CN116529109A - Hybrid power driving module - Google Patents

Abstract

The present invention relates to a hybrid drive module including an electric motor having a rotor and a stator, the hybrid drive module including: a housing provided with the stator; a rotor hub provided with the rotor rotatably supported by the housing; and an axial movement prevention portion between the housing and the rotor hub for restricting forward movement and backward movement of the rotor hub relative to the housing. The axial movement prevention portion may be provided at a bearing interposed between the housing and the rotor hub. The bearing comprises: a first ring in contact with the first circumferential surface; a second ring in contact with the second circumferential surface; and a rolling element interposed between the first and second rings, the axial movement prevention unit including: a bearing groove provided on a surface of the first ring; a circumferential surface groove provided in the first circumferential surface; and a gap preventing ring inserted across the circumferential surface groove and the bearing groove. The height of the gap preventing ring is smaller than or equal to the depth of the circumferential groove.

Description

Hybrid power driving module

Technical Field

The present invention relates to a hybrid drive module, and more particularly, to a hybrid drive module in which a seal structure is provided between a rotor hub that rotates relative to a housing that is a fixed end of the hybrid drive module and the housing, and a motor position sensor is mounted between a motor and an output member.

Background

A drive module used in a hybrid vehicle has a structure that transmits the force of a motor and an engine to a transmission. A hybrid drive module comprising: an input member for transmitting a force from an engine, an electric motor, an engine clutch for connecting the input member and the electric motor, an output member for transmitting a force from the electric motor and/or the engine to a transmission, and a power transmission unit for connecting the electric motor and the output member. The power transmission portion may be a structure that directly connects the motor and the output member or a structure that includes a torque converter (fluid clutch) and a lockup clutch.

The motor, including a stator and a rotor, may be provided on a rotor hub. A space for disposing a clutch or the like is provided in a radially inner space of a rotor formed by the rotor hub. After the space is provided with a clutch or the like, a cover or a boss is provided to cover the space. The hub protrusion is arranged to rotate integrally with the rotor hub.

The stator is disposed on the housing. The input member, the rotor hub, the output member, and the like are rotatably provided to the housing.

The clutch provided in the radially inner space of the rotor hub is operated or released by hydraulic pressure. Furthermore, the hydraulic pressure may be supplied to the radially inner space of the rotor hub through a housing. At this time, the hydraulic pressure provided for operating the clutch also serves as a force for moving the rotor hub itself in the axial direction from the housing. Axial movement of the rotor hub relative to the housing may result in interference between the parts and thus wear. Furthermore, such interference and wear may cause serious abnormal driving of the hybrid drive module. Therefore, there is an additional need for a structure that prevents relative movement between the housing and the rotor hub.

In addition, as described above, when components such as thrust bearings are added as an axial support structure to prevent relative movement of the housing and the rotor hub, an increase in the number of components and the number of assembly processes causes an increase in production costs. Therefore, there is a need for a structure that prevents relative movement between the housing and the rotor hub while minimizing the number of parts and assembly steps.

Disclosure of Invention

The present invention has been made to solve the above-described problems, and an object thereof is to provide a hybrid drive module in which a rotor hub does not move relative to a housing in an axial direction.

Another object of the present invention is to provide a hybrid drive module that prevents relative movement between a housing and a rotor hub while minimizing the number of parts and assembly processes.

In order to solve the above-described problem, the present invention is applicable to a hybrid drive module including a motor 40 having a rotor 42 and a stator 41.

The hybrid drive module includes: a housing 80 provided with the stator 41; a rotor hub 43 provided with the rotor 42 and rotatably supported by the housing 80; and an axial movement preventing portion between the housing 80 and the rotor hub 43 for restricting forward movement and backward movement of the rotor hub 43 relative to the housing 80.

The axial movement prevention portion may be provided between the housing 80 and the rotor hub 43 to support the bearings B2, B3 of the rotor hub 43 for rotation with respect to the housing 80.

The bearing may be interposed between the circumferential surface of the housing 80 side and the circumferential surface of the rotor hub 43 side, which face each other in the radial direction.

The bearing may include: a first ring that contacts a first circumferential surface that is a surface selected from the circumferential surface on the housing 80 side and the circumferential surface on the rotor hub 43 side; a second ring that contacts a second circumferential surface of the other of the circumferential surface on the housing 80 side and the circumferential surface on the rotor hub 43 side; and a rolling element interposed between the first and second rings.

One of the first and second rings may be an inner ring and the other may be an outer ring.

As the rolling elements, various rolling elements such as a rotor and a ball can be used.

The axial movement prevention part may include: a bearing groove formed in a surface of the first ring opposite to the first circumferential surface; a circumferential surface groove formed in a first circumferential surface at a position corresponding to the bearing groove; and a gap preventing ring RR inserted across the circumferential groove and the bearing groove.

The height h of the gap preventing ring may be less than or equal to the depth of the circumferential groove.

Optionally, the height of the gap preventing ring may be greater than the depth of the bearing groove.

The second circumferential surface may be provided with a radially protruding second bearing boss so as to interfere with the other axial side of the second ring.

The second circumferential surface may be provided with a bearing fixing portion which interferes with one side in the axial direction of the second ring.

The axial-movement preventing portion may be assembled by fixing the bearing to the second circumferential surface through the second bearing boss and the bearing fixing portion.

The first circumferential surface may be provided with a first bearing boss protruding radially so as to interfere with one side in the axial direction of the first ring.

As an example, the bearing fixing portion may include: an annular groove formed in the second circumferential surface at a position not opposed to the second ring; and a retainer ring inserted into the annular groove, whereby a retainer ring portion protruding radially from the annular groove may interfere with one side in the axial direction of the second ring.

As another example, the bearing fixing portion may include a plastic working portion.

The plastic working portion may be a portion that is plastically deformed to protrude in a radial direction of the second circumferential surface in a state where the bearing is inserted into the second bearing boss in the axial direction.

The plastic working portion may be formed by caulking.

In an embodiment, the housing 80 includes an input member 10, the input member 10 is rotatably supported with respect to the housing 80 and receives a driving force from an engine, and a circumferential surface of the housing 80 side may be provided at the input member 10.

The rotor hub 43 includes a central shaft extension 450 extending in an axial direction from a central portion of the rotor hub 43, and a circumferential surface of the rotor hub 43 side may be provided at the central shaft extension 450.

The circumferential surface of the central shaft extension 450 may be disposed radially inward of the circumferential surface of the input member 10.

In other embodiments, the housing 80 includes an axial protrusion 823 protruding axially from the housing 80, and the circumferential surface of the housing 80 side may be disposed on the axial protrusion 823.

The rotor hub 43 includes a hub boss 46 which is connected to the rotor hub 43 so as to be restrained from rotation and which extends in a radial direction, an axial extension 464 which extends axially from the hub boss 46 is provided radially inward of the hub boss 46, and a circumferential surface on the rotor hub 43 side may be provided on the axial extension 464.

