KR20230028194A - Hybrid drive module - Google Patents

Abstract

The present invention provides a hybrid drive module, wherein a lockup clutch between a rotor hub and an output member is compact in an axial direction, has sufficient clutch capacity, and can be cooled easily, comprising: a rotor hub (20) having a rotor (52) installed thereon; an output member (80) for receiving the power of the rotor hub (20) and transmitting the power to a transmission; a lockup clutch (70) for selectively connecting the rotor hub (20) and the output member (80) therebetween; and a piston member (75) installed on the output member (80) to be able to slide in an axial direction and pressurizing or depressurizing the lockup clutch (70). The output member (80) includes: a sliding outer circumference surface (82) on which the piston member (75) slides; a connection flange (83) arranged behind the sliding outer circumference surface (82) and extending in a centrifugal direction; and a communicating hole (84) arranged on the connection flange (83) to connect a space in front of the connection flange (83) and a space therebehind to communicate with each other. The lockup clutch (70) is connected to the connection flange (83) at a more outward position in a radial direction than the communicating hole (84).

Description

Hybrid drive module {HYBRID DRIVE MODULE}

The present invention relates to a hybrid drive module, and more particularly, to a hybrid drive module in which a lock-up clutch between a rotor hub and an output member is compact in an axial direction, has sufficient clutch capacity, and is easy to cool.

A driving module used in a hybrid vehicle has a structure that transmits power of a motor and an engine to a transmission. The hybrid driving module includes an input member receiving power from the engine, a housing supporting the stator, a rotor hub supporting the rotor, an engine clutch connecting them between the input member and the rotor hub, and a motor and/or engine from the rotor hub. It includes an output member for receiving and transmitting the force of the transmission to the transmission, and a power transmission unit for connecting them between the rotor hub and the output member. The power transmission unit may have a structure including a torque converter and a lock-up clutch arranged in parallel on a power system.

An engine clutch, a lock-up clutch, and the like may be installed in a radially inner space of the rotor in the rotor hub. After the clutch or the like is installed in the space, a hub ridge or cover is installed to cover the space. The hub ridge is installed to rotate integrally with the rotor hub.

The input member and the rotor hub are mutually supported to be relatively rotatable, and the rotor hub and the output member are also mutually supported to be relatively rotatable.

The hybrid drive module is located between the engine and the transmission, and a compact design is required to improve mountability. These demands are even higher in the case of front-wheel drive vehicles.

Republic of Korea Patent Registration Publication KR 10-2239269 B1 discloses a hybrid drive module structure that is compact in the axial direction. Since the lock-up clutch of the disclosed hybrid driving module must transmit both engine power and motor power to the output member, it is necessary to increase clutch capacity. However, since the inner space of the hybrid driving module is already narrow in the axial direction, it is difficult to add a friction material any longer.

After all, in order to increase the clutch capacity without increasing the friction material in the above hybrid driving module, the operating pressure for pressing the clutch must be increased. Increasing the operating pressure means that power for forming such an operating pressure is consumed, which causes deterioration in fuel economy.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a hybrid drive module capable of increasing the capacity of a clutch without increasing a friction material and without increasing an operating pressure.

An object of the present invention is to provide a hybrid driving module implemented with a structure capable of increasing clutch capacity even in a narrow space.

An object of the present invention is to provide a hybrid driving module capable of smoothly flowing a fluid for cooling a friction material even in a narrow space.

The technical problems of the present invention are not limited to the above-mentioned purposes, and other objects and advantages of the present invention not mentioned above can be understood by the following description and will be more clearly understood by the embodiments of the present invention. . It will also be readily apparent that the objects and advantages of the present invention may be realized by means of the instrumentalities and combinations indicated in the claims.

The present invention for solving the above problems may be applied to a hybrid driving module having a motor disposed between an engine and a transmission in a power system and providing power to the transmission.

The hybrid drive module includes a rotor hub 20 in which a rotor 52 of a motor is installed, an output member 80 receiving power from the rotor hub 20 and transmitting the power to the transmission, and the rotor hub 20 and output A lock-up clutch 70 for selectively connecting them between members 80, and a piston member 75 that is slidably installed on the output member 80 in the axial direction to pressurize or release the pressurization of the lock-up clutch 70 can include

The output member 80 includes a sliding outer circumferential surface 82 on which the piston member 75 slides, a connecting flange 83 provided at the rear of the sliding outer circumferential surface 82 and extending in a centrifugal direction, and the connecting flange ( 83) and includes a communication hole 84 connecting the front space and the rear space of the connection flange 83 to pass through.

The lock-up clutch 70 is connected to the connecting flange 83 at a radially outer side than the communication hole 84 .

The lock-up clutch 70 includes a plurality of friction materials 71, a rotor side carrier 25 provided on the rotor hub 20 and connected to a selected portion of the friction materials 71 to be rotationally constrained, and the friction material 71 ) may include an output side carrier 72 connected to the rest of the rotationally constrained.

Among the plurality of friction materials 71, the rotor side carrier 25, the rotationally constrained friction material 71, the output carrier 72, and the rotationally constrained friction material 71 may be alternately disposed in the axial direction.

The rotor hub 20 includes a hub shaft 21 provided on a centripetal side and extending in the axial direction, a radially extending portion 23 extending radially from the hub shaft 21, and the radially extending portion 23. An axially extending portion 24 extending in the axial direction from the distal side end of the portion 23 may be provided.

The rotor side carrier 25 may be disposed further outside the output side carrier 72 in a radial direction.

The rotor-side carrier 25 may be provided on an inner circumference of the axially extending portion 24 .

The output-side carrier 72 may be disposed more inward than the rotor-side carrier 25 in the radial direction.

The communication hole 84 may communicate with a space (outflow space) between the piston member 75 and the output side carrier 72 in a forward direction.

A fluid clutch for fluidly coupling the rotor hub 20 and the output member 80 may be provided at a rear of the output member 80 .

The fluid clutch may be a torque converter 60 including an impeller 61, a turbine 62, and a reactor 64 disposed between them.

The reactor 64 may be connected to allow rotation in one direction with respect to the fixed end 65 and restrict rotation in the other direction. For example, this connection can be made by a one-way clutch (67).

The front surface of the fixed end 65 may be spaced apart from the rear surface of the connecting flange 83 .

The output member 80 may further include a rear outer circumferential surface 87 that extends further from the inner side in the radial direction to the rear than the communication hole 84 of the connection flange 83 .

A portion of the rear outer circumferential surface 87 may overlap with the fixed end 65 supporting the reactor 64 of the torque converter 60 in the axial direction and may be disposed further inward in the radial direction.

The rear outer circumferential surface 87 may include a shape in which an outer diameter gradually decreases toward the rear.

