electrical machine MG as a drive force source of the vehicle. The hybrid drive device 1 is configured as a so-called 1-motor parallel type hybrid drive device.

  As shown in FIG. 1, the hybrid drive device 1 according to the present embodiment includes an input shaft I that is drivingly connected to the internal combustion engine E, an intermediate shaft M that is drivingly connected to the speed change mechanism TM, an input shaft I, and an intermediate shaft. The clutch CL is provided so as to be able to switch between transmission and disconnection of the driving force to and from the M, and the case 2 that accommodates the input shaft I, the intermediate shaft M, and the clutch CL. In such a configuration, the hybrid drive device 1 according to the present embodiment is characterized by the support structure in the axial direction of the clutch housing CH.

  That is, as shown in FIGS. 2 and 3, the hybrid drive device 1 is arranged on one side in the axial direction of the clutch CL and extends in the radial direction on one side radially extending portion 41 and on the other side in the axial direction of the clutch CL. A clutch housing CH that accommodates the clutch CL having the other radial extension portion 45 that is arranged and extends in the radial direction, and an axial extension portion 49 that is arranged on the outer side in the radial direction of the clutch CL and extends in the axial direction. I have. In addition, the input shaft I has a flange portion 11 that passes through the radially inner side of the one-side radial extending portion 41 and enters the clutch housing CH, and extends at least in the radial direction. On the premise of such a configuration, the input shaft I is supported by the intermediate shaft M from the other axial side through the first bearing 51 and the intermediate shaft M can be rotated by the case 2 from the other axial direction. Furthermore, the one side radial extending portion 41 is supported by the flange portion 11 from the other side in the axial direction via the second bearing 52. By combining these characteristic configurations, the hybrid drive device 1 that can appropriately support the clutch housing CH in the axial direction without increasing the weight of the entire device is realized. Below, the hybrid drive device 1 which concerns on this embodiment is demonstrated in detail.

1-1. Overall Configuration of Hybrid Drive Device First, the overall configuration of the hybrid drive device 1 according to the present embodiment will be described. As shown in FIG. 1, the hybrid drive device 1 includes an input shaft I that is drivingly connected to an internal combustion engine E as a first driving force source of a vehicle, and a rotating electrical machine MG as a second driving force source of the vehicle. A transmission mechanism TM, an intermediate shaft M drivingly connected to the rotating electrical machine MG and drivingly connected to the transmission mechanism TM, and an output shaft O drivingly connected to the wheels W. Further, the hybrid drive device 1 includes a clutch CL provided so as to be able to switch between transmission and disconnection of driving force between the input shaft I and the intermediate shaft M, a counter gear mechanism C, an output differential gear device DF, It has. Each of these components is accommodated in a case 2 as a drive device case. In the present embodiment, the input shaft I corresponds to the “first axis” in the present invention, and the intermediate shaft M corresponds to the “second axis” in the present invention.

  “Drive coupling” refers to a state where two rotating elements are coupled so as to be able to transmit a driving force, and the two rotating elements are coupled so as to rotate integrally, or the two rotating elements. Is used as a concept including a state in which a driving force can be transmitted through one or more transmission members. Examples of such a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like. Further, “driving force” is used synonymously with torque. The “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.

  The internal combustion engine E is a device that extracts power by being driven by combustion of fuel inside the engine. For example, various known engines such as a gasoline engine and a diesel engine can be used. In this example, an internal combustion engine output shaft Eo such as a crankshaft of the internal combustion engine E is drivingly connected to the input shaft I via a damper D. The input shaft I is drivingly connected to the rotating electrical machine MG and the intermediate shaft M via the clutch CL, and the input shaft I is selectively connected to the rotating electrical machine MG and the intermediate shaft M by the clutch CL. In the engaged state of the clutch CL, the internal combustion engine E and the rotary electric machine MG are drivingly connected via the input shaft I, and in the released state of the clutch CL, the internal combustion engine E and the rotary electric machine MG are separated.

  The rotating electrical machine MG includes a stator St and a rotor Ro, and functions as a motor (electric motor) that generates power by receiving power supply, and a generator (power generation) that generates power by receiving power supply. Function). Therefore, rotating electrical machine MG is electrically connected to a power storage device (not shown). In this example, a battery is used as the power storage device. Note that it is also preferable to use a capacitor or the like as the power storage device. The rotating electrical machine MG is powered by receiving electric power from the battery, or supplies the battery with electric power generated by the torque output from the internal combustion engine E or the inertial force of the vehicle. The rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the intermediate shaft M. The intermediate shaft M is an input shaft (transmission input shaft) of the speed change mechanism TM.

  The speed change mechanism TM is a device that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the speed change output gear G. In this embodiment, the transmission mechanism TM includes a single pinion type and Ravigneaux type planetary gear mechanism and a plurality of engagement devices such as a clutch, a brake, and a one-way clutch. An automatic transmission mechanism provided with a switchable gear is used. As the speed change mechanism TM, an automatic speed change mechanism having other specific configurations, an automatic continuously variable speed change mechanism capable of changing the speed ratio steplessly, and a plurality of speed stages having different speed ratios can be switched. A manual stepped transmission mechanism or the like may be used. The speed change mechanism TM changes the rotational speed of the intermediate shaft M at a predetermined speed change ratio at each time point, converts torque, and transmits the torque to the speed change output gear G.

  The counter gear mechanism C transmits the rotation and torque of the transmission output gear G to the wheel W side. The counter gear mechanism C has a counter shaft Cs, a first gear C1, and a second gear C2. The first gear C1 meshes with the transmission output gear G. The second gear C2 meshes with the differential input gear Di included in the output differential gear device DF. The differential gear device for output DF distributes the rotation and torque of the differential input gear Di to the plurality of wheels W and transmits them. In this example, the output differential gear device DF is a differential gear mechanism using a plurality of bevel gears meshing with each other, and is transmitted to the differential input gear Di via the second gear C2 of the counter gear mechanism C. Is distributed to the two left and right wheels W via the output shaft O, respectively. Thereby, the hybrid drive device 1 transmits the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the wheels W to cause the vehicle to travel.

  In the hybrid drive device 1 according to the present embodiment, the input shaft I and the intermediate shaft M are coaxially arranged, and the counter shaft Cs and the output shaft O are the input shaft I and the intermediate shaft M, respectively. They are arranged parallel to each other on different axes. Such a configuration is suitable as a configuration of the hybrid drive device 1 mounted on, for example, an FF (Front Engine Front Drive) vehicle.

1-2. Next, the configuration of each part of the hybrid drive device 1 according to this embodiment will be described. As shown in FIG. 2, the case 2 includes a case peripheral wall 3 that covers the outer periphery of each housing component such as a rotating electrical machine MG and a transmission mechanism TM housed therein, and one axial direction side of the case peripheral wall 3 (internal combustion engine). The first support wall 4 that closes the opening on the E side and the right side in FIG. 2 and the same applies to the other side in the axial direction of the case peripheral wall 3 (the opposite side to the internal combustion engine E and the left side in FIG. And an end support wall 9 for closing the end of the same. Further, the case 2 includes a second support wall 7 disposed between the rotary electric machine MG and the speed change mechanism TM in the axial direction.