The circumferential surface of the axial protrusion 823 may be disposed radially inward of the circumferential surface of the axial extension 464.

Effects of the invention

According to the hybrid drive module of the present invention, by controlling the axial clearance of the rotor hub with respect to the housing, the operation stability of the hybrid drive module can be improved.

According to the invention, the thrust bearing action of the rolling bearing, in particular the ball bearing, is used as such when controlling the axial play of the rotor hub relative to the housing, so that no additional further thrust bearing elements are required.

According to the present invention, since no additional other thrust bearing element is required, the number of parts and the number of assembly processes can be minimized while also preventing relative movement between the housing and the rotor hub.

The specific matters for carrying out the present invention will be described below, together with specific effects of the present invention other than the above effects.

Drawings

Fig. 1 is a conceptual diagram of a first embodiment of a hybrid drive module according to the invention.

Fig. 2 is a side sectional view showing a process of disposing a housing and a spring damper at a rotor hub.

Fig. 3 is a diagram showing a transmission path of the driving force in the diagram of fig. 1.

Fig. 4 is a view showing a flow control direction of a fluid in the view of fig. 1.

Fig. 5 is an enlarged view of the first embodiment of the axial-movement prevention portion (section E of fig. 4).

Fig. 6 is an exploded view of the axial movement prevention portion of fig. 5.

Fig. 7 is an enlarged view of a second embodiment of the axial-movement prevention portion (section E of fig. 4).

Fig. 8 is an enlarged view of a third embodiment of the axial-movement prevention portion (section E of fig. 4).

Fig. 9 is an enlarged view of a fourth embodiment of the axial-movement prevention portion (section F of fig. 3).

Reference numerals:

9: spring damper, 10: input part, 101: first input member annular groove, 102: spline, 105: first input member boss, 107: second input member boss, 108: second input member annular groove, 109: second input member snap ring, 110: third input member annular groove, 12: input board, 13: first input member snap ring, 20: engine clutch, 21: first piston plate, 22: first clutch pack, 23: first carrier, 40: motor, 41: stator (stator), 42: rotor (rotor), 420: retainer, 43: rotor hub, 44: rotor holder, 441: radial support, 442: axial support portion, 45: hub plate, 450: central shaft extension 451: hub inner shaft, 453: center shaft boss, 454: first central shaft annular groove, 455: center shaft snap ring, 458: plastic working portion (caulking portion), 459: second central shaft annular groove, 46: hub boss (ridge), 464: axial extension, 465: radially outer and inner peripheral surfaces 466: radially inner peripheral surface, 467: flow holes, 468: sliding projection, 469: raised snap ring, 470: raised snap ring, 471: raised annular groove, 4691: first sealing face, 4692: second sealing face, 49: circle snap ring (protruding fixing part), 50: fluid clutch, 51: impeller, 52: rear cover, 53: bolt, 54: turbine, 55: turbine plate, 56: reactor, 57: one-way clutch, 60: lockup clutch, 61: second piston plate, 62: second clutch pack, 64: output plate, 70: output member, 75: fixed end, 80: a housing 821: first axial projection 822: first seal groove, 823: second axial projection, 824: second seal groove, 828: housing boss, 829: housing annular groove, 83: first flow passage, 84: second flow channel, 90: elastomer, 91: first elastomer, 92: second elastic body, 93: third elastomer, 94: fourth elastomer, S1: first sealing member, S2: second sealing member, S3: third sealing members B1, B2, B3, B4, B5, B6: bearing, B21: second inner wheel, B22: second outer wheel, B23: second rolling elements, B24: second bearing grooves, B31: third inner wheel, B32: third outer wheel, B33: third rolling element, B34: third bearing grooves, A1, A2, A3, A4: space, RR: gap preventing ring

Detailed Description

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 modifications may be applied thereto, and the present invention may be realized in different forms from each other. The present embodiment is provided only for completing the disclosure of the present invention and for fully explaining the scope of the present invention to a person having ordinary skill. Therefore, it is to be understood that the present invention is not limited to the embodiments disclosed below, but includes not only the structures of the embodiments that are substituted for or attached to each other and that are different from the structures of any one of the embodiments, but also all modifications, equivalents, and alternatives included in the technical idea and scope of the present invention.

It should be understood that the drawings are for ease of understanding only the embodiments disclosed in the present specification, and are not intended to limit the technical ideas disclosed in the present specification by the drawings, but are to include all modifications, equivalents, and even substitutes included in the concept and technical scope of the present invention. The constituent elements in the drawings may be shown in an enlarged or reduced size or thickness in consideration of easy understanding and the like, but the scope of the present invention is not limited thereto.

The terminology used in the description presented herein is for the purpose of describing particular embodiments only or is not intended to be limiting of the invention. Then, where there is no other meaning explicitly in the text, the singular includes the plural. In the specification, terms "comprises," "comprising," and "including" are intended to specify the presence of stated features, integers, steps, operations, elements, components, or groups thereof. That is to say, the terms "comprising," "including," "forming," and the like in the specification should be understood to not exclude one or more other features or numbers, a priori the existence or additional possibilities of steps, operations, components, devices, or combinations thereof.

The terms including ordinal numbers of first, second, etc., may be used in describing various elements, however, the elements are not limited to the terms. The term is used only for the purpose of distinguishing one component from another.

When it is mentioned that a certain component is "connected" or "connected" to another component, it may be directly connected or connected to the other component, but it is understood that another component may be present in between. In contrast, when reference is made to a component being "directly connected" or "directly connected" to another component, it is to be understood that there are no other components in between.

When referring to a certain component as being "on" or "under" other components, it is understood that other components may be present in the middle as well as being disposed not only directly above the other components.

Unless otherwise defined, 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 this invention belongs. The same terms defined in the dictionary generally used should be construed to have meanings consistent with those of the related art, and should not be construed to have ideal or excessively formal meanings when not explicitly defined in the present application.

The hybrid driving module of the embodiment is symmetrical about an axis, and thus only half of the axis is shown for convenience of drawing. For convenience of explanation, a direction along a longitudinal direction of an axis constituting a rotation center of the hybrid drive module is referred to as an axial direction. That is, the front-rear direction or the axial direction is a direction parallel to the rotation axis, and the front (front side) means a direction of a power source, for example, a direction toward the engine side, and the rear (rear side) means another direction, for example, a direction toward the transmission side. Thus, front (front) refers to the front facing surface and rear (rear) refers to the rear facing surface.

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

The circumferential direction or circumferential direction refers to a direction around the circumference of the rotation axis. The outer periphery refers to the outer side edge and the inner periphery refers to the inner side edge. Accordingly, the outer peripheral surface means a surface facing away from the rotation axis, and the inner peripheral surface means a surface facing toward the rotation axis.