The facing inner circumferential surface 66 provided in the section overlapping the rear outer circumferential surface 87 in the axial direction at the fixed end 65 may include a shape in which the inner diameter gradually decreases toward the rear. Accordingly, the fluid supplied from the transmission receives the centrifugal force in the space between the rear outer circumferential surface 87 and the facing inner circumferential surface 66 and can smoothly flow forward.

The communication hole 84 may communicate with a space (inflow space) between the output member 80, the reactor 64, and the fixed end 65 in the rear.

Specifically, the communication hole 84 may communicate with a space between the rear surface and the rear outer circumferential surface 87 of the connecting flange 83 and the reactor 64 and the fixed end 65 in the rear.

The bearing 88 supporting the relative rotation of the output member 80 generated with the fluid clutch interposed therebetween is connected to the connection flange 83 from the outer side in the radial direction than the communication hole 84 located on the rear surface of the connection flange 83. (83) can be connected.

The bearing 88 may partially/entirely block/block the fluid in the inlet space from flowing outward in the radial direction. Accordingly, the inflow of the fluid in the inflow space into the communication hole 84 can be promoted.

The bearing 88 may define the inflow space at a radially outer side of the inflow space.

The communication hole 84 may be provided in the connection flange 83 in a form in which a plurality of the communication holes 84 are spaced apart along the circumferential direction.

The communication hole 84 may be inclined to extend radially outward from the rear to the front of the connection flange 83 . This can guide/promote the flow of the fluid from the inflow space to the outflow space through the communication hole 84 .

The communication hole 84 may have a hole portion 85 extending forward from the rear surface of the connection flange 83 .

The hole part 85 is connected to the first hole 851 recessed forward from the rear surface of the connection flange 83 and the front of the first hole 851 and has a diameter smaller than that of the first hole 851. It may include a second hole 852 having a. The second hole 852 may guide/accelerate the inflow of the fluid in the inflow space into the first hole 851 .

When viewed in the extension direction of the second hole 852, the flow end face of the second hole 852 may be disposed within the flow end face of the first hole 851. The second hole 852 may further guide/accelerate the inflow of the fluid in the inflow space into the first hole 851 .

The communication hole 84 is recessed from the front surface to the rear of the connection flange 83 so as to communicate with the hole portion 85 and the front end of the hole portion 85, and an annular groove 86 formed as a whole along the circumferential direction. can include

The inner circumferential surface provided on the distal side of the annular groove 86 may be inclined to extend outward in a radial direction from the rear to the front. This can guide/accelerate the flow of the fluid flowing from the hole 85 to the annular groove 86 into the outflow space.

The inner circumferential surface provided on the distal side of the annular groove 86 may be disposed further outward in the radial direction than the outlet of the hole 85 communicating with the annular groove 86 . This can guide/promote the outflow of the fluid from the hole 85 to the annular groove 86 .

The outer peripheral surface provided on the centripetal side of the annular groove 86 has a sliding extension surface 861 connected to the sliding outer peripheral surface 82 in a shape corresponding to the sliding outer peripheral surface 82, and the sliding extension surface 861 It may include a tapered surface 862 of a shape in which the outer diameter gradually decreases toward the rear.

A sliding portion 76 extending in the axial direction and having a bore sliding with the sliding outer circumferential surface 82 may be provided at the centripetal end of the piston member 75 .

The sliding portion 76 may extend rearward from a piston portion of the piston member 75 .

An outer diameter of the sliding portion 76 may be smaller than an inner diameter of an inner circumferential surface provided on a distal side of the annular groove 86 . Accordingly, even if the sliding part 76 moves backward to the sliding extension surface 861, a phenomenon in which the flow cross section of the annular groove 86 is reduced can be minimized.

A chamfer surface 77 may be provided at a radially outer corner of the rear end of the sliding part 76 . This can guide the flow of the fluid flowing out of the annular groove 86 into the outflow space.

Since the inner circumferential surface on the centrifugal side of the annular groove 86 is inclined, and the chamfer surface 77 of the sliding part 76 is also inclined, the cross-sectional area of flow between them can be regulated, thereby reducing the flow of fluid passing through the space between them. flow rate can be increased.

A spacer 89 may be interposed between the rotor hub 20 and the output member 80 to allow fluid to flow while maintaining a predetermined gap between the rotor hub 20 and the output member 80 .

A space between the rotor hub 20 and the piston member 75 may communicate with a space in which the spacer 89 is interposed.

The lockup clutch 70 may be disposed behind the piston member 75 .

The centripetal end of the lock-up clutch 70 may be disposed more rearward in the axial direction than a portion of the connection flange 83 disposed radially inside. Accordingly, it is possible to prevent the concavo-convex shape of the lock-up clutch 70 from acting as resistance to the flow of the fluid flowing into the outflow space through the communication hole 84.

The torque converter 60 may be disposed behind the lock-up clutch 70 .

The inner circumferential surface of the centripetal end of the lock-up clutch 70 and the inner circumferential surface of the centripetal end of the turbine plate 63 of the torque converter 60 may come into contact with the outer circumferential surface of the connection flange 83 . Accordingly, it is possible to prevent the concavo-convex shapes of the lock-up clutch 70 and the turbine plate 63 from acting as resistance to the flow of the fluid flowing into the outflow space through the communication hole 84.

The centripetal end of the lock-up clutch 70, the centripetal end of the turbine plate 63 of the torque converter 60, and the connecting flange 83 may contact each other in the axial direction and be riveted together. Accordingly, the axis alignment and fixation of the lock-up clutch 70 and the turbine plate 63 to the output member 80 can be performed at once.

According to the hybrid driving module of the present invention, the capacity of the clutch can be increased by securing the area of the piston member 75 without increasing the friction material and without increasing the operating pressure.

According to the present invention, the clutch capacity can be increased even in a narrow space without increasing the axial dimension of the hybrid drive module.

According to the present invention, the flow of fluid for cooling the friction material of the lock-up clutch can be smoothly induced even in a narrow space.

In addition to the effects described above, specific effects of the present invention will be described together while explaining specific details for carrying out the present invention.

1 is a cross-sectional view of an embodiment of a hybrid drive module according to the present invention.
2 is an enlarged view of a lock-up clutch, an output member, and a torque converter of the hybrid driving module shown in FIG. 1;
FIG. 3 is an enlarged view of an output member of the hybrid driving module shown in FIG. 2 and its vicinity.

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

The present invention is not limited to the embodiments disclosed below, and various changes may be applied and may be implemented in various different forms. Only this embodiment is provided to complete the disclosure of the present invention and to fully inform those skilled in the art of the scope of the invention. Therefore, the present invention is not limited to the embodiments disclosed below, but all changes and equivalents included in the technical spirit and scope of the present invention as well as substitution or addition of the configuration of one embodiment and the configuration of another embodiment each other to substitutes.