  The first support wall 4 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. An axial through hole is formed in the first support wall 4, and an input shaft I inserted through the through hole is inserted into the case 2 through the first support wall 4. The first support wall 4 includes a cylindrical (boss-shaped) axial projecting portion 5 projecting to the other side in the axial direction. The axial protrusion 5 is formed integrally with the first support wall 4. In the present example, the first support wall 4 is located on the other axial side so that the radially inner portion is positioned on the other axial side with respect to the radially outer portion in the portion where the input shaft I is penetrated. It is set as the wall part which has the shape curved in the dish shape which becomes convex toward it. The first support wall 4 is arranged adjacent to the clutch housing CH at a predetermined interval on one side in the axial direction. Further, an oil passage forming member 71 having a discharge oil passage 72 (see FIG. 3) formed therein is attached to the first support wall 4 along the radial direction.

  The second support wall 7 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. A through hole in the axial direction is formed in the second support wall 7, and an intermediate shaft M inserted through the through hole passes through the second support wall 7. The second support wall 7 is disposed adjacent to the clutch housing CH at a predetermined interval on the other side in the axial direction. An oil pump 18 is accommodated in a pump chamber formed inside the second support wall 7. In the present embodiment, the oil pump 18 is an inscribed gear pump having an inner rotor and an outer rotor. The inner rotor of the oil pump 18 is drivingly connected (here, splined) so as to rotate integrally with the clutch housing CH at its radial center. As the clutch housing CH rotates, the oil pump 18 discharges oil and generates hydraulic pressure for supplying oil to the clutch CL, the speed change mechanism TM, and the like. Note that oil passages are respectively formed in the second support wall 7, the end support wall 9, the intermediate shaft M, and the like, and the oil discharged by the oil pump 18 is supplied to a hydraulic control device (not shown) and It distributes through these oil passages and is supplied to each part to be supplied with oil. In addition, the surface of the second support wall 7 on the one axial side (clutch housing CH side) is axially only around the portion where the oil passage is formed in order to reduce the weight while appropriately forming the oil passage. It is formed in an uneven shape in the axial direction so as to protrude to one side. In the present embodiment, the second support wall 7 corresponds to a “support wall portion” in the present invention.

  The end support wall 9 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. The end support wall 9 is not completely formed with an axial through hole and is completely closed. The end support wall 9 is a substantially plate-like wall portion that extends flat in the radial direction at a portion that intersects the virtual axis of the intermediate shaft M that extends to the end portion on the other axial side of the case 2.

  The input shaft I is a shaft for inputting the torque of the internal combustion engine E to the hybrid drive device 1, and is drivingly connected to the internal combustion engine E at one end in the axial direction as shown in FIG. Here, the input shaft I is disposed in a state of penetrating the first support wall 4, and is connected to the internal combustion engine output shaft Eo of the internal combustion engine E via the damper D on one axial side of the first support wall 4. Drive connected so as to rotate integrally. The damper D is a device that transmits the rotation of the internal combustion engine output shaft Eo to the input shaft I while attenuating torsional vibration of the internal combustion engine output shaft Eo, and various known devices can be used. In the present embodiment, the damper D has a plurality of coil springs arranged along the circumferential direction, and is fixed and integrated with a drive plate DP fixed to the internal combustion engine output shaft Eo. The input shaft I is splined. The damper D as a whole has a smaller diameter than the drive plate DP, and is disposed on the other axial side of the drive plate DP. Further, a third seal is formed across the input shaft I and the first support wall 4 to prevent leakage of oil to one side in the axial direction (the damper D and the internal combustion engine E side) with a liquid-tight state therebetween. A member 63 is disposed (see FIG. 3).

  In the present embodiment, a shaft end hole portion 12 extending in the axial direction is formed in the inner diameter portion of the other end portion in the axial direction of the input shaft I. A first bearing 51 is disposed in the shaft end hole portion 12, and an end portion on one side in the axial direction of the intermediate shaft M enters in the axial direction. Further, the input shaft I has a flange portion 11 extending radially from the input shaft I at the other end portion in the axial direction. The flange portion 11 is formed integrally with the input shaft I. As shown in FIG. 2, the flange portion 11 enters the clutch housing CH and is connected to the clutch hub 21 of the clutch CL accommodated in the clutch housing CH. A second bearing 52 is disposed on one axial side of the flange portion 11.

  The intermediate shaft M is a shaft for inputting one or both of the torque of the rotating electrical machine MG and the torque of the internal combustion engine E via the clutch CL to the transmission mechanism TM, and is splined to the clutch housing CH. As shown in FIG. 2, the intermediate shaft M is disposed so as to penetrate the second support wall 7. As described above, an axial through hole is formed at the radial center of the second support wall 7, and the intermediate shaft M passes through the second support wall 7 through the through hole. The intermediate shaft M is supported in the radial direction so as to be rotatable with respect to the second support wall 7. Further, one end of the intermediate shaft M in the axial direction is inserted into the shaft end hole 12 of the input shaft I in the axial direction, and a first bearing 51 disposed in the shaft end hole 12 is interposed. In contact with the input shaft I. The other axial end of the intermediate shaft M extends in the axial direction to the vicinity of the end support wall 9. In the present embodiment, the intermediate shaft M has a plurality of oil passages including a supply oil passage 15 and a discharge oil passage 16 on the inner diameter portion thereof. The supply oil passage 15 extends in the axial direction on one side in the axial direction of the intermediate shaft M and extends in the radial direction at a predetermined position in the axial direction so as to communicate with the hydraulic oil chamber 37 of the clutch CL. Is open. The drain oil passage 16 extends in the axial direction at a position different from the supply oil passage 15 in the axial direction on one side of the intermediate shaft M, and opens to the end surface on the one axial side. In the present embodiment, the discharged oil passage 16 corresponds to an “in-shaft oil passage” in the present invention.

  Here, in the present embodiment, a thrust washer capable of receiving an axial load (thrust force) is used as the first bearing 51. As the material constituting the first bearing 51, for example, a metal material such as high carbon chrome or the like, a resin material such as tetrafluoroethylene resin (PTFE), or the like having an excellent sliding property and wear resistance is arbitrarily adopted. can do. In the present embodiment, as shown in FIG. 4, the first bearing 51 is formed in an annular plate shape, and the radial groove 66 that communicates between the outer peripheral surface 51 a and the inner peripheral surface 51 b in the radial direction. Have In this example, the first bearing 51 is formed using a single member. As shown in FIG. 4 (a), four radial grooves 66a having a concave shape and extending in the radial direction are formed on one surface of the single annular plate member. It is formed evenly distributed in the direction. Further, as shown in FIG. 4B, four radial grooves 66b having a concave shape and extending in the radial direction are evenly provided in the circumferential direction on the other surface of the annular plate member. Distributed and formed. At this time, a total of eight radial grooves 66 including the radial grooves 66a on one surface and the radial grooves 66b on the other surface are uniformly distributed in the circumferential direction. Further, in the present embodiment, the outer peripheral surface 51a at the circumferential position where a total of eight radial grooves 66 of a single annular plate-like member are formed has a concavely recessed shape in the axial direction. Eight axial grooves 67 are formed. In the present embodiment, the radial groove 66 corresponds to the “communication portion” in the present invention.