The circumferential side surface means a surface in which the normal line of the surface faces in the circumferential direction.

Hybrid drive Module

The structure of the hybrid drive module of the embodiment is explained below with reference to fig. 1 to 4.

The hybrid drive module of the embodiment includes: an input member 10 connected to an output side of the engine for inputting an output of the engine; and an output member 70 that transmits the driving force of the motor or the driving force of the motor and the engine to the transmission.

The output of the engine is input to the input member 10 via the spring damper 9. The spring damper 9 is a torsional vibration damper. The spring damper 9 engages with the spline 102 of the input member 10 to restrict rotation to each other. The spring damper 9 dampens the engine output from shaking to prevent vibration.

The spline 102 is provided on the axially forward outer peripheral surface of the input member 10. Then, an input plate 12 extending radially outward is connected to the axially rear side outer peripheral surface of the input member 10. The input plate 12 is integrally fixed to the input member 10 by welding or the like, and thus integrally rotates with the input member 10.

An engine clutch 20 is connected to a radially outer end portion of the input member 10. The engine clutch 20 is disposed between the rotor hub 43 and the input member 10 so as to transmit or not transmit the output of the engine to the rotor hub 43.

The hybrid drive module is provided with a motor 40. The motor 40 includes: an annular stator 41, and an annular rotor 42 disposed radially inward of the stator 41. The rotor 42 rotates by electromagnetic interaction with the stator 41.

The stator 41 is fixed to the housing 80. The housing 80 is disposed axially forward of the motor 40 and extends radially. The input member 10 is rotatably supported at a radially inner end portion of the housing 80 by a first bearing B1. The first bearing B1 is fixed in the axial direction by a first input member retainer ring 13 inserted into a first input member annular groove 101 provided on the outer peripheral surface of the input member 10. The first input member boss 105 of the input member 10 supports the inner ring of the first bearing B1 axially rearward, and the first input member snap ring 13 supports the inner ring of the first bearing B1 axially forward. The outer ring of the first bearing B1 is supported by the housing 80 in the axial direction and the radial direction. Thus, the input member 10 is supported radially and axially with respect to the housing 80 by the first bearing B1. That is, the input member 10 is restrained from moving axially relative to the housing 80 by the first bearing B1, the first input member boss 105, and the first input member snap ring 13.

A first sealing member S1 is provided between the input member 10 and the housing 80 to prevent fluid inside the housing 80 from leaking to the outside.

The rotor 42 is fixed to the rotor hub 43. The rotor hub 43 includes: a rotor holder 44 for holding the rotor 42, and a hub plate 45 extending radially inward from the rotor holder 44.

The rotor holder 44 includes: a radial support portion 441 for supporting the inner peripheral surface of the rotor 42, and an axial support portion 442 for supporting the axial rear end portion of the rotor 42. The radial support 441 may have a cylindrical shape extending in an axial direction. The axial support portion 442 may have a flange shape extending radially outward at an axially rear end portion of the radial support portion 441.

The radial support portion 441 supports the inner peripheral surface of the rotor 42, and the axial support portion 442 supports the axially rear end portion of the rotor 42. An axial support portion extending in the radial direction is not formed at the front end portion of the radial support portion 441. As a result, the rotor 42 is supported so that the inner peripheral surface of the rotor 42 faces the outer peripheral surface of the radial support portion 441 from the axial front side to the rear side Fang Waicha, and the axial rear end portion of the rotor 42 faces the front side of the axial support portion 442.

A boss 46 is coupled to a front end of the radial support portion 441. The boss protrusions 46 are coupled to the front end portions of the radial supporting portions 441 in a shape to restrict rotation from each other. The hub projection 46 extends radially outward than the radial support portion 441, and thereby the radially outer end portion of the hub projection 46 axially supports the front end portion of the rotor 42. After the boss 46 is inserted into the radial supporting portion 441, a boss snap ring 49 as a boss fixing member is inserted into a groove formed in an inner peripheral surface of the radial supporting portion 441 in front of the boss 46 to prevent the boss 46 from coming off axially forward.

The hub plate 45 is connected to the rotor holder 44 near the axial center portion of the radial support portion 441. The hub plate 45 has a shape extending radially inward from the inner peripheral surface of the radial support portion 441, and has a disk-like shape. A center shaft extension 450 extending forward is provided at a center portion of the radius of the hub plate 45, and the center shaft extension 450 and the input member 10 are supported so as to be rotatable relative to each other by a third bearing B3. For this, a central shaft boss 453 is provided at the central shaft extension 450 to restrict the rear position of the third bearing B3 to the input member 10, and a second input member boss 107 is provided at the input member 10 to restrict the front position of the third bearing B3. The third bearing B3 supports the input member 10 axially and radially with respect to the central shaft extension 450 of the hub plate 45.

The engine clutch 20 is provided radially inward of the radial support portion 441, and corresponds to a space axially forward of the hub plate 45. The engine clutch 20 includes a first clutch pack 22 including a friction plate or friction material and a first carrier 23. A first carrier 23 may be provided at the hub plate 45 of the rotor hub 43. The first carrier 23 is connected to the rotor hub 43 in a rotation-limiting manner and rotates integrally with the rotor hub 43. The radially outer side of the first clutch pack 22 is connected to the first carrier 23 and the radially inner side is connected to the input member 10 via the input plate 12. The clutch plates connected to the first carrier 23 and the clutch plates connected to the input member 10 are alternately arranged with a friction material interposed therebetween.

A first piston plate 21 is disposed axially forward of the first clutch pack 22. If the first piston plate 21 axially pressurizes the first clutch pack 22, the input plate 12 and the first carrier 23 are connected to restrict rotation to each other. Thus, the output of the engine transferred to the input plate 12 may be transferred to the rotor hub 43 via the engine clutch 20. If the first piston plate 21 does not pressurize the first clutch pack 22, the input plate 12 and the first carrier 23 do not restrict rotation with each other. Thus, the engine output is transmitted only to the input plate 12 and not to the rotor hub 43.

A hub boss (ridge) is disposed axially forward of the first piston plate 21. Referring to fig. 2, the hub protrusion 46 may be a substantially disk-shaped or disc-shaped member having a central portion opened and extending in a radial direction.

The first piston plate 21 of the engine clutch 20 is disposed axially rearward of the hub boss 46. The hub boss 46 includes: a radially outer inner peripheral surface 465 extending radially outward and axially rearward, and a radially inner outer peripheral surface 466 extending radially inward and axially rearward. The radially inner peripheral surface 466 is provided with an axial extension 464 extending rearward from the center end of the hub projection 45. The first piston plate 21 extends radially. An outer peripheral surface of a radially outer end portion of the first piston plate 21 is in contact with the radially outer inner peripheral surface 465 so as to be slidable in the axial direction, and an inner peripheral surface of a radially inner end portion of the first piston plate 21 is in contact with the radially inner outer peripheral surface 466 so as to be slidable in the axial direction.