The accompanying drawings are only for easy understanding of the embodiments disclosed in this specification, and the technical idea disclosed in this specification is not limited by the accompanying drawings, and all changes and equivalents included in the spirit and technical scope of the present invention are included. It should be understood to include water or substitutes. In the drawings, components may be exaggeratedly large or small in size or thickness in consideration of convenience of understanding, etc., but due to this, the scope of protection of the present invention should not be construed as being limited.

Terms used in this specification are only used to describe specific implementations or examples, and are not intended to limit the present invention. And expressions in the singular include plural expressions unless the context clearly dictates otherwise. In the specification, terms such as "comprise" and "consist of" are intended to designate that features, numbers, steps, operations, components, parts, or combinations thereof described in the specification exist. That is, in the specification, terms such as ~ include, ~ consist of, etc. It should be understood that it does not preclude the possibility of the presence or addition of one or more other features, numbers, steps, operations, components, parts, or combinations thereof.

Terms including ordinal numbers, such as first and second, may be used to describe various components, but the components are not limited by the terms. These terms are only used for the purpose of distinguishing one component from another.

It is understood that when an element is referred to as being "connected" or "connected" to another element, it may be directly connected or connected to the other element, but other elements may exist in the middle. It should be. On the other hand, when an element is referred to as “directly connected” or “directly connected” to another element, it should be understood that no other element exists in the middle.

When an element is referred to as being “on top” or “under” another element, it should be understood that other elements may exist in the middle as well as being directly above the other element. .

Unless defined otherwise, all terms used herein, including technical or scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art to which the present invention belongs. Terms such as those defined in commonly used dictionaries should be interpreted as having a meaning consistent with the meaning in the context of the related art, and unless explicitly defined in the present application, they should not be interpreted in an ideal or excessively formal meaning. don't

Since the hybrid driving module of the embodiment is symmetrical about the axis, only half of the axis is shown for convenience of drawing. Also, for convenience of explanation, a direction along the longitudinal direction of an axis forming the center of rotation of the hybrid driving module is referred to as an axial direction. That is, the front-rear direction or the axial direction is a direction parallel to the axis of rotation, and the front (front) means a direction toward the power source, such as the engine, and the rear (rear) means the direction toward the other direction, such as the transmission. . Therefore, the front side (front side) means the side where the surface faces forward, and the rear side (rear side) means the side where the surface looks backward.

The radial direction or the radial direction means a direction approaching the center or a direction away from the center along a straight line passing through the center of the rotation axis on a plane perpendicular to the rotation axis. A direction away from the center in a radial direction is referred to as a centrifugal direction, and a direction approaching the center is referred to as a centripetal direction.

The circumferential direction or circumferential direction means a direction that surrounds the circumference of the rotating shaft. The outer circumference means an outer circumference, and the inner circumference means an inner circumference. Therefore, the outer circumferential surface is a surface in a direction facing away from the rotational axis, and the inner circumferential surface means a surface in a direction facing the rotational axis.

The circumferential side surface means a surface whose normal line is directed in the circumferential direction.

[Overall structure of hybrid drive module]

The hybrid drive module of the present invention is disposed between an engine and a transmission in a power system. In the drawing of the embodiment, the engine is disposed on the left side and the transmission is disposed on the right side.

The hybrid driving module includes a motor 50 that provides power to the transmission. The motor 50 includes a stator 51 and a rotor 52.

The stator 51 is fixed to the housing 10 of the hybrid drive module. And, the rotor 52 is accommodated in the housing 10 at a radially inner side of the stator 51 . The rotor 52 may be fixed to the rotor hub 20 disposed inside the housing 10 .

An input member 30 connected to the engine and receiving power of the engine is provided at the front center of the housing 10 . The input member 30 is rotatably supported with respect to the housing 10 through an input shaft bearing 34 .

The input member 30 protrudes more forward than the housing 10, and an input spline 32 is formed on an outer circumferential surface of the protruding portion. A torsional damper 36 is connected to the input spline 32 . The input side of the torsional damper 36 is connected to the engine, and the output side is connected to the input member 30.

A sealing member is interposed in front of the input shaft bearing 34 between the inner circumferential surface of the housing 10 and the outer circumferential surface of the input member 30 . That is, the fluid supplied from the transmission is filled behind the sealing member, and the sealing member and the housing 10 constitute a boundary of a space filled with the fluid. That is, the torsional damper 36 may be a dry spring damper.

The rotor hub 20 may include an axial extension portion 24 for fixing the rotor 52 and a radial extension portion 23 extending radially inward from the axial extension portion 24. can The axially extending portion 24 may have a shape similar to a cylinder extending in the axial direction.

The radially extending portion 23 is connected to an approximately central portion of the axially extending portion 24 in the axial direction.

A hub shaft 21 extending in the axial direction is provided at a radially inner end of the radially extending portion 23 . The hub shaft 21 is disposed rearward than the input member 30 in the axial direction, and a section in the axial direction overlaps the input member 30 . A hub shaft bearing 22 is interposed in a section where the input member 30 and the hub shaft 21 overlap, so that the input member 30 and the hub shaft 21 are mutually supported by rotation.

A hub ridge 40 is connected to the front end of the axially extending portion 24 . The hub ridge 40 is fitted into the axial extension portion 24 in a form accommodated in a radially inner space of the axial extension portion 24 from the front side of the axial extension portion 24 . At this time, the hub coupling part 41 provided at the radially outer end of the hub ridge 40 may be rotationally engaged with the axial extension part 24 . Subsequently, a snap ring is inserted into the axial extension portion 24 to prevent the hub ridge 40 from being separated from the axial extension portion 24 .

The radially inner end of the hub ridge 40 has a piston installation portion 42 extending rearward, and the radially inner end of the housing 10 also extends from the inner side to the rearward than the hub ridge 40. is extended And the ridge bearing 47 is interposed between them. That is, the hub ridge 40 is rotatably supported with respect to the housing 10 .

Accordingly, the rotor hub 20 is rotatably supported by the housing 10 through the hub ridge 40 and the ridge bearing 47, and the hub shaft bearing 22, the input member 30, and the input shaft bearing It is rotatably supported on the housing 10 via 34.

A back cover 55 is connected to the rear end of the axial extension part 24 . The back cover 55 is integrally fixed to the rear end of the axially extending portion 24 through welding or fastening means such as bolts.