  As described above, the clutch CL is provided so as to be able to switch between transmission and disconnection of the driving force between the input shaft I and the intermediate shaft M, and selectively engages and connects the internal combustion engine E and the rotating electrical machine MG. It is. In the present embodiment, the clutch CL is configured as a wet multi-plate clutch mechanism. As shown in FIG. 3, the clutch CL includes a clutch hub 21, a clutch drum 26, a plurality of friction plates 31, and a piston 36. The clutch hub 21 is coupled to the flange portion 11 of the input shaft I so as to rotate integrally with the input shaft I. The clutch drum 26 is connected so as to rotate integrally with the intermediate shaft M via the clutch housing CH. In this embodiment, the clutch drum 26 has a cylindrical shape and is formed integrally with the clutch housing CH. The friction plate 31 includes a hub-side friction plate and a drum-side friction plate that form a pair. The hub-side friction plate is supported from the inside in the radial direction by the clutch hub 21, and relative rotation with respect to the clutch hub 21 is restricted and slidable in the axial direction. The drum-side friction plate is supported by the clutch drum 26 from the outside in the radial direction, and relative rotation with respect to the clutch drum 26 is restricted and slidable in the axial direction. The hub side friction plate and the drum side friction plate are alternately arranged in the axial direction. A backing plate 32 that functions as a pressing member when the friction plates 31 are engaged with each other is held on one axial side of all the friction plates 31. The backing plate 32 is held in a state in which movement in the axial direction is restricted by a snap ring. The piston 36 is disposed on the other axial side with respect to the plurality of friction plates 31 in a state of being biased to the other axial side by a return spring.

  In the present embodiment, a fluid-tight hydraulic oil chamber 37 is formed between the clutch housing CH integrated with the clutch drum 26 and the piston 36. In the hydraulic oil chamber 37, pressure oil discharged by the oil pump 18 and adjusted to a predetermined hydraulic pressure by a hydraulic control device (not shown) is formed in the supply oil passage 15 formed in the intermediate shaft M and the clutch housing CH. Supplied through the connecting oil passage 48. When the hydraulic pressure in the hydraulic oil chamber 37 rises and becomes greater than the urging force of the return spring, the piston 36 moves in a direction to expand the volume of the hydraulic oil chamber 37 (in this example, one side in the axial direction), and the backing plate 32. The plurality of friction plates 31 are engaged with each other in cooperation with the. As a result, the torque of the internal combustion engine E transmitted from the input shaft I is transmitted to the rotating electrical machine MG and the intermediate shaft M via the clutch CL. On the other hand, a circulating oil chamber 38 is formed on the opposite side of the piston 36 from the hydraulic oil chamber 37. The circulating oil chamber 38 is supplied with pressure oil discharged by the oil pump 18 and adjusted to a predetermined hydraulic pressure by a hydraulic control device (not shown) via a circulating oil passage 47 formed in the clutch housing CH. .

  The hybrid drive device 1 according to the present embodiment further includes a clutch housing CH that houses the clutch CL. The clutch housing CH is disposed across the input shaft I and the intermediate shaft M in a state of rotating relative to the input shaft I and rotating integrally with the intermediate shaft M. The clutch housing CH encloses both sides of the clutch CL in the axial direction and radially outside of the input shaft I and the intermediate shaft M arranged coaxially and accommodates the clutch CL. Therefore, the clutch housing CH is disposed on one side in the axial direction of the clutch CL and extends in the radial direction on one side, and the other side diameter extends in the radial direction on the other side in the axial direction of the clutch CL. A direction extending portion 45 and an axially extending portion 49 that is disposed on the radially outer side of the clutch CL and extends in the axial direction are configured.

  On the other hand, the side radial direction extending portion 41 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. An axial through hole is formed at the radial center of the one side radial extending portion 41, and the input shaft I inserted through the through hole penetrates the one side radial extending portion 41 to engage the clutch. It is inserted in the housing CH. The one-side radial extending portion 41 includes a cylindrical (boss-shaped) axial protruding portion 42 that protrudes to the one axial side around the input shaft I. A sixth bearing 56 is disposed between the axial protrusion 42 and the input shaft I. The axial projecting portion 42 is formed integrally with the one side radial extending portion 41. In this example, the one-side radially extending portion 41 is a dish that is convex toward the other side in the axial direction so that the radially inner portion is located on the other side in the axial direction relative to the radially outer portion as a whole. The member has a curved shape. The one side radially extending portion 41 is adjacent to the first support wall 4 at a predetermined interval on the other side in the axial direction, and the axial protrusion 42 is connected to the axial protrusion 5 of the first support wall 4. On the other hand, they are arranged in a state adjacent to each other at a predetermined interval on the radially inner side. Further, the one-side radial extending portion 41 is disposed adjacent to the clutch hub 21 and the flange portion 11 of the input shaft I at a predetermined interval on one side in the axial direction. In addition, the fifth bearing 55 extends between the axial protrusion 42 and the axial protrusion 5 of the first support wall 4, and the space between them is in a liquid-tight state toward the other axial side (the rotating electrical machine MG side). A first seal member 61 for suppressing oil leakage is disposed.

  The axially extending portion 49 has a shape extending at least in the axial direction, and in the present embodiment, extends in the axial direction and the circumferential direction. The axially extending portion 49 connects the one side radially extending portion 41 and the other side radially extending portion 45 in the axial direction at these radially outer ends. The axially extending portion 49 has a cylindrical shape that surrounds the radially outer side of the clutch CL, and in the present embodiment, from the radially outer end of the one side radially extending portion 41 to the other side in the axial direction. Extends towards. In this example, the axially extending portion 49 is formed integrally with the one side radial extending portion 41.