A slide protrusion 468 that extends further axially rearward is provided at an end of the axially extending portion 464 provided radially inward of the hub boss 46. The sliding protrusion 468 may be disposed near the radially inner outer peripheral surface 466. A sliding groove having a shape complementary to the sliding protrusion 468 is provided in the first piston plate 21. Thus, the first piston plate 21 and the hub boss 46 are allowed to slide in the axial direction while restricting rotation.

The boss 46 is provided with a flow hole 467 for fluid to flow into the engine clutch operation chamber, which is defined by the first piston plate 21, the rear surface of the boss 46, the radially outer inner peripheral surface 465, and the radially inner peripheral surface 466.

A first sealing surface 4691 and a second sealing surface 4692 are provided on the radially outer side and the radially inner side of the hub boss 46 than the flow hole 467, respectively, and are radially opposed to the first axial protrusion 821 and the second axial protrusion 823 of the housing 80, respectively.

Further, a first seal groove 822 is provided at an outer peripheral surface portion of the first axial protruding portion 821 of the housing 80 facing the first seal surface 4691, and a second seal member S2 is inserted into the first seal groove 822. A second seal groove 824 is provided at a portion of the outer peripheral surface of the second axial projection 823 of the housing 80 facing the second seal surface 4692, and a third seal member S3 is inserted into the second seal groove 824.

When the first sealing surface 4691 and the second sealing surface 4692 are in contact with the first axial projection 821 and the second axial projection 823, respectively, sandwiching the second seal S2 and the third seal S3, respectively, a predetermined space A1 for sealing is provided between the housing 80 and the hub boss 46.

A first flow passage 83 for supplying oil to the space A1 is formed in the housing 80. The first flow passage 83 extends radially from the radially outer end of the housing 80 to a predetermined position between the first axial protrusion 821 and the second axial protrusion 823, and communicates with the space A1.

As shown in a "clutch actuation" path shown in fig. 4, when fluid flows into the front space A1 of the first piston plate 21 through the housing 80, the first piston plate 21 moves axially rearward relative to the hub boss 46, thereby pressurizing the first clutch pack 22. That is, when hydraulic pressure is supplied to the first flow passage 83, pressurized oil is supplied to the engine clutch operation chamber through the space A1 and the flow hole 467, and at this time, the first piston plate 21 moves rearward while pressurizing the first clutch pack 22, so that the engine clutch 20 connects the input plate 12 and the rotor hub 43 to each other for rotation restriction. Then, as shown in an "Engine power" path shown in fig. 3, the rotational force of the Engine is transmitted to the rotor hub 43.

As shown in the "clutch actuation" path shown in fig. 4, fluid flows through the housing 80 into the front space A1 of the first piston plate 21, and when the first piston plate 21 pressurizes the first clutch pack 22, the pressure of the first piston plate 21 pressurizing the first clutch pack 22 pushes the rotor hub 43 itself rearward. Accordingly, when hydraulic pressure is supplied to operate the engine clutch 20 as shown in fig. 4, the rotor hub 43 and the hub boss 46 form a room for rearward movement with respect to the housing 80, the input member 10, and the input plate 12. Thus, the possibility of the sliding protrusion 468 of the hub protrusion 46 interfering with the input plate 12 cannot be excluded. The present invention provides a structure for preventing axial clearance of a rotor hub 43.

In addition, a second flow passage 84 for supplying fluid to the rear space A2 of the first piston plate 21 is formed at the housing 80. The second passage 84 extends radially from the radially outer end of the housing 80 to a position corresponding to the second axial projection 823, and extends axially along the second axial projection 823, communicating with the rear space A2. Since the second flow passage 84 is formed at different positions in the circumferential direction of the first flow passage 83 and the housing, independent flow passages are formed in the housing 80 so as not to communicate with each other.

As shown in the "clutch & Rotor cooling" path of fig. 4, when fluid flows into the rear space A2 of the first piston plate 21 through the second flow passage 84 of the housing 80, the first piston plate 21 moves axially forward relative to the hub boss 46 without pressurizing the first clutch pack 22. The fluid (oil) flowing into the rear space A2 through the second flow passage 84 cools and/or lubricates the bearings B1, B2, B3, and cools and/or lubricates the engine clutch 20, and cools the rotor 42.

The radially inner side of the hub projection 46 is rotatably connected with respect to the housing 80. For this purpose, a second bearing B2 is interposed between the inner peripheral surface of the axially extending portion 464 provided radially inward of the boss 46 and the outer peripheral surface of the second axially protruding portion 823 provided radially inward of the housing 80. A boss 469 for restricting the rear position of the second bearing B2 is provided at the axially extending portion 464 of the boss 46. Thus, the outer race of the second bearing B2 supports the boss 46 in the radial and axial directions. A housing boss 828 for restricting the forward position of the second bearing B2 is provided in the housing 80. Accordingly, the inner ring of the second bearing B2 supports the housing 80 in the radial and axial directions. Thus, the hub projection 46 is supported radially and axially forward relative to the housing 80.

In addition, a holder 420 for protecting and supporting the rotor 42 may be provided axially forward and/or rearward of the rotor 42. The outboard end of the hub boss 46 may interface with the retainer 420.

According to the structure of the hub boss 46 as described above, the first piston plate 21 is provided together in the process of providing the hub boss 46 to the rotor hub 43, and at the same time, the hub boss 46 fixes the rotor 42. From another point of view, the rotor 42 may limit the hub protrusion 46 from moving axially rearward.

That is, the hub protrusion 46 may be restricted from being separated axially forward by the hub snap ring 49, and may be restricted from moving axially rearward by the radial support portion 441 and/or the rotor 42.

Due to manufacturing errors of the radial supporting portion 441 and the hub projection 46, etc., a gap may occur in the axial direction of the hub projection 46. That is, vibrations may occur when the boss 46 moves in the axial direction, which may become a cause of noise.

For this purpose, the hybrid drive module may further include an elastic body 90 to elastically press the hub boss 46 axially forward to the hub snap ring 49 side.

The elastic body 90 may be provided anywhere as long as the boss 46 is pushed toward the boss collar 49 side in place. Fig. 1 also shows a configuration in which the first elastic body 91 to the fourth elastic body 94 are provided at different positions from each other, and the hub protrusion 46 is pressed toward the hub snap ring 49. However, for convenience of explanation, the elastic body 90 may include only any one of the first to fourth elastic bodies 91 to 94. Of course, the elastic body 90 may include 2 or more elastic bodies 90 among the first to fourth elastic bodies 91 to 94.

The first elastic body 91 and/or the second elastic body 92 provide elastic force in the axial expansion direction.