A radially inner space of the axially extending portion 24 of the rotor hub 20 constitutes a space filled with a fluid such as transmission oil. This space may be divided into a first accommodating space 26 and a second accommodating space 27 by the radially extending portion 23 . The first accommodating space 26 may be defined as a space between the radially extending portion 23 and the back cover 55 in an axial direction. The second accommodating space 27 may be defined as a space between the hub ridge 40 and the radial extension part 23 in the axial direction. That is, the second accommodating space 27 is disposed more forward than the first accommodating space 26 .

The input member 30 is disposed on the side of the second accommodating space 27 . The input member 30 and the rotor hub 20 are connected through an engine clutch 37. The engine clutch 37 is also disposed in the second accommodating space 27 . The engine clutch 37 includes a clutch pack 38 in which a plurality of friction plates are disposed in an axial direction.

The radially outer side of the clutch pack 38 is fixed to the inner circumferential surface of the axially extending portion 24 of the rotor hub 20, and the radially inner side of the clutch pack 38 is the rear side of the input member 30. It is fixed to the input plate 33 extending outward in the radial direction at the end.

A piston plate 43 is disposed in front of the clutch pack 38 . The piston plate 43 is disposed between the hub ridge 40 and the clutch pack 38 in the axial direction. The outer circumferential surface of the piston plate 43 slidably contacts the hub ridge 40, and the inner circumferential surface of the piston plate 43 slidably contacts the piston mounting portion 42 of the hub ridge 40. . A space between the piston plate 43 and the hub ridge 40 forms a first operation chamber 430 .

An operation hole 44 connected to communicate with the first operation chamber 430 is provided in the hub ridge 40 .

A compensation plate 45 is disposed at the front of the clutch pack 38 and at the rear of the piston plate 43 . An outer circumferential surface of the compensating plate 45 is in contact with the piston plate 43 . The radially inner end of the compensating plate 45 is supported by the piston mounting portion 42 of the hub ridge 40 . Accordingly, the piston plate 43 comes into contact with the compensating plate 45 to be slidable. A space between the piston plate 43 and the compensation plate 45 constitutes a compensation chamber 450 . A return spring 48 is accommodated in the compensation chamber 450 . The return spring 48 is interposed between the piston plate 43 and the compensating plate 45 and elastically presses the piston plate 43 away from the compensating plate 45 . That is, the return spring 48 elastically biases the piston plate 43 in a direction in which the clutch pack 38 is depressurized.

A radial inner boundary of the compensation chamber 450 may be defined by the piston installation part 42 . A compensation hole 46 connected to communicate with the compensation chamber 450 is provided in the piston installation part 42 of the hub ridge 40 .

Although not shown, a first flow path communicating with the operation hole 44 is provided in the housing 10 . The fluid supplied to the first operation chamber 430 is supplied to the first operation chamber 430 through the first passage and the operation hole 44 . Then, the engine clutch 37 operates, and engine power is transmitted to the rotor hub 20 through the input member 30 and the clutch pack 38.

The housing 10 is provided with a second passage 11 communicating with the second accommodating space 27 . In the housing 10, the first flow path and the second flow path 11 do not communicate with each other.

The compensation hole 46 communicates with the second accommodating space 27 . Accordingly, the fluid supplied to the compensation chamber 450 is supplied to the compensation chamber 450 through the second passage 11, the second accommodating space 27, and the compensation hole 46.

In the second accommodating space 27, the above-described input shaft bearing 34, ridge bearing 47, and hub shaft bearing 22 are disposed, and a clutch pack 38 is also disposed. A passage hole 31 may be formed in the input member 30 so that the fluid filled in the second accommodating space 27 flows smoothly through the second passage 11 . Accordingly, the fluid supplied through the second flow passage 11 fills the second accommodating space 27 and lubricates and cools the bearings and the clutch pack 38 .

When the pressure of the fluid supplied through the first flow path overcomes the pressure of the fluid supplied through the second flow path 11 and the elastic force of the return spring 48, the piston plate 43 moves the clutch pack 38 is pressurized, and otherwise, the piston plate 43 depressurizes the clutch pack 38 .

The piston plate 43 and the compensating plate 45 rotate together with the hub ridge 40, and the hub ridge 40 is connected to the rotor hub 20 to be rotationally constrained. Accordingly, the piston plate 43 and the compensating plate 45 rotate together with the rotor hub 20 .

An output member 80 and a power transmission unit transmitting rotational force of the rotor hub 20 to the output member 80 may be accommodated in the first accommodating space 26 of the rotor hub 20 .

The power transmission unit may include a fluid clutch connected to the rotor hub 20 and friction materials in the form of a clutch pack connected to the rotor hub 20 .

The fluid clutch may be a torque converter (60). That is, the fluid clutch is a half torus type impeller 61 and a turbine 62 facing each other, and a reactor 64 disposed between them and connected to the fixed end 65 through a one-way clutch 67 can include

The impeller 61 may be provided on the back cover 55 . Accordingly, the impeller 61 is rotationally constrained to the rotor hub 20 .

A pump drive hub 56 extending rearwardly is provided on the inside of the back cover 55 in the radial direction.

The fixing end 65 is disposed on the inner side of the pump driving hub 56 in the radial direction, and a cover bearing 57 may be interposed therebetween. The output member 80 is disposed radially inward while being forward of the fixed end 65, and a bearing 88 may be interposed therebetween.

When the rotor hub 20 rotates, the rotational force drives the pump through the back cover 55 and the pump driving hub 56, and thus, the space between the output member 80 and the fixed end 65 Transmission oil is supplied to the first accommodating space 26 through. Accordingly, the first accommodating space 26 is filled with fluid for operating the fluid clutch and cooling the friction material 71 . The oil introduced into the first accommodating space 26 may flow out to the transmission through the space between the fixed end 65 and the back cover 55 . During the fluid circulation process, the friction material 71, the one-way clutch 67, the cover bearing 57, and the bearing 88 may be lubricated and cooled.

The turbine 62 faces the impeller 61 and is disposed in front of the impeller 61, and the radially inner side of the turbine plate 63 on which the turbine 62 is installed is connected to the output member 80. The output member 80 is connected to the input of the transmission.

A reactor 64 is disposed between the impeller 61 and the turbine 62. The reactor 64 is installed on the fixed end 65 via the one-way clutch 67. The reactor 64 relatively rotates with respect to the back cover 55 and also relatively rotates with respect to the output member 80 . In order to allow the relative rotation of the back cover 55 and the reactor 64 and the relative rotation of the output member 80 and the reactor 64 and to mutually support them, the reactor 64 and the back cover 55 The cover bearing 57 is interposed between them, and the bearing 88 is interposed between the reactor 64 and the output member 80. That is, the output member 80 and the back cover 55 are rotatably supported with respect to the fixed end 65 .