  The other-side radial extending portion 45 has a shape extending at least in the radial direction, and extends in the radial direction and the circumferential direction in the present embodiment. In this example, the other-side radial extending portion 45 is a plate-like member having a generally flat shape in the radial direction as a whole. The other-side radial extending portion 45 is connected to a portion on the other axial side of the axial extending portion 49 in the vicinity of the radially outer end portion by welding or the like. An axial through hole is formed in the radial center of the other side radially extending portion 45, and the intermediate shaft M inserted through this through hole penetrates the other side radially extending portion 45 to engage the clutch. It is inserted in the housing CH. The other side radially extending portion 45 has an inner peripheral surface in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction at the radially inner end. The other-side radially extending portion 45 includes a cylindrical (boss-shaped) axial protruding portion 46 that protrudes to the other axial side around the intermediate shaft M. The axial protrusion 46 is coupled to rotate integrally with the intermediate shaft M. In this example, an inner spline groove extending in the axial direction is formed on the inner peripheral surface of the other axial end of the axial protrusion 46, and an outer spline groove extending in the axial direction on the outer peripheral surface of the intermediate shaft M. Is formed, and the axially projecting portion 46 of the other side radially extending portion 45 located at the end of the other side in the axial direction of the clutch housing CH is in a state in which it can be displaced relative to the intermediate shaft M in the axial direction. Are connected by spline. The other-side radial extending portion 45 is disposed adjacent to the second support wall 7 at a predetermined interval on one side in the axial direction. Further, the other-side radial extending portion 45 is disposed adjacent to the flange portion 11 of the input shaft I at the other side in the axial direction at a predetermined interval in a radially inner portion. Further, the second seal member for suppressing oil leakage to the one axial side (rotating electrical machine MG side) between the axial projecting portion 46 and the second support wall 7 in a liquid-tight state therebetween. 62 is disposed.

  In the present embodiment, the clutch drum 26 is formed integrally with the other-side radial extending portion 45. More specifically, in the vicinity of the radially outer end portion of the other-side radial extending portion 45, the cylindrical clutch extends from the other-side radial extending portion 45 toward one side in the axial direction. The drum 26 is integrally formed. At this time, the clutch drum 26 is disposed radially inward of the axially extending portion 49 and adjacent to the axially extending portion 49 at a predetermined interval in the radial direction. A gap formed between the clutch drum 26 and the axially extending portion 49 opens in the axial direction at one axial end portion in the clutch housing CH. In the present embodiment, a hydraulic oil chamber 37 is formed between the other-side radial extending portion 45 and the piston 36. Further, a communication oil passage 48 extending in the radial direction is formed in the other-side radial extending portion 45 so as to communicate the supply oil passage 15 and the hydraulic oil chamber 37.

  Of the space formed inside the clutch housing CH, the space that occupies most of the space excluding the hydraulic oil chamber 37 is the circulating oil chamber 38 described above. In this embodiment, the oil discharged from the oil pump 18 and adjusted to a predetermined oil pressure is circulated through the circulation oil passage 47 formed so as to extend in the axial direction in the axial protrusion 46. It is supplied to the chamber 38. The oil supply flow rate at this time is much larger than the supply flow rate when oil leaks from between predetermined members of the clutch CL as described in the background art section. Further, in the present embodiment, the sixth bearing 56 disposed between the axial projecting portion 42 and the input shaft I is a bearing with a sealing function configured to ensure a certain degree of liquid tightness (here, Needle bearing with seal ring). Furthermore, the inner peripheral surface of the other-side radially extending portion 45 is in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction at the radially inner end. Therefore, when oil is supplied to the circulating oil chamber 38 via the circulating oil passage 47, the circulating oil chamber 38 in the clutch housing CH is basically always filled with oil. Thereby, in the hybrid drive device 1 according to the present embodiment, the plurality of friction plates 31 provided in the clutch CL can be effectively cooled with a large amount of oil that is always filled in the circulating oil chamber 38. . In the present embodiment, the circulating oil chamber 38 corresponds to the “oil chamber” in the present invention.

  Basically, the oil circulates in the circulating oil chamber 38 while maintaining a state always filled with oil. This oil flow is indicated by broken-line arrows in FIG. That is, the oil supplied to the circulating oil chamber 38 from the circulating oil passage 47 first passes between the other side radial extending portion 45 and the flange portion 11 and between the piston 36 and the clutch hub 21 in the radial direction. It flows toward the outside and reaches the plurality of friction plates 31. Next, the oil flows in the axial direction through gaps or the like of the plurality of friction plates 31, and then passes between the clutch hub 21 and the flange portion 11 and the one side radial extending portion 41 to the inside in the radial direction. Flows toward the base end of the flange 11. Thereafter, the oil is discharged from the circulating oil chamber 38. It should be noted that the oil may flow in the circumferential direction at the same time, but the main flows in the radial direction and the axial direction are as described above.

  In this example, the oil discharge path from the circulating oil chamber 38 is divided into two systems. The first discharge path is through a radial communication hole opened on the outer peripheral surface of the input shaft I and a discharge oil path 16 formed in the inner diameter portion of the intermediate shaft M. In the present embodiment, a first bearing 51 formed in an annular plate shape is disposed between the input shaft I and the intermediate shaft M. The first bearing 51 extends in the radial direction and the axial direction, respectively. A plurality of radial grooves 66 and axial grooves 67 are formed (see FIG. 4). Further, the outer diameter of the end portion on one side in the axial direction of the intermediate shaft M is formed to be slightly smaller than the inner diameter of the shaft end hole portion 12 of the input shaft I. Thereby, the oil discharged from the circulating oil chamber 38 through the radial communication hole formed in the input shaft I is separated from the outer peripheral surface of the intermediate shaft M and the inner peripheral surface of the shaft end hole portion 12 of the input shaft I. And a plurality of radial grooves 66 and axial grooves 67 can be appropriately guided to the drain oil passage 16. The second discharge path is intended for oil leaking in the axial direction from the sixth bearing 56, and passes through the discharge oil path 72 inside the oil path forming member 71 attached to the first support wall 4. Such a second discharge path includes the third seal member 63 disposed between the input shaft I and the first support wall 4, the axial protrusion 42 of the one-side radial extension 41, and the first It is demarcated by the 1st seal member 61 arrange | positioned between the axial direction protrusion parts 5 of the one support wall 4. FIG. Thereby, the oil leaking in the axial direction from the sixth bearing 56 can be appropriately guided to the drain oil passage 72.

  As shown in FIG. 2, the rotating electrical machine MG is disposed on the radially outer side of the clutch housing CH. The rotating electrical machine MG includes a stator St fixed to the case 2 and a rotor Ro that is rotatably supported on the radially inner side of the stator St. The stator St includes a stator core that is configured as a laminated structure in which a plurality of annular plate-shaped electromagnetic steel plates are stacked and is fixed to the first support wall 4, and a coil that is wound around the stator core. In addition, the part which protrudes in the axial direction both sides of a stator core among coils is the coil end part Ce. The rotor Ro of the rotating electrical machine MG includes a rotor core configured as a laminated structure in which a plurality of annular plate-shaped electromagnetic steel plates are stacked, and a permanent magnet embedded in the rotor core.