First, the first elastic body 91 may be configured to elastically press the boss 46 forward in the front direction of the rotor 42 to push the boss 46 toward the boss collar 49 side. The second elastic body 92 may be configured to elastically press the rotor 42 and the hub protrusion 46 in the rear-front direction of the rotor 42 so as to push the hub protrusion 46 toward the hub snap ring 49 side.

Accordingly, the boss 46 is abutted against the boss collar 49 side by the first elastic body 91 and/or the second elastic body 92, so that vibration or rattling does not occur, and the rotor 42 can be firmly supported in the axial direction between the axial support portion 442 and the radially extending portion 462.

Next, the elastic body 90 may be configured to elastically press the piston setting portion 464 forward on the engine clutch 20 side to push the boss 46 toward the boss collar 49 side. The third elastic body 93 and the fourth elastic body 94 shown in fig. 1 belong to this.

A third elastic body 93 may be interposed between the front end of the first carrier 23 and the hub protrusion 46. Then, the third elastic body 93 exerts elastic force that elastically returns in the direction of axial expansion. Accordingly, the first carrier 23 and the boss 46 are elastically pressurized in a direction away from each other by the third elastic body 93. Thereby, the hub protrusion 46 is pushed toward the hub snap ring 49 side.

A fourth elastomer 94 may be provided on the first clutch pack 22. The fourth elastic body 94 may function as a return spring of the first piston plate 21. The fourth elastic body 94 is interposed between the plurality of clutch plates so as to open the clutch plates in a direction in which the first clutch pack 22 is axially opened, and the elastic force of the fourth elastic body 94 pushes the first piston plate 21 toward the boss 46 side. In this way, the hub projection 46 is elastically pressed to the hub snap ring 49 side.

The elastic bodies 90, i.e., the first elastic body 91 to the fourth elastic body 94 may be annular coil springs or wave washers. However, the type of the spring is not limited thereto.

The rear cover 52 is fixed to the axial support portion 442 of the rotor holder 44 by bolts 53. The rear cover 52 extends radially inward from the rotor holder 44. The radially inner end of the rear cover 52 is connected to an oil pump of the transmission. An impeller 51 is provided in front of the rear cover 52.

An output member 70 is provided between the hub plate 45 and the rear cover 52. A spline is formed on the inner peripheral surface of the output member 70, and is connected to an input shaft of a transmission (not shown). The output member 70 is integrally connected to the turbine plate 55. The turbine plate 55 extends radially. A turbine 54 axially opposed to the impeller 51 is provided behind the turbine plate 55.

A fixed end 75 is disposed between the rear cover 52 and the output member 70. A spline is formed on the inner peripheral surface of the fixed end 75, and is connected to a fixed shaft of a transmission (not shown).

A reactor 56 is disposed between the impeller 51 and the turbine 54. The reactor 56 is connected to the fixed end 75 by a one-way clutch 57. The impeller 51, turbine 54, and reactor 56 constitute a torque converter that multiplies the torque of the motor 40 and then transmits the multiplied torque to the output member 70.

The output member 70 is rotatably supported to the fixed end 75 by a fourth bearing B4. The rear cover 52 is rotatably supported to the fixed end 75 by a fifth bearing B5. At the same time, the hub plate 45 and the output member 70 are rotatably supported with each other by a sixth bearing B6.

A lock clutch 60 is provided on the inner peripheral surface of the rotor holder 44 rearward of the hub plate 45. The output member 70 is integrally connected to the output plate 64 and integrally rotates. The output plate 64 extends radially from the output member 70 toward the lockup clutch 60.

The lockup clutch 60 includes a second clutch pack 62 having friction plates or friction members. The second clutch pack 62 is disposed between the rotor hub 43 and the output plate 64.

A second piston plate 61 is disposed axially forward of the second clutch pack 62. If the second piston plate 61 axially pressurizes the second clutch pack 62, the rotor hub 43 and the output plate 64 are connected to restrict rotation to each other. Thereby, the rotational force of the rotor hub 43 can be transmitted to the output plate 64 and the output member 70 via the lockup clutch 60. If the second piston plate 61 does not pressurize the second clutch pack 62, the rotor hub 43 and output plate 64 do not restrict rotation to each other. Thereby, the rotational force of the rotor hub 43 is transmitted to the output member 70 through the torque converter.

The second piston plate 61 extends radially. An outer circumferential surface of the second piston plate 61 on the radially outer side faces an inner circumferential surface of the rotor holder 44, and is slidably contacted in the axial direction. An inner circumferential surface of the second piston plate 61 on the radially inner side faces an outer circumferential surface of the output member 70, and is slidably contacted in the axial direction.

As shown in "Inlet (Inlet)" of fig. 4, when fluid flows into the rear space A3 of the second piston plate 61 through the transmission, the second piston plate 61 moves axially forward with respect to the rotor holder 44, and the second clutch pack 62 is not pressurized.

As shown in "L/up clutch actuation (L/up clutch actuating)" of fig. 4, if fluid flows into the front space A4 of the second piston plate 61 through the transmission, the first piston plate 21 moves axially rearward with respect to the rotor holder 44, thereby pressurizing the second clutch pack 62.

Next, the driving operation of the hybrid driving module is described with reference to fig. 3.

First, when the engine does not provide driving force and the motor 40 provides driving force, the engine clutch 20 does not transmit power between the input plate 12 and the first carrier 23. When the torque of the motor 40 is multiplied and needs to be transmitted to the transmission, that is, when the rotational speed of the motor 40 is greater than the rotational speed of the output member 70, the torque of the motor 40 is multiplied by the torque converter and then transmitted to the output member 70. As a result, when the rotational speed of the output member 70 approaches the rotational speed of the motor 40, the lockup clutch 60 is activated, and the rotor hub 43 and the output member 70 are directly connected.

On the one hand, when the engine or the engine and the motor 40 provide driving force, the engine clutch 20 transmits power between the input plate 12 and the first carrier 23. In this way, the torque of the engine and the motor 40 are added and transmitted to the output member 70 through the torque converter. Torque of the engine and the motor 40 may be multiplied by the torque converter and then transferred to the output member 70, and if the Speed Ratio (SR) of the rotor hub 43 and the output member 70 is 1:1, the rotor hub 43 and the output member 70 are directly connected through the lockup clutch 60. That is, the torque damper and the lockup clutch 60 constitute a power transmission portion between the rotor hub 43 and the output member 70 for transmitting power therebetween.

According to the hybrid drive module of the embodiment, the torque of the engine is transmitted to the rotor hub 43 through the input plate 12, the engine clutch 20, and the first carrier 23, and the hub boss 46 is not in the torque transmission path.

[ axial gap prevention Structure of rotor hub ]

The possibility of the rotor hub 43 and the hub projection 46 being axially clearance with respect to the housing 80 and the input member 10 cannot be excluded. In an embodiment, a structure for preventing such axial clearance is provided.