In a state where there is a difference between the rotational speeds of the rotor hub 20 and the output member 80, the rotational force of the motor and/or engine may be transmitted to the output member 80 through the torque converter 60.

A lock-up clutch 70 is disposed in front of the turbine plate 63 in the first accommodating space 26 . The lock-up clutch 70 includes a friction material 71 in which a plurality of friction plates are disposed in an axial direction.

The friction material 71 connects or disconnects the rotor hub 20 and the output member 80 between them.

The plurality of friction materials 71 include a friction material 71 connected to the rotor side carrier 25 provided on the inner circumferential surface of the axially extending portion 24 of the rotor hub 20 from the outside in the radial direction, and the friction material 71 in the radial direction. Friction materials 71 connected to the output member 80 from the inside are disposed alternately along the axial direction.

The rotor side carrier 25 may be disposed further outside the output side carrier 72 in a radial direction. That is, the output-side carrier 72 may be disposed more inward than the rotor-side carrier 25 in the radial direction.

In the embodiment, a structure in which the rotor-side carrier 25 is integrally formed on the inner circumferential surface of the axially extending portion 24 is exemplified. However, the rotor side carrier 25 may have a structure that is manufactured as a separate part and then coupled to the rotor hub 20 .

The friction material 71 may be connected to the output carrier 72 at its inner side in the radial direction, and the output carrier 72 may be connected to the output member 80 in a form in which the output carrier 72 is fixed to the output member 80.

A piston member 75 pressurizing or releasing the pressurization of the friction material 71 is installed in the first accommodating space 26 .

The piston member 75 has a shape extending in the radial direction, and has a first surface (rear surface) facing one side in the axial direction and a second surface (front surface) facing the opposite direction. That is, the first surface and the second surface face each other (opposite).

The piston member 75 is disposed at the rear of the radially extending portion 23 and at the front of the lock-up clutch 70 . Accordingly, the first surface is disposed to face the friction material 71 and the torque converter. And the second surface is disposed to face the radially extending portion 23 .

A radially inner end of the piston member 75 comes into contact with the outer circumferential surface of the output member 80 in a sliding manner. The radially outer end of the piston member 75 comes into contact with the inner circumferential surface of the axially extending portion 24 in a sliding manner.

The radially extending portion 23 and the piston member 75 define a second operating chamber 750 for the piston member 75 . The second surface of the piston member 75 faces the second operation chamber 750 .

The output member 80 has a hollow shaft shape. An output spline 81 connected to the input of the transmission is formed on the inner circumferential surface of the hollow shaft. The hollow part of the output member 80 constitutes a passage through which fluid is supplied to the second operation chamber 750 . A spacer 89 is interposed between the output member 80 and the radially extending portion 23 to allow movement of fluid while maintaining a distance therebetween. The passage communicates with the second operation chamber 750 through a space between the output member 80 and the radially extending portion 23 . Therefore, the transmission oil supplied through the passage may flow into the second operation chamber 750 . When the pressure in the second operation chamber 750 is higher than the pressure in the first accommodating space 26, the piston member 75 moves backward to operate the lock-up clutch 70, and the rotational force of the rotor hub 20 It can be transmitted to the output member 80 through the lock-up clutch 70 . When the pressure in the second operation chamber 750 is lower than the pressure in the first accommodating space 26, the piston member 75 advances and the lock-up clutch 70 is released.

[Expansion of the area of the piston member and cooling structure of the friction material]

The hybrid drive module is located between the engine and the transmission, and a compact design is required to improve mountability. In the case of a front-wheel drive vehicle, the space in the engine room is narrow, requiring a more compact design.

The demand for miniaturization of the hybrid drive module is demanded for both axial dimension reduction as well as radial dimension reduction, but the demand for axial dimension reduction is particularly greater.

In the hybrid driving module described above, the engine clutch 37 requires a clutch capacity sufficient to transfer engine power to the rotor hub 20, whereas the lock-up clutch 70 is a rotor in which engine power and motor power are combined. Since the rotational force of the hub 20 must be transmitted to the output member 80 or vice versa, a higher clutch capacity is required.

The clutch capacity is influenced by the characteristics of the friction material and the characteristics of the pressing force that presses the friction material. Regarding the characteristics of the friction material, the clutch capacity increases as the friction coefficient of the friction material increases, the number of friction materials increases, and the effective radius of the friction material increases. Regarding the characteristics of the pressing force for pressurizing the friction material, the clutch capacity increases as the operating pressure of the fluid pressing the piston increases and the cross-sectional area of the piston on which the operating pressure of the fluid acts increases.

Here, if an attempt is made to increase the number of friction materials, the axial dimension of the hybrid drive module is inevitably increased. That is, there is a limit to increasing the number of friction materials in a state where the axial dimension of the hybrid driving module is limited.

In addition, if the effective radius of the friction material is increased, the radial dimension of the hybrid drive module will inevitably be increased. That is, there is a limit to increasing the effective radius of the friction material in a state where the radial dimension of the hybrid drive module is limited.

In addition, in order to increase the operating pressure of the fluid that pressurizes the piston, power is consumed to generate hydraulic pressure, which leads to deterioration in fuel efficiency.

In this embodiment, a structure for maximizing the cross-sectional area of the piston is proposed.

In the embodiment, the centrifugal side of the piston member 75 directly slides on the inner circumferential surface of the axially extending portion 24 of the rotor hub 20 to secure the outer diameter as much as possible.

In the embodiment, the outer diameter of the output member 80 to which the centripetal side of the piston member 75 slides is reduced as much as possible to reduce the inner diameter of the piston member 75 as much as possible.

Then, the effective area of the piston member 75 receiving pressure acting in the axial direction from the fluid in the second operation chamber 750 can be secured as much as possible.

In addition, the embodiment proposes a structure capable of smoothly cooling the friction material so that the friction coefficient of the friction material is maintained.

In the embodiment, the fluid coupling is performed in the torque converter 60 and the heated fluid is supplied to the friction material 71 to reduce the phenomenon in which the friction coefficient of the friction material is lowered. 71) to provide a flow path structure that leads to smooth supply.

The output member 80 is connected to the power transmission unit, that is, the turbine plate 63 of the torque converter 60 and the output side carrier 72 of the lock-up clutch 70 to receive the rotational force of the rotor hub 20, and It is connected to the input shaft of the transmission through the output spline 81 provided in the transmission and transmits the rotational force to the transmission. In addition, the output member 80 provides a sliding outer peripheral surface 82 on which the piston member 75 slides.

Therefore, the output member 80 secures rigidity for transmitting rotational force between the rotor hub 20 and the input of the transmission while minimizing the axial dimension for compactness of the hybrid drive module, and also the outer diameter of the sliding outer peripheral surface 82 It is preferable to reduce the inner diameter of the piston member 75 to the maximum by reducing the maximum.