  In the present embodiment, the rotating electrical machine MG is disposed so as to overlap the clutch housing CH in the axial direction. Regarding the arrangement of the two members (here, the rotary electric machine MG and the clutch housing CH), “overlap” in the axial direction means that at least a part where the two members are at the same position with respect to the arrangement in the axial direction. It means having. In this case, the rotating electrical machine MG is disposed so as to overlap the clutch housing CH when viewed from the radial direction. Particularly in this example, the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the axially extending portion 49 constituting the clutch housing CH. That is, the inner peripheral surfaces of the plurality of electromagnetic steel plates constituting the rotor Ro are fixed in contact with the outer peripheral surface of the axially extending portion 49. As a result, the clutch housing CH also functions as a rotor support member that supports the rotor Ro, and in this embodiment, the clutch housing CH and the rotor support member are formed in common.

  In the present embodiment, the rotation sensor 19 is provided adjacent to both the second support wall 7 of the case 2 and the other-side radial extending portion 45 on the other axial side of the clutch housing CH. The rotation sensor 19 is a sensor for detecting the rotation phase of the rotor Ro relative to the stator St of the rotating electrical machine MG. In the present embodiment, the rotation sensor 19 is disposed on the radially outer side of the oil pump 18 accommodated in the second support wall 7 so as to overlap the oil pump 18 in the axial direction. That is, the rotation sensor 19 is disposed so as to overlap with the oil pump 18 when viewed from the radial direction. In this example, the sensor stator of the rotation sensor 19 is fixed to the second support wall 7, and the sensor rotor of the rotation sensor 19 is fixed to the inner peripheral surface of the other axial end portion of the axial extension portion 49. As such a rotation sensor 19, a resolver etc. can be used, for example.

  In the present embodiment, the first support wall 4 formed in a dish-like shape that is convex toward the other side in the axial direction is on the other side in the axial direction when viewed from one side in the axial direction. A damper D is disposed in the retired space. In the present example, the damper D is further arranged in the radial direction inside the coil end portion Ce of the stator St of the rotating electrical machine MG so as to overlap the coil end portion Ce in the axial direction. That is, the damper D is disposed so as to overlap with the coil end portion Ce as viewed from the radial direction.

1-3. Next, the support structure in the axial direction of the clutch housing CH according to the present embodiment will be described. In the present embodiment, the clutch housing CH is rotatably supported on the first support wall 4 of the case 2 on one side in the axial direction, and the case on the other side in the axial direction via the input shaft I and the intermediate shaft M. The two end support walls 9 are supported in a rotatable state. Details will be described below.

  As shown in FIGS. 2 and 3, the one side radial extending portion 41 constituting the clutch housing CH includes an axial protrusion 42 formed integrally with the one side radial extending portion 41. The axial projecting portion 42 is disposed adjacent to the axial projecting portion 5 of the first support wall 4 at a predetermined interval radially inward. A stepped portion 43 in the axial direction is formed on the outer peripheral surface of the axial protruding portion 42. Here, the “stepped portion in the axial direction” on the outer peripheral surface is a portion formed at a predetermined position in the axial direction of the axial protruding portion 42 where the outer diameter of the axial protruding portion 42 changes. In the present embodiment, the axial protrusion 42 is formed to have an axial stepped shape such that a portion on one side in the axial direction has a smaller diameter than a portion on the other side in the axial direction than the stepped portion 43. ing. And between the outer peripheral surface of the small diameter part of the axial direction protrusion part 42 and the inner peripheral surface of the axial direction protrusion part 5 of the 1st support wall 4 in the state contact | abutted from the axial direction one side with respect to the level | step difference part 43. A fifth bearing 55 is provided. In this example, a ball bearing capable of receiving both an axial load and a radial load is used as the fifth bearing 55. The fifth bearing 55 is also in contact with the other surface of the first support wall 4 in the axial direction. Accordingly, the one-side radial extending portion 41 constituting the clutch housing CH is supported by the first support wall 4 in the axial direction and the radial direction so as to be rotatable via the fifth bearing 55. Here, in particular, the one side radially extending portion 41 is supported by the first support wall 4 in the axial direction from one side in the axial direction.

  As shown in FIG. 2, the other axial end of the intermediate shaft M extends in the axial direction to the vicinity of the end support wall 9. The intermediate shaft M has a flange portion 13 connected to the intermediate shaft M and extending at least in the radial direction at the other axial end portion. A fourth bearing 54 is disposed between the intermediate shaft M in contact with both the surface on the other axial side of the flange portion 13 and the surface on the one axial side of the end support wall 9. Yes. In this example, a thrust bearing capable of receiving an axial load is used as the fourth bearing 54. Thus, the intermediate shaft M is supported in the axial direction by the end support wall 9 so as to be rotatable via the fourth bearing 54. Here, in particular, the intermediate shaft M is supported by the end support wall 9 in the axial direction from the other side in the axial direction. Although a detailed description is omitted here, in this example, the intermediate shaft M is configured as a composite of a plurality of shaft portions, and a bearing (here, a thrust bearing) is also provided between the plurality of shaft portions. Are appropriately disposed. In this way, the entire intermediate shaft M is supported by the end support wall 9 in the axial direction from the other side in the axial direction via the fourth bearing 54.

  As shown in FIGS. 2 and 3, the end portion on the one axial side of the intermediate shaft M is inserted into the shaft end hole portion 12 of the input shaft I in the axial direction. The first bearing 51 is disposed between the intermediate shaft M in contact with both the axial end surface of the intermediate shaft M and the surface defining the axial bottom of the shaft end hole 12 of the input shaft I. Has been. In the present embodiment, a thrust washer capable of receiving an axial load is used as the first bearing 51. Thus, the input shaft I is supported in the axial direction by the intermediate shaft M so as to be rotatable via the first bearing 51. Here, in particular, the input shaft I is supported by the intermediate shaft M in the axial direction from the other side in the axial direction. Accordingly, the input shaft I is supported in the axial direction from the other axial side by the end support wall 9 via the first bearing 51, the intermediate shaft M, and the fourth bearing 54.

  As shown in FIGS. 2 and 3, the input shaft I enters the clutch housing CH through the radially inner side of the one side radially extending portion 41, and the input shaft I is connected to the other end portion in the axial direction. And a flange portion 11 extending in the radial direction. Further, the one-side radial extending portion 41 constituting the clutch housing CH is disposed adjacent to the flange portion 11 at a predetermined interval on the one axial side. A second bearing 52 is disposed between the flange 11 in contact with both the surface on the one axial side of the flange portion 11 and the surface on the other axial side of the one-side radial extending portion 41. . In this example, as such a second bearing 52, a thrust bearing capable of receiving an axial load is used. Thereby, the one side radial direction extension part 41 is supported by the flange part 11 integrally formed with the input shaft I in the axial direction in the state which can rotate via the 2nd bearing 52. Here, in particular, the one side radially extending portion 41 is supported by the flange portion 11 in the axial direction from the other side in the axial direction. Therefore, the one side radial direction extending portion 41 is end-supported via the second bearing 52, the flange portion 11 formed integrally with the input shaft I, the first bearing 51, the intermediate shaft M, and the fourth bearing 54. It is supported by the wall 9 in the axial direction from the other side in the axial direction.