In particular, in providing such a gap preventing structure, the present invention supports the relative rotation between the rotor hub 43 and the input member 10 using the mounting structure of the third bearing B3 or the mounting structure of the second bearing B2 for supporting the relative rotation between the hub boss 46 and the housing 80, and thus, no additional other thrust bearing elements are required.

An axial movement preventing portion for preventing the rotor hub 43 (including the concept of a hub protrusion) from moving axially due to a clearance in the axial direction with respect to the housing 80 (including the concept of an input member) will be described with reference to the first embodiment shown in fig. 5 and 6 and the second to fourth embodiments shown in fig. 7 to 9, respectively.

The axial movement prevention part prevents the rotor hub 43 from moving forward with respect to the housing 80 and also prevents rearward movement. That is, the axial movement prevention portion eliminates or minimizes the axial clearance of the rotor hub 43 relative to the housing 80.

< first embodiment >

Referring to fig. 5 and 6, the axial movement prevention portion according to the first embodiment is reflected in the mounting structure of the third bearing B3.

The third bearing B3 includes: an annular third inner ring B31 disposed radially inward; a third outer ring B32 radially opposed to the third inner ring B31 and arranged radially outward of the third inner ring B31; and a third rolling element B33 interposed between the third inner ring B31 and the third outer ring B32. The third rolling elements B33 may be balls, and the third bearing B3 may be a ball bearing. The third bearing B3 may support rotation in the radial and axial directions.

The central shaft extension 450 of the hub plate 45 of the rotor hub 43 extends axially forward from the hub plate 45. A center shaft boss 453 is provided on an outer peripheral surface of the center shaft extension 450. The central shaft extension 450 has a front diameter smaller than a rear diameter based on the central shaft boss 453.

The inner circumferential surface of the third inner ring B31 is in radial contact with the outer circumferential surface of the central shaft extension 450. Further, the rear end portion of the third inner ring B31 is in facing contact with the center shaft boss 453 in the axial direction.

In a state where the third inner ring B31 is in contact with the center shaft boss 453, a center shaft snap ring 455 is provided in front of the third inner ring B31. A first central shaft annular groove 454 is formed in the outer peripheral surface of the central shaft extension 450 immediately in front of the third inner ring B31, and the central shaft snap ring 455 is inserted into the first central shaft annular groove 454. That is, the position of the third inner ring B31 is restricted rearward by the central shaft boss 453 and forward by the first central shaft annular groove 454 and the central shaft snap ring 455.

A hollow portion is provided behind the input member 10. Further, the central shaft extension 450 is accommodated in a hollow portion formed at the rear of the input member 10. An inner peripheral surface for defining the hollow portion is formed at the rear portion of the input member 10. A second input member boss 107 is formed on the inner peripheral surface of the input member 10. The inner diameter of the front side of the input member 10 is smaller than the inner diameter of the rear side of the input member, based on the second input member boss 107.

The outer peripheral surface of the third outer ring B32 is in radial contact with the inner peripheral surface of the input member 10. The front end portion of the third outer ring B32 is in axially facing contact with the second input member boss 107.

A third bearing groove B34 is formed in the outer peripheral surface of the third outer ring B32. In a state where the third outer race B32 is in contact with the second input member boss 107, the third input member annular groove 110 is formed at a portion of the inner peripheral surface of the input member 10 facing the third bearing groove B34. Thus, the third bearing groove B34 and the third input member annular groove 110 are connected in radial communication.

A gap preventing ring RR is inserted between the third bearing groove B34 and the third input member annular groove 110. The gap preventing ring RR may be a C-shaped ring capable of being elastically deformed to increase or decrease the radius.

The depth of the third input member annular groove 110 measured in the radial direction may be equal to or greater than the height h of the gap preventing ring RR measured in the radial direction. Conversely, the depth of the third bearing groove B34 may be smaller than the height of the gap preventing ring RR.

Referring to fig. 6, a mounting sequence of the third bearing B3 reflecting the axial movement prevention portion will be described.

First, the third inner ring B31 of the third bearing B3 is externally inserted to the outer peripheral surface of the center shaft extension 450 until reaching the center shaft boss 453. Then, the center shaft snap ring 455 is inserted into the first center shaft annular groove 454 immediately in front of the third inner ring B31.

Next, the gap preventing ring RR is inserted into the third input member annular groove 110 provided on the inner peripheral surface of the input member 10. During the insertion of the gap preventing ring RR into the third input member annular groove 110, the gap preventing ring RR is elastically deformed to reduce its outer diameter, and is elastically restored and expanded in outer diameter at the moment of reaching the third input member annular groove 110, thereby being inserted into the third input member annular groove 110. In a state where the gap preventing ring RR is inserted into the third input member annular groove 110, a radially inner end portion of the gap preventing ring RR protrudes radially inward from an inner peripheral surface of the input member 10.

In this state, the input member 10 is externally inserted to the outer peripheral surface of the center shaft extension 450. Then, the third outer ring B32 of the third bearing B3 elastically deforms the gap preventing ring RR to increase the radius thereof. Since the depth of the third input member annular groove 110 is equal to or greater than the height of the gap preventing ring RR, the gap preventing ring RR can be completely inserted into the third input member annular groove 110. For smoother fitting, a tapered or chamfered shape may be formed at the corner between the front face and the outer peripheral face of the third outer ring B32.

The gap preventing ring RR having a larger radius is inserted into the third bearing groove B34 by elastically restoring to a smaller inner diameter at the moment of reaching the third bearing groove B34. In a state where the gap preventing ring RR is inserted into the third bearing groove B34, a radially outer end portion of the gap preventing ring RR is inserted into the third input member annular groove 110.

Thereby, as shown in fig. 5, the installation of the third bearing B3 is completed.

In this state, when hydraulic pressure is supplied to the first space A1 in order to actuate the engine clutch 20, the rotor hub 43 tries to move rearward due to the rearward pressure received by the first piston plate 21, but at this time, the center shaft retainer ring 455 interferes with the third inner ring B31, the third inner ring B31 interferes with the third rolling element B33, the third rolling element B33 interferes with the third outer ring B32, the third outer ring B32 interferes with the gap preventing ring RR, and the gap preventing ring RR interferes with the input member 10, thereby preventing rearward movement of the rotor hub 43.

In order to actuate the lockup clutch 60, when hydraulic pressure is supplied to the fourth space A4, the rotor hub 43 tries to move forward, but at this time, the center shaft boss 453 interferes with the third inner ring B31, the third inner ring B31 interferes with the third rolling element B33, the third rolling element B33 interferes with the third outer ring B32, the third outer ring B32 interferes with the gap preventing ring RR, and the gap preventing ring RR interferes with the input member 10, thereby preventing the rotor hub 43 from moving forward.