To this end, the output member 80 has a shape in which the radial position of a portion connected to the power transmission unit, that is, the torque converter 60 and the lock-up clutch 70, and a portion where the sliding outer circumferential surface 82 is provided are different. do. That is, the radial distance of the connecting portion from the center of rotation is greater than the radial distance of the sliding outer circumferential surface 82 .

The sliding outer peripheral surface 82 is provided on the front part of the output member 80 . Further, the torque converter 60 and the lock-up clutch 70 are provided behind the sliding outer circumferential surface 82 and are connected to a connection flange 83 whose diameter is larger than the sliding outer circumferential surface 82 . That is, the connection flange 83 extends in a centrifugal direction from the rear of the sliding outer circumferential surface 82 .

The output spline 81 may be provided on an inner circumferential surface of the output member 80 in an axial section in which the sliding outer circumferential surface 82 and the connection flange 83 are provided. Accordingly, while suppressing the increase in the axial length of the output member 80, the axial length of the output spline 81 is secured to secure the coupling force or power transmission rigidity between the output member 80 and the transmission, and transmit the rotational force. By securing the radial distance of the connection flange 83 for this purpose, and minimizing the outer diameter of the sliding outer peripheral surface 82 to reduce the inner diameter of the piston member 75, the pressure acting area of the piston member 75 can be secured as much as possible. there is.

The centripetal part of the turbine plate 63 of the torque converter 60 overlaps with the centripetal part of the output side carrier 72 of the lock-up clutch 70 from the rear side in the axial direction. And it overlaps with the centrifugal portion of the connection flange 83 in the axial direction, and is mutually fastened through a fastening means such as a rivet 832.

Then, the rotational force of the rotor hub 20 is transmitted to the output member 80 through the rivet 832 . At this time, since the radial distance of the rivet 832 from the center of rotation is longer than the radial distance of the sliding outer circumferential surface 82 from the center of rotation, the stress applied to the rivet 832 may be smaller even when the same amount of torque is transmitted. there is.

According to the embodiment, at the front part of the distal side of the connection flange 83, the front step opened in the forward and centrifugal direction so that the centripetal part of the turbine plate 63 and the centripetal part of the output carrier 72 can be engaged. shape is prepared. In addition, the inner circumferential surface of the centripetal of the output carrier 72 and the inner circumferential surface of the centripetal of the turbine plate 63 are in contact with the outer circumferential surface of the front step shape, and the rear surface of the turbine plate 63 is in contact with the front surface of the front step and is positioned in the axial direction. and the radial position are mutually regulated. Accordingly, coupling and alignment of parts can be performed very easily and accurately.

At the rear part of the distal side of the connection flange 83, a rear step shape opened in the rearward and centrifugal direction is provided so that the bearing 88 is seated. The bearing 88 is in contact with the outer circumferential surface and the rear surface of the rear step, and its axial position and radial position are mutually regulated. Due to the rear step shape of the connecting flange 83, the distance between the output member 80 and the fixing end 65 can be made closer, thereby making the axial dimension of the hybrid driving module more compact. .

The rear head portion of the rivet 832 is accommodated in the head receiving groove 831 provided on the rear surface of the rear step of the connection flange 83 . Therefore, the bearing 88 does not interfere with the rivet 832 and can contact the rear surface of the rear step of the connecting flange 83 and be accurately seated on the connecting flange 83.

According to the embodiment, as if the rivet 832 fastened to the connection flange 83 of the output member 80 has a radial distance from the center of rotation, the portion of the connection flange 83 through which the rivet 832 passes rotates. Since the radial distance from the center is also secured, there is no problem in transmitting torque even if the axial thickness of the distal portion of the connection flange 83 is reduced by placing a step shape on the front and rear portions of the distal side of the connection flange 83.

According to the structure of the output member 80 as above, due to the shape of the connection flange 83, the space in front of the connection flange 83 and the space behind the connection flange 83 are blocked. In addition, a portion where the connection flange 83 and the rivet 832 are coupled is covered by the bearing 88 positioned at the rear step of the connection flange 83.

According to this structure, the fluid supplied between the output member 80 and the fixed end 65 is supplied to the torus space of the torque converter 60 through the gap provided in the bearing 88, and the fluid in the torus space is supplied to the turbine plate ( 63) and the axially extending portion 24 of the rotor hub 20, it flows toward the friction material 71.

The temperature of the fluid flowing through the fluid coupling in the torus space rises, and according to the above structure, the high temperature fluid reaches the friction material 71 . Then, there is a concern that the friction coefficient of the friction material 71 is lowered due to the high-temperature environment.

However, for a compact design, since the holes of the connection flange 83 prepared for fastening the rivet 832 are covered by the bearing 88, there is a gap between the output member 80 and the fixed end 65. It is difficult for the supplied fluid to flow from the rear space of the connection flange 83 to the front space through the holes of the connection flange 83.

According to the embodiment, in order to prepare a path through which fluid flows from the rear space of the connection flange 83 to the front space of the connection flange 83, the communication hole 84 penetrated in the front and rear directions of the connection flange 83 provides

The lock-up clutch 70 and the torque converter 60 are connected to the connection flange 83 at a radially outer side than the communication hole 84 . That is, the front step shape and the rear step shape of the connection flange 83 are formed outside the communication hole 84 in the radial direction.

The communication hole 84 communicates with the space between the piston member 75 and the output side carrier 72 (i.e., the outflow space) in the front, and the output member 80 and the fixed end 65 in the rear. ) communicates with the space between (i.e., inlet space).

The output member 80 further includes a rear outer circumferential surface 87 extending further from the inner side in the radial direction to the rear than the communication hole 84 of the connection flange 83 . The section in which the rear outer circumferential surface 87 is formed in the output member 80 in the axial direction is a part that is not directly involved in transmitting rotational force between the rotor hub 20 and the transmission. Therefore, the radial thickness of the output member 80 in the corresponding section can be formed thinner than the radial thickness of the output member 80 in the connecting flange 83 section or the sliding outer circumferential surface 82 section provided ahead of it.

Accordingly, there is no particular difficulty in ensuring that a portion of the rear outer circumferential surface 87 overlaps with the fixing end 65 in the axial direction and is arranged more inward in the radial direction.

The rear outer circumferential surface 87 may include a shape in which an outer diameter gradually decreases toward the rear. Correspondingly, the facing inner circumferential surface 66 provided in the section overlapping the rear outer circumferential surface 87 in the axial direction at the fixed end 65 may include a shape in which the inner diameter gradually decreases toward the rear. Then, the fluid supplied from the transmission receives the centrifugal force in the space between the rear outer circumferential surface 87 and the facing inner circumferential surface 66 to smoothly flow forward.