  Thus, in the present embodiment, the one-side radial extending portion 41 constituting the clutch housing CH is supported in the axial direction from the one axial side by the first support wall 4 via the fifth bearing 55. Along with the second bearing 52, the flange portion 11 formed integrally with the input shaft I, the first bearing 51, the intermediate shaft M, and the fourth bearing 54, the axial direction from the other axial side by the end support wall 9. It is supported by. That is, the axial support of the clutch housing CH is realized only by supporting the one side radially extending portion 41 from both sides in the axial direction by the first support wall 4 and the end support wall 9 constituting the case 2. Yes. In other words, the axial support of the clutch housing CH is realized without particularly supporting the other-side radial extending portion 45 constituting another part of the clutch housing CH in the axial direction.

  Therefore, in the present embodiment, the other-side radial extending portion 45 extends from the second support wall 7 on the other side in the axial direction without any other member such as a bearing between the second support wall 7. They are arranged at predetermined intervals in the axial direction. In this embodiment, as described above, the circulating oil chamber 38 formed in the clutch housing CH is basically always filled with oil so as to effectively cool the friction plate 31 of the clutch CL. It has become. For this reason, when the vehicle in which the clutch housing CH rotates integrally with the intermediate shaft M is traveling normally, a so-called ballooning phenomenon may occur. That is, there is a possibility that centrifugal force acts on the oil filled in the circulating oil chamber 38 and the clutch housing CH is elastically deformed so as to expand in the axial direction due to the influence. Even in this case, in the present embodiment, the other-side radial extending portion 45 is spline-connected in a state in which the other-side radially extending portion 45 can be relatively displaced in the axial direction with respect to the intermediate shaft M, and the other-side radial extending portion 45. Is disposed at a predetermined interval from the second support wall 7 in the axial direction, so that a ballooning phenomenon actually occurs and the clutch housing CH is deformed in the axial direction (here, the other-side radial extending portion 45 is Even if it moves to the other side in the axial direction), the other side radial extending portion 45 can be suppressed from pressing the second support wall 7 in the axial direction.

  Here, in the present embodiment, the axial separation distance L between the other-side radial extending portion 45 and the second support wall 7 is a circulation formed inside the clutch housing CH when it rotates. The distance (here, “ballooning” in which the clutch housing CH can be deformed and the other side radially extending portion 45 can move toward the other side in the axial direction due to the influence of the centrifugal force acting on the oil filled in the oil chamber 38. It is set to a value larger than the maximum value of “the amount of displacement”. Note that such a maximum value of the ballooning displacement amount is acquired as an experimental value obtained experimentally. In this way, even if the ballooning phenomenon actually occurs by arranging the other radial extending portion 45 at a distance L longer than the ballooning displacement amount in the axial direction from the second support wall 7, It is possible to prevent the laterally extending portion 45 from coming into contact with the second support wall 7 and further pressing the second support wall 7 in the axial direction.

  Furthermore, in the present embodiment, the axial separation distance L between the other-side radial extending portion 45 and the second support wall 7 is the maximum value of the ballooning displacement amount and the intermediate shaft M with respect to the case 2. It is set to a value larger than the sum of the total values of the support clearances of a plurality of bearings (including at least the fourth bearing 54) provided to support them. The “bearing support clearance” is a clearance required for two members arranged on both sides in the support direction of the bearing to be supported in a relatively rotatable state, and is determined by the specifications of each bearing. In this manner, the other radial extending portion 45 is disposed with a separation distance L longer than the sum of the ballooning displacement amount and the total value of the support clearances of the plurality of bearings in the axial direction from the second support wall 7. Thus, even if the ballooning phenomenon actually occurs in a state where the support clearances of the respective bearings are all clogged, it is possible to prevent the other-side radial extending portion 45 from pressing the second support wall 7 in the axial direction. . Therefore, in consideration of the support clearance of each bearing, the oil pump 18 accommodated in the second support wall 7 is prevented from being pressed, and the rotation efficiency of the oil pump 18 is almost certainly prevented from being lowered. can do.

  In the present embodiment, the other-side radial extending portion 45 extends from the flange portion 11 without interposing any other member such as a bearing between the input shaft I and the flange portion 11 even on one axial side thereof. They are arranged at predetermined intervals in the axial direction. Therefore, in the present embodiment, the other-side radial extending portion 45 is splined to the intermediate shaft M in a state where it is not supported at all in the axial direction. In such a configuration, as compared with the case where other members such as a bearing are disposed between the other-side radial extending portion 45 and the flange portion 11, as much as such other members are omitted, There is an advantage that the axial length of the hybrid drive device 1 can be shortened and the manufacturing cost can be reduced.

2. Second Embodiment A second embodiment of the present invention will be described with reference to the drawings. Also in this embodiment, the case where the transmission according to the present invention is applied to the hybrid drive device 1 will be described as an example. The overall configuration and the configuration of each part of the hybrid drive device 1 according to this embodiment are basically the same as those of the first embodiment. However, in the present embodiment, the support structure in the axial direction of the other-side radial extending portion 45 is partially different from that in the first embodiment. Note that points not particularly specified are the same as those in the first embodiment.

  In the present embodiment, as shown in FIG. 5, the other-side radial extending portion 45 is arranged between the flange portion 11 of the input shaft I via a third bearing 53 on one axial direction side. It is installed. That is, the third bearing 53 is arranged between the axially extending one side surface of the other radial extending portion 45 and the axially other side surface of the flange portion 11 of the input shaft I. It is installed. In this example, a thrust bearing capable of receiving an axial load is used as the third bearing 53 like the second bearing 52. Thereby, in this embodiment, the other side radial direction extension part 45 is an axial direction in the state which can be rotated via the 3rd bearing 53 by the flange part 11 on the other axial direction side of the flange part 11 of the input shaft I. It will be supported by. Here, in particular, the other-side radially extending portion 45 is supported by the flange portion 11 in the axial direction from one axial direction.

  Here, as shown in FIG. 5, the third bearing 53 is a cylindrical (boss-shaped) axial projecting portion formed so as to project from the other-side radial extending portion 45 to the one axial side. It is fitted and arranged on the peripheral surface. As a result, the third bearing 53 is positioned in the radial direction. By providing such a third bearing 53, the other-side radial extending portion 45 and the flange portion 11 can be appropriately and smoothly relatively rotated.

  Also in the present embodiment, the other-side radial extending portion 45 is spline-connected in a state in which it can be relatively displaced in the axial direction with respect to the intermediate shaft M on the other side in the axial direction, and also in the other-side radial direction. The extending portion 45 is disposed with a separation distance L longer than the ballooning displacement amount in the axial direction from the second support wall 7. Therefore, even if the ballooning phenomenon actually occurs and the other-side radial extending portion 45 moves to the other axial side, the other-side radial extending portion 45 abuts against the second support wall 7 and further It is possible to prevent the two support walls 7 from being pressed in the axial direction. Therefore, it is possible to prevent the oil pump 18 accommodated in the second support wall 7 from being pressed and to prevent the rotation efficiency of the oil pump 18 from being lowered.