As described above, the clearance prevention ring RR, the third bearing groove B34, and the third input member annular groove 110 serve as axial movement prevention portions that prevent the rotor hub 43 from being cleared in the front-rear direction.

< second embodiment >

For the second embodiment, differences from the first embodiment will be mainly described.

Referring to fig. 7, unlike the first embodiment in which a first center shaft annular groove 454 and a center shaft snap ring 455 are applied as bearing fixing portions, in the second embodiment, a so-called caulking portion 458 using plastic working portions is used as bearing fixing portions, which is different from the first embodiment.

A caulking portion 458 is formed in front of the third wheel in a state where the third inner ring B31 is in contact with the center shaft boss 453. The rivet 458 results in an enlarged outer diameter of the central shaft extension 450. Therefore, the position of the third inner ring B31 is restricted from moving forward by the caulking portion 458, which is the plastic working portion.

In this method of mounting the third bearing B3 reflecting the axial movement prevention portion, a portion different from the first embodiment will be described.

In the second embodiment, the third inner ring B31 of the third bearing B3 is externally inserted to the outer peripheral surface of the center shaft extension 450 until reaching the center shaft boss 453, and then the center shaft extension 450 immediately before the third inner ring B31 is swaged to fix the front of the third inner ring B31, which is different from the first embodiment.

According to the second embodiment, when hydraulic pressure is supplied to the first space A1 in order to operate the engine clutch 20, the rotor hub 43 tries to move rearward due to the first piston plate 21 receiving rearward pressure, but at this time, the caulking portion 458 interferes with the third inner ring B31, the third inner ring B31 interferes with the third rolling body B33, the third rolling body B33 interferes with the third outer ring B32, the third outer ring B32 interferes with the gap preventing ring RR, and the gap preventing ring RR interferes with the input member 10, thereby preventing rearward movement of the rotor hub 43.

< third embodiment >

Referring to fig. 7, the third embodiment is most different from the first embodiment in that a gap preventing ring RR is applied to the third inner ring B31 side. Due to these differences, there are other differences. The third embodiment will be described below focusing on the difference.

The second input member snap ring 109 is mounted behind the third outer race B32 in a state where the third outer race B32 is in contact with the second input member boss 107. A second input member annular groove 108 is formed immediately behind the third outer race B32 on the inner peripheral surface of the input member 10, and the second input member snap ring 109 is inserted into the second input member annular groove 108. That is, the position of the third outer race B32 is limited forward by the second input member boss 107 and rearward by the second input member annular groove 108 and the second input member snap ring 109. Of course, the front end portion of the input member 10 may be caulking-processed to form a bearing fixing portion as in the second embodiment.

A third bearing groove B34 is formed in the inner peripheral surface of the third inner ring B31. In a state where the third inner ring B31 is in contact with the center shaft boss 453, a second center shaft annular groove 459 is formed in a portion of the outer peripheral surface of the center shaft extension 450 facing the third bearing groove B34. Thereby, the third bearing groove B34 is connected in radial communication with the second center shaft annular groove 459.

A gap preventing ring RR is inserted between the third bearing groove B34 and the second center shaft annular groove 459.

The depth of the second central axial annular groove 459 measured in the radial direction may be equal to or greater than the height h of the gap preventing ring RR measured in the radial direction. Conversely, the depth of the third bearing groove B34 may be smaller than the height of the gap preventing ring RR.

A mounting sequence of the third bearing B3 reflecting the axial movement prevention portion will be described.

First, the third outer ring B32 of the third bearing B3 is inserted into the inner peripheral surface of the input member 10 until reaching the second input member boss 107. Then, the second input member snap ring 109 is inserted into the second input member annular groove 108 immediately behind the third outer race B32.

Next, the gap preventing ring RR is inserted into the second central shaft annular groove 459 provided on the outer peripheral surface of the central shaft extension 450. During the insertion of the gap preventing ring RR into the second central shaft annular groove 459, the gap preventing ring RR is elastically deformed to increase its inner diameter, and is elastically restored and reduced in inner diameter at the moment of reaching the second central shaft annular groove 459, thereby being inserted into the second central shaft annular groove 459. In a state where the gap preventing ring RR is inserted into the second central shaft annular groove 459, a radially outer end portion of the gap preventing ring RR protrudes radially outward from an outer peripheral surface of the central shaft extension 450.

In this state, the input member 10 is externally inserted to the outer peripheral surface of the center shaft extension 450. Then, the third inner ring B31 of the third bearing B3 elastically deforms the gap preventing ring RR to reduce the radius thereof. Since the depth of the second central shaft annular groove 459 is equal to or greater than the height of the gap preventing ring RR, the gap preventing ring RR may be completely inserted into the second central shaft annular groove 459. For smoother fitting, a tapered or chamfered shape may be formed at the corner between the rear face and the inner peripheral face of the third outer ring B32.

The gap preventing ring RR having a smaller radius is elastically restored to an increased outer diameter at the moment of reaching the third bearing groove B34, and is thus inserted into the third bearing groove B34. In a state where the gap preventing ring RR is inserted into the third bearing groove B34, a radially inner end portion of the gap preventing ring RR is inserted into the second center shaft annular groove 459.

Thereby, as shown in fig. 8, the mounting of the third bearing B3 is completed.

In this state, when hydraulic pressure is supplied to the first space A1 in order to actuate the engine clutch 20, the rotor hub 43 tries to move rearward due to the rearward pressure applied to the first piston plate 21, but at this time, the center shaft extension 450 interferes with the gap preventing ring RR, which interferes with the third inner ring B31, the third inner ring B31 interferes with the third rolling element B33, the third rolling element B33 interferes with the third outer ring B32, and the third outer ring B32 interferes with the second input member snap ring 109, thereby preventing rearward movement of the rotor hub 43.

In order to actuate the lockup clutch 60, when hydraulic pressure is supplied to the fourth space A4, the rotor hub 43 tries to move forward, but at this time, the center shaft extension 450 interferes with the gap preventing ring RR, which interferes with the third inner ring B31, the third inner ring B31 interferes with the third rolling element B33, the third rolling element B33 interferes with the third outer ring B32, and the third outer ring B32 interferes with the second input member boss 107, thereby preventing forward movement of the rotor hub 43.

As described above, the clearance prevention ring RR, the third bearing groove B34, and the second center shaft annular groove 459 serve as axial movement prevention portions that prevent the rotor hub 43 from being cleared in the front-rear direction.

The first to third embodiments described above are premised on a state in which the outer peripheral surface of the center shaft extension 450 is disposed radially inward of the inner peripheral surface of the input member 10.