At the rear of the communication hole 84, the inflow space defined by the rear surface and the rear outer circumferential surface 87 of the connection flange 83, the reactor 64, and the fixed end 65 is provided.

The bearing 88 is disposed radially outward from the communication hole 84 at the rear surface of the connection flange 83 . Accordingly, the inner circumferential surface of the bearing 88 can define the outer boundary in the radial direction of the inlet space.

Since the bearing 88 partially/entirely blocks/blocks the flow of the fluid in the inflow space outward in the radial direction, the fluid in the inflow space is prevented from flowing outward in the radial direction through the gap of the bearing 88. Rather, it flows more toward the communication hole 84.

The communication hole 84 may be inclined to extend radially outward from the rear to the front of the connection flange 83 . This can guide/promote the flow of the fluid from the inflow space to the outflow space through the communication hole 84 .

In the embodiment, a shape in which the degree of inclination of the communication hole 84 and the degree of inclination of the rear outer circumferential surface 87 substantially correspond to each other is exemplified. However, the inclination angles do not necessarily have to coincide with each other.

The communication hole 84 includes a plurality of hole portions 85 formed in the connection flange 83 in a spaced apart arrangement along the circumferential direction.

The hole portion 85 extends forward from the rear surface of the connection flange 83 .

The hole part 85 is connected to the first hole 851 recessed forward from the rear surface of the connection flange 83 and the front of the first hole 851 and has a diameter smaller than that of the first hole 851. It includes a second hole 852 having a. When viewed in the extension direction of the second hole 852, the flow end face of the second hole 852 is disposed within the flow end face of the first hole 851. That is, the first hole 851 and the second hole 852 have a funnel-like shape. This shape allows the fluid in the inlet space to more easily flow into the communication hole 84 .

The communication hole 84 further includes an annular groove 86 recessed backward from the front surface of the connection flange 83 and formed as a whole along the circumferential direction so as to communicate with the front end of the hole portion 85 .

The piston member 75, which moves in the front-rear direction and slides on the sliding outer circumferential surface 82 of the output member 80 to operate/release the lock-up clutch 70, extends in the axial direction and extends in the sliding outer circumferential surface 82 and a sliding portion 76 having a bore that slides.

The sliding part 76 may have a shape extending rearward from the centripetal end of the piston member 75 .

It is preferable that the sliding part 76 has a certain length in the axial direction so that sliding occurs smoothly.

Accordingly, the sliding part 76 has a shape extending rearward from the centripetal end of the piston member 75, and the outer diameter of the sliding part 76 is the inner circumferential surface provided on the distal side of the annular groove 86. If it is smaller than the inner diameter of , when the sliding part 76 slides in the axial direction, a part of the rear end side of the sliding part 76 does not interfere with the connecting flange 83 and is defined by the annular groove 86. Since the sliding outer circumferential surface 82 of the output member 80 can be extended in the axial direction, it is possible to further compact the length of the output member 80.

The outer circumferential surface provided on the centripetal side of the annular groove 86 has a sliding outer circumferential surface 82 and a sliding extension surface 861 connected to the sliding outer circumferential surface 82 in a shape corresponding to the sliding extension surface 861. It is connected to the rear side and includes a tapered surface 862 having a shape in which the outer diameter gradually decreases toward the rear. The sliding extension surface 861 guides sliding of the sliding portion 76 of the piston member 75 . In addition, the tapered surface 862 further increases the flow sectional area of the communication hole 84 to promote the flow of fluid through the communication hole 84 .

The inner circumferential surface provided on the distal side of the annular groove 86 is disposed more outward in the radial direction than the outlet of the hole portion 85 communicating with the annular groove 86 . Accordingly, the fluid flowing through the hole portion 85 flows more smoothly into the annular groove 86 .

The inner circumferential surface provided on the distal side of the annular groove 86 has an inclined shape so as to extend outward in the radial direction from the rear to the front. This guides and promotes the forward flow of the fluid in the annular groove 86.

As described above, since the outer diameter of the sliding part 76 is smaller than the inner diameter of the inner circumferential surface provided on the distal side of the annular groove 86, even if the sliding part 76 moves backward to the sliding extension surface 861, it has an annular shape. A phenomenon in which the flow cross section of the groove 86 is reduced can be minimized.

In addition, the chamfer surface 77 is provided at the radially outer corner of the rear end of the sliding part 76, so that the reduction in the flow cross section of the annular groove 86 can be further minimized, and from the annular groove 86 It is possible to guide the fluid flowing out into the outflow space.

At this time, if the degree of inclination of the chamfer surface 77 of the sliding part 76 is steeper than the degree of inclination of the inner circumferential surface on the distal side of the annular groove 86, the distance between them gradually increases from the rear to the front. It can be made into a reduced form. In this way, if the flow cross-sectional area is properly designed, the effect of increasing the flow velocity of the fluid passing through the space between them can be exerted.

Meanwhile, the inner circumferential surface of the centripetal end of the output carrier 72 and the inner circumferential surface of the centripetal end of the turbine plate 63 are fitted into the front step portion of the connecting flange 83 and may come into contact with the outer circumferential surface of the front step portion. there is. Accordingly, concavo-convex shapes that may exist at the centripetal end of the output carrier 72 and the turbine plate 63 are not exposed in the centripetal direction. Accordingly, the concavo-convex shape does not hinder the flow of the fluid flowing into the outflow space through the communication hole 84.

According to this structure, the fluid supplied from the transmission to the first accommodating space flows into the inflow space while receiving a centrifugal force through the space between the rear outer circumferential surface 87 and the facing inner circumferential surface 66 . The fluid is smoothly introduced toward the communication hole 84 through the first hole 851 in a state in which the flow into the torus is blocked by the bearing 88 in the inflow space.

The fluid in the communication hole 84 receives a centrifugal force, promotes a forward flow, and flows out into the outflow space. The fluid in the outflow space flows in a centrifugal direction through the space between the piston member 75 and the output side carrier 72 to cool the friction material 71 and flows toward the torus of the torque converter 60.

The fluid in the Taurus returns to the transmission through the space between the fixed end 65 and the back cover 55.

That is, according to the present invention, the capacity of the lock-up clutch 70 can be further increased by increasing the area of the piston member 75 and allowing the relatively low-temperature fluid to cool the friction material 71.

As described above, the present invention has been described with reference to the drawings illustrated, but the present invention is not limited by the embodiments and drawings disclosed herein, and various modifications are made by those skilled in the art within the scope of the technical idea of the present invention. It is obvious that variations can be made. In addition, although the operation and effect according to the configuration of the present invention have not been explicitly described and described while describing the embodiments of the present invention above, it is natural that the effects predictable by the corresponding configuration should also be recognized.