[Other Embodiments]
Finally, other embodiments of the transmission according to the present invention will be described. Note that the feature configurations disclosed in each of the following embodiments are not applied only in that embodiment, and should be applied in combination with the feature configurations disclosed in the other embodiments unless a contradiction arises. Is also possible.

(1) In each of the above-described embodiments, the other-side radial extending portion 45 is not connected to the second support wall 7 on the other side in the axial direction without interposing other members such as a bearing. The case where it arrange | positions at predetermined intervals in the axial direction from the support wall 7 was demonstrated as an example. However, the embodiment of the present invention is not limited to this. That is, it is also one preferred embodiment of the present invention that another member is disposed so as to be interposed between the other-side radial extending portion 45 and the second support wall 7 in the axial direction. It is. In this case, the “other member” is configured to be arranged at a predetermined interval in the axial direction without contacting at least one of the other-side radial extending portion 45 and the second support wall 7. The In this case, the separation distance between the other-side radial extending portion 45 and the second support wall 7 is a plurality of values provided to support the maximum value of the ballooning displacement amount and the intermediate shaft M with respect to the case 2. It is preferable that the value is set to a value larger than the sum of the total value of the bearing clearances of the other bearings and the axial length of the “other member”.

(2) In each of the above embodiments, the case where the circulating oil chamber 38 is formed in the clutch housing CH and the circulating oil chamber 38 is filled with oil has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, in the case where the circulating oil chamber 38 is formed in the clutch housing CH, the circulating oil chamber 38 is not filled with oil, and the oil may be stored only partially. This is one of the preferred embodiments. It is also a preferred embodiment of the present invention that no oil is contained in the clutch housing CH and the circulating oil chamber 38 is not formed. In such a configuration, it is not necessary to consider the influence of ballooning as in the above embodiments, but it is possible to reduce the weight of the second support wall 7 that accommodates at least the oil pump 18, and the entire apparatus. The clutch housing CH can be appropriately supported in the axial direction without increasing the weight of the clutch.

(3) In each of the above-described embodiments, the axial separation distance L between the other-side radial extending portion 45 and the second support wall 7 is the maximum value of the ballooning displacement amount and the intermediate shaft M is the case. As an example, the case where the value is set to a value larger than the sum of the support clearances of the plurality of bearings provided to support 2 is described. However, the embodiment of the present invention is not limited to this. That is, for example, when the support clearance of each bearing is small enough to be ignored, the axial separation distance L between the other-side radial extending portion 45 and the second support wall 7 is not considered. May be set to a value at least larger than the maximum value of the ballooning displacement. Further, for example, when the third bearing 53 is disposed between the other-side radial extending portion 45 and the flange portion 11 as in the second embodiment, the third bearing 53 is fitted between them. In the case of being combined, the occurrence of ballooning phenomenon can be suppressed by the sliding resistance in the fitting portion between the third bearing 53 and the other-side radial extending portion 45 and the flange portion 11, It is also possible to adopt a configuration in which the axial separation distance L between the other radial extending portion 45 and the second support wall 7 is set to a value smaller than the maximum value of the ballooning displacement amount. In this case, the “maximum value of the ballooning displacement amount” is a state in which the other-side radially extending portion 45 is not supported in the axial direction as in the first embodiment without using the third bearing 53. It shall be experimentally obtained.

(4) In each of the above embodiments, the second support wall 7 of the case 2 that houses the oil pump 18 is disposed at a predetermined interval on the other side in the axial direction with respect to the clutch housing CH. The case has been described as an example. However, the embodiment of the present invention is not limited to this. That is, not the second support wall 7 that accommodates the oil pump 18 therein, but other components such as a clutch and a gear constituting the hybrid drive device 1 are spaced apart from each other in the axial direction with respect to the clutch housing CH by a predetermined distance. It is also one of the preferred embodiments of the present invention to have a configuration in which a gap is provided. Even in this case, even if a ballooning phenomenon occurs, it is possible to prevent the other-side radial extending portion 45 of the clutch housing CH from pressing the “other components” in the axial direction. Therefore, it is possible to suppress the influence on “other components” due to the ballooning phenomenon.

(5) In each of the above embodiments, the first bearing 51 is formed in an annular plate shape using a single member, and the concave shape is formed on both sides of the annular plate member. The case where the radial grooves 66a and 66b having the radial direction and extending in the radial direction are formed has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the first bearing 51 is one of the surfaces of the annular plate member (here, the surface on the other side in the axial direction that is the intermediate shaft M side in the state of being disposed in the shaft end hole portion 12). It is also possible to adopt a configuration having a radial groove 66 formed only in the shape of a ring-shaped plate member or a configuration having a radial communication hole formed in the annular plate-like member in the radial direction. One of the forms. In addition, it is also preferable that the first bearing 51 is configured by combining a plurality of members so as to have a form having the radial grooves 66 (66a, 66b) and the radial communication holes described above. This is one of the embodiments.

(6) In each of the above embodiments, the drain oil passage 16 constituting one of the oil discharge passages from the circulating oil chamber 38 is formed in the inner diameter portion of the intermediate shaft M, and the annular plate The case where the radial groove 66 communicating between the outer peripheral surface 51a and the inner peripheral surface 51b in the radial direction is formed in the first bearing 51 formed in the shape has been described as an example. However, the embodiment of the present invention is not limited to this. That is, it is also one of the preferred embodiments of the present invention that the intermediate shaft M has a configuration in which the drain oil passage 16 is not provided in the inner diameter portion thereof. In this case, the first bearing 51 does not have to be formed with the radial groove 66 that communicates between the outer peripheral surface 51a and the inner peripheral surface 51b in the radial direction. In this case, the oil discharge path from the circulating oil chamber 38 is only one system via the discharge oil path 72 inside the oil path forming member 71 attached to the first support wall 4.

(7) In each of the above embodiments, a thrust washer is used as the first bearing 51, and a thrust bearing is used as the second bearing 52, the third bearing 53 (only the second embodiment), and the fourth bearing 54. The case where there was was demonstrated as an example. However, the embodiment of the present invention is not limited to this. That is, each of these bearings only needs to be a bearing capable of receiving at least an axial load. For example, a thrust bearing is used as the first bearing 51, and the second bearing 52, the third bearing 53, and the fourth bearing are used. Adopting a configuration using a thrust washer as any one or more of the bearings 54 is also a preferred embodiment of the present invention.