10: housing
11: 2nd Euro
20: rotor hub
21: hub axis
22: hub shaft bearing
23: radial extension
24: axial extension
25: rotor side carrier
26: first receiving space
27: second receiving space
30: input member
31: Eurohole
32: input spline
33: input plate
34: input shaft bearing
36: torsional damper
37: engine clutch
38: clutch pack
40: Hub Ridge
41: hub coupling part
42: piston installation part
43: piston plate
430: first operating chamber
44: operating hole
45: compensation plate
450: compensation chamber
46: compensation hall
47: ridge bearing
48: return spring
50: motor
51: stator
52: rotor
55: back cover
56: pump drive hub
57: cover bearing
60: torque converter
61: impeller
62: Turbine
63: turbine plate
64: reactor
65: fixed end
66: If you give in face to face
67: one way clutch
70: lock-up clutch
71: friction material
72: output side carrier
75: piston member
750: second working chamber
76: sliding part
77: chamfer surface
80: output member
81: output spline
82: sliding outer circumference
83: connection flange
831: head receiving groove
832: rivets
84: communication hole
85: hole part
851: 1st hole
852: 2nd hole
86: annular groove
861: sliding extension surface
862: tapered surface
87: rear outer circumference
88: bearing
89: spacer

Claims (17)

A hybrid drive module disposed between an engine and a transmission in a power system and having a motor for providing power to the transmission,
a rotor hub 20 on which a rotor 52 is installed;
an output member 80 receiving power from the rotor hub 20 and transmitting the power to the transmission;
a lock-up clutch 70 selectively connecting the rotor hub 20 and the output member 80; and
A piston member 75 that is slidably installed on the output member 80 in the axial direction and pressurizes or releases the lock-up clutch 70,
The output member 80 is:
a sliding outer peripheral surface 82 on which the piston member 75 slides;
a connection flange 83 provided at the rear of the sliding outer circumferential surface 82 and extending in a centrifugal direction; and
A communication hole 84 provided in the connection flange 83 and connecting the front space and the rear space of the connection flange 83 through,
The hybrid driving module, wherein the lock-up clutch (70) is connected to the connecting flange (83) at a radially outer side of the communication hole (84).
The method of claim 1,
The communication hole (84) is inclined to extend outward in a radial direction from the rear to the front of the connection flange (83).
The method of claim 1,
The communication hole 84 is,
a first hole 851 recessed forward from the rear surface of the connection flange 83; and
A hybrid drive module comprising: a second hole 852 connected to the front of the first hole 851 and having a smaller diameter than the first hole 851.
The method of claim 3,
When viewed in the extension direction of the second hole (852), the flow end face of the second hole (852) is disposed within the flow end face of the first hole (851).
The method of claim 1,
The communication hole 84 is,
a hole 85 extending forward from the rear surface of the connection flange 83; and
A hybrid drive module comprising: an annular groove 86 recessed from the front to the rear of the connection flange 83 to communicate with the front end of the hole 85 and formed as a whole along the circumferential direction.
The method of claim 5,
The inner circumferential surface provided on the distal side of the annular groove 86 is inclined to extend outward in a radial direction from the rear to the front.
The method of claim 5,
An inner circumferential surface provided on the distal side of the annular groove (86) is disposed further outside in a radial direction than the exit of the hole portion (85) communicating with the annular groove (86).
The method of claim 5,
The outer peripheral surface provided on the centripetal side of the annular groove 86 has a sliding extension surface 861 connected to the sliding outer peripheral surface 82 in a shape corresponding to the sliding outer peripheral surface 82, and the sliding extension surface 861 A hybrid drive module comprising a tapered surface 862 connected and having a shape whose outer diameter gradually decreases toward the rear.
The method of claim 5,
At the centripetal end of the piston member 75, a sliding portion 76 extending in the axial direction and having a bore sliding with the sliding outer peripheral surface 82 is provided,
An outer diameter of the sliding portion (76) is smaller than an inner diameter of an inner circumferential surface provided on a distal side of the annular groove (86).
The method of claim 9,
A chamfer surface (77) is provided at a radially outer corner of the rear end of the sliding portion (76).
The method of claim 1,
A fluid clutch for fluidly coupling the rotor hub 20 and the output member 80 is provided at the rear of the connection flange 83 of the output member 80,
The bearing 88 supporting the relative rotation of the output member 80 generated with the fluid clutch interposed therebetween is connected to the connection flange 83 from the outer side in the radial direction than the communication hole 84 located on the rear surface of the connection flange 83. Hybrid drive module, connected to (83).
The method of claim 1,
The output member 80 further includes a rear outer circumferential surface 87 extending further from the inner side in the radial direction to the rear than the communication hole 84 of the connection flange 83,
The rear outer circumferential surface (87) includes a shape in which an outer diameter gradually decreases toward the rear.
The method of claim 12,
A torque converter 60 fluidly coupling the rotor hub 20 and the output member 80 is provided at the rear of the output member 80,
A portion of the rear outer circumferential surface 87 overlaps with the fixed end 65 supporting the reactor 64 of the torque converter 60 in the axial direction and is disposed more inward in the radial direction,
The hybrid driving module, wherein the inner circumferential surface 66 provided in the section overlapping the rear outer circumferential surface 87 in the axial direction at the fixed end 65 includes a shape in which the inner diameter gradually decreases toward the rear.
The method of claim 13,
The front surface of the fixed end (65) is spaced apart from the rear surface of the connecting flange (83), the hybrid driving module.
The method of claim 1,
A spacer 89 is interposed between the rotor hub 20 and the output member 80 to allow fluid flow while maintaining a predetermined gap between the rotor hub 20 and the output member 80,
The space between the rotor hub 20 and the piston member 75 communicates with the space in which the spacer 89 is interposed,
The hybrid driving module, wherein the lock-up clutch (70) is disposed behind the piston member (75).
The method of claim 1,
The hybrid drive module, wherein the centripetal end of the lock-up clutch (70) is disposed more rearward in the axial direction than a portion of the connection flange (83) disposed radially inside.
The method of claim 1,
At the rear of the lock-up clutch 70, a torque converter 60 for fluidly coupling the rotor hub 20 and the output member 80 is provided,
The inner circumferential surface of the centripetal end of the lock-up clutch 70 and the inner circumferential surface of the centripetal end of the turbine plate 63 of the torque converter 60 are in contact with the outer circumferential surface of the connecting flange 83,
Hybrid drive module, wherein the centripetal end of the lock-up clutch (70), the centripetal end of the turbine plate (63) of the torque converter (60) and the connection flange (83) are in contact with each other in the axial direction and are riveted.

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