(8) In each of the above embodiments, the intermediate shaft M is configured as a composite of a plurality of shaft portions that are connected to each other via a bearing (here, a thrust bearing), and includes a plurality of fourth bearings 54. The case where the axial separation distance L between the other side radial extending portion 45 and the second support wall 7 is set in consideration of the support clearance of the thrust bearing has been described as an example. However, the embodiment of the present invention is not limited to this. That is, it is one of the preferred embodiments of the present invention that the intermediate shaft M is configured as a single shaft portion. In this case, when setting the axial separation distance L between the other-side radial extending portion 45 and the second support wall 7, when considering the support clearance of the bearing, the support of the fourth bearing 54 is used. Only the clearance needs to be considered.
In both cases where the intermediate shaft M is configured as a composite of a plurality of shaft portions and when configured as a single shaft portion, the intermediate shaft M is further axially moved by the case 2 via another shaft. It is also one of the preferred embodiments of the present invention that the structure is supported in a rotatable state from the other side. Such a configuration is suitable for a hybrid drive device mounted on an FR (Front Engine Rear Drive) vehicle in which an output shaft as an “other shaft” is arranged coaxially with the input shaft I and the intermediate shaft M, for example. It becomes. In this case, when setting the axial separation distance L between the other-side radial extending portion 45 and the second support wall 7, the intermediate shaft M and “ It is preferable to take into consideration the total value of the support clearances of a plurality of bearings provided to support the shaft “of the shaft” with respect to the case 2.

(9) In each of the above embodiments, the other axial end of the intermediate shaft M extends in the axial direction to the vicinity of the end support wall 9, and the intermediate shaft M is rotated by the end support wall 9. The case where it is supported in the axial direction in a possible state has been described as an example. However, the embodiment of the present invention is not limited to this. That is, for example, the case 2 is configured to include another wall portion between the end support wall 9 and the second support wall 7 in the axial direction, and the intermediate shaft M can be rotated with the “other wall portion” being rotatable. It is one of the preferred embodiments of the present invention that the structure is supported in the direction.

(10) In each of the above embodiments, the clutch hub 21 is drivingly connected so as to rotate integrally with the input shaft I, and the clutch drum 26 is driven and connected so as to rotate integrally with the intermediate shaft M. Described as an example. However, the embodiment of the present invention is not limited to this. That is, the drive connection relationship between the clutch hub 21 and the clutch drum 26 with the input shaft I and the intermediate shaft M is switched, and the clutch hub 21 is driven and connected to rotate integrally with the intermediate shaft M, and the clutch drum 26 is input. It is also one of preferred embodiments of the present invention that the drive connection is made so as to rotate integrally with the shaft I.

(11) In each of the above embodiments, the rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the axially extending portion 49 constituting the clutch housing CH, and the transmission according to the present invention is used as the hybrid drive device 1. The case where is configured has been described as an example. However, the embodiment of the present invention is not limited to this. That is, it is not always essential that the rotating electrical machine MG is provided in the transmission, and it is also a preferred embodiment of the present invention to configure the transmission according to the present invention as a simple clutch-equipped transmission. In this case, it is also possible to manufacture the hybrid drive device by incorporating the rotating electrical machine MG into the clutch-equipped transmission device in a separate process performed differently in time or geographically.

(12) Regarding other configurations as well, the embodiments disclosed herein are illustrative in all respects, and the embodiments of the present invention are not limited thereto. That is, as long as the configuration described in the claims of the present application and a configuration equivalent thereto are provided, a configuration obtained by appropriately modifying a part of the configuration not described in the claims is naturally also included in the present invention. Belongs to the technical scope.

  The present invention includes a first shaft that is drivingly connected to an internal combustion engine, a second shaft that is disposed coaxially with the first shaft and that is drivingly connected to a speed change mechanism, and a driving force between the first shaft and the second shaft. Can be suitably used for a transmission including a clutch that can be switched between transmission and disconnection, a first shaft, a second shaft, and a case that houses the clutch.

1 Hybrid drive (transmission)
2 Case 7 Second support wall (support wall)
11 Flange part 16 Drain oil passage (shaft oil passage)
18 Oil pump 41 One side radial extending portion 45 The other side radial extending portion 49 Axial extending portion 51 First bearing 51a Outer peripheral surface 51b Inner peripheral surface 52 Second bearing 53 Third bearing 66 Radial groove (communication) Part)
E Internal combustion engine I Input shaft (first shaft)
M Intermediate shaft (second shaft)
CL Clutch CH Clutch housing L Separation distance

Claims (8)

A first shaft that is drivingly connected to the internal combustion engine, a second shaft that is arranged coaxially with the first shaft and is drivingly connected to the speed change mechanism, and a driving force between the first shaft and the second shaft. A transmission comprising: a clutch that can be switched between transmission and disconnection; and a case that houses the first shaft, the second shaft, and the clutch,
Drive-coupled so as to rotate integrally with the second shaft, disposed on one side of the clutch in the axial direction and extending in the radial direction, and disposed on the other side in the axial direction of the clutch in the radial direction A clutch housing that accommodates the clutch having an axially extending portion that extends in the axial direction and is disposed on the radially outer side of the clutch.
The first shaft enters the clutch housing through the radially inner side of the one side radially extending portion and has a flange portion extending in the radial direction,
The first shaft is supported by the second shaft from the other side in the axial direction via the first bearing, and the second shaft is supported by the case so as to be rotatable from the other side in the axial direction.
The transmission in which the one side radially extending portion is supported by the flange portion from the other side in the axial direction via a second bearing. The case includes a support wall portion that is disposed on the other axial side with respect to the clutch housing and accommodates an oil pump therein.
The transmission according to claim 1, wherein the other-side radial extending portion and the support wall portion are arranged at a predetermined interval in the axial direction without any other member interposed therebetween.   The transmission according to claim 1 or 2, wherein an oil chamber filled with oil is formed inside the clutch housing. The case includes a support wall portion that is disposed on the other axial side with respect to the clutch housing and accommodates an oil pump therein.
The other side radial direction extending portion and the support wall portion are arranged at a predetermined interval in the axial direction without interposing other members therebetween,
The axial distance between the other radial extension portion and the support wall portion is affected by centrifugal force acting on oil filled in the clutch housing when the clutch housing rotates. 4. The transmission according to claim 3, wherein the transmission is set to a value larger than a maximum value of a distance by which the other-side radially extending portion can move toward the other side in the axial direction.   The transmission according to any one of claims 1 to 4, wherein an end of the clutch housing on the other side in the axial direction is splined so as to be relatively displaceable in the axial direction with respect to the second shaft.   The other side radial direction extension part and the said flange part are arrange | positioned at predetermined intervals in the axial direction on the other side in the axial direction of the said flange part, without interposing another member in between. The transmission according to claim 5.   The said other side radial direction extension part is supported via the 3rd bearing from the axial direction one side by the said flange part on the other side of the said axial direction of the said flange part. The transmission described. An oil chamber filled with oil is formed inside the clutch housing,
The second shaft has an in-shaft oil passage for allowing the oil flowing out from the oil chamber to circulate at an end face on one axial side in the inner diameter portion thereof,
8. The first bearing according to claim 1, wherein the first bearing is formed in an annular plate shape and includes a communication portion that communicates at least between an outer peripheral surface and an inner peripheral surface in a radial direction. Gearbox.

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