However, the present invention is not limited to this, and the hollow portion is formed in the central shaft extension portion 450, and the rear end portion of the input member 10 is inserted into the hollow portion of the central shaft extension portion 450, so that the present invention can be applied to a configuration in which the outer peripheral surface of the input member 10 is disposed radially inward of the inner peripheral surface of the central shaft extension portion 450.

< fourth embodiment >

Referring to fig. 9, the axial-movement prevention portion according to the fourth embodiment is reflected in the mounting structure of the second bearing B2.

The second bearing B2 includes: an annular second inner ring B21 disposed radially inward; a second outer ring B22 radially opposed to the second inner ring B21 and disposed radially outward of the second inner ring B21 with a gap therebetween; and a second rolling element B23 interposed between the second inner ring B21 and the second outer ring B22. The second rolling bodies B23 may be balls, and the second bearing B2 may be a ball bearing. The second bearing B2 may support rotation in the radial and axial directions.

An axially extending portion 464 of the hub boss 46 of the rotor hub 43 extends axially rearward from the hub boss 46. The axial extension 464 has a boss 469 provided on its inner peripheral surface. The forward inner diameter of the axial extension 464 is smaller than the rearward inner diameter, based on the boss 469.

The outer peripheral surface of the second outer ring B22 is in radial opposed contact with the inner peripheral surface of the axially extending portion 464. And, the rear end portion of the second outer ring B22 is in opposing contact with the boss 469 in the axial direction.

In a state where the second outer ring B22 is in contact with the boss 469, a boss snap ring 470 is installed in front of the second outer ring B22. A protruding annular groove 471 is formed immediately in front of the second outer ring B22 on the inner peripheral surface of the axial extension 464, and the protruding snap ring 470 is inserted into the protruding annular groove 471. That is, the position of the second outer ring B22 is restricted from moving rearward by the boss 469 and from moving forward by the annular groove 471 and the collar 470.

The second axial projection 823 includes a portion that extends axially further inside in the radial direction than the axially extending portion 464. Therefore, at least a part of the section of the outer peripheral surface of the second axial projection 823 is opposed to at least a part of the section of the inner peripheral surface of the axial extension 464 in the radial direction. A housing boss 828 is provided on the outer peripheral surface of the second axial projection 823. The outer diameter of the second axial protrusion 823 is smaller at the rear than at the front, based on the housing boss 828.

The inner peripheral surface of the second inner ring B21 is in radial opposition contact with the outer peripheral surface of the second axial projection 823. And, the front end portion of the second inner ring B21 is in axially opposite contact with the housing boss 828.

A second bearing groove B24 is formed in the inner peripheral surface of the second inner ring B21. In a state where the second outer race B22 is in contact with the housing boss 828, a housing annular groove 829 is formed at a portion of the outer peripheral surface of the second axial projection 823 that faces the second bearing groove B24. Thus, the second bearing groove B24 and the housing annular groove 829 are connected to communicate in the radial direction.

A gap preventing ring RR is inserted between the second bearing groove B24 and the housing annular groove 829. The gap preventing ring RR may be a C-shaped ring capable of being elastically deformed to increase or decrease the radius.

The depth of the housing annular groove 829 measured in the radial direction may be equal to or greater than the height h of the gap prevention ring RR measured in the radial direction. Conversely, the depth of the second bearing groove B24 may be smaller than the height of the gap preventing ring RR.

The order of mounting the second bearing B2 reflecting the axial movement prevention portion is as follows.

First, the second outer ring B22 of the second bearing B2 is inserted onto the inner peripheral surface of the axial extension 464 until reaching the boss 469. Then, the convex snap ring 470 is inserted in the convex annular groove 471 immediately in front of the second outer ring B22.

Next, a gap preventing ring RR is inserted into a housing annular groove 829 formed on the outer peripheral surface of the second axial projection 823. During the insertion of the gap preventing ring RR into the housing annular groove 829, the gap preventing ring RR is elastically deformed to increase its inner diameter, and is elastically restored to reduce its inner diameter at the moment of reaching the housing annular groove 829, thereby being inserted into the housing annular groove 829. In a state where the gap preventing ring RR is inserted into the housing annular groove 829, a radially outer end portion of the gap preventing ring RR protrudes radially outward from an outer peripheral surface of the second axial protruding portion 823.

In this state, the second axial protrusion 823 is inserted to the inner peripheral surface of the axial extension 464. Then, the second inner ring B21 of the second bearing B2 elastically deforms the gap preventing ring RR so that the radius thereof becomes small. Since the depth of the housing annular groove 829 is equal to or greater than the height of the gap prevention ring RR, the gap prevention ring RR may be completely inserted into the housing annular groove 829. For smoother fitting, a tapered or chamfered shape may be formed at the corner between the front face and the inner peripheral face of the second inner ring B21.

The gap preventing ring RR having a smaller radius is elastically restored at the moment of reaching the second bearing groove B24, and has a larger outer diameter, thereby being inserted into the second bearing groove B24. In a state where the gap preventing ring RR is inserted into the second bearing groove B24, a radially inner end portion of the gap preventing ring RR is inserted into the housing annular groove 829.

Through these processes, as shown in fig. 9, the installation of the second bearing B2 is completed.

In this state, when hydraulic pressure is supplied to the first space A1 in order to actuate the engine clutch 20, the rotor hub 43 tries to move rearward due to the rearward pressure applied to the first piston plate 21, but at this time, the protruding retainer ring 470 interferes with the second outer ring B22, the second outer ring B22 interferes with the second rolling element B23, the second rolling element B23 interferes with the second inner ring B21, the second inner ring B21 interferes with the gap preventing ring RR, and the gap preventing ring RR interferes with the second axial protrusion 823, thereby preventing rearward movement of the rotor hub 43.

In order to actuate the lockup clutch 60, when hydraulic pressure is supplied to the fourth space A4, the rotor hub 43 tries to move forward, but at this time, the boss 469 interferes with the second outer race B22, the second outer race B22 interferes with the second rolling element B23, the second rolling element B23 interferes with the second inner race B21, the second inner race B21 interferes with the gap preventing ring RR, and the gap preventing ring RR interferes with the second axial protrusion 823, thereby preventing forward movement of the rotor hub 43.

As described above, the clearance prevention ring RR, the second bearing groove B24, and the housing annular groove 829 serve as axial movement prevention parts that prevent the rotor hub 43 from being clearance in the front-rear direction.

As in the second and third embodiments, which are modifications to the first embodiment, in the fourth embodiment, instead of the protruding annular groove 471 and the protruding snap ring 470, a plastic processed portion 458 such as a caulking portion or a second bearing groove B24 may be formed in the second outer ring B22 instead of the second inner ring B21.

In the fourth embodiment, the second axial protruding portion may be disposed radially outward of the axial extending portion of the boss 46, as in the modifications of the first to third embodiments.

As described above, the present invention has been described with reference to the exemplary drawings, however, it should be understood that the present invention is not limited to the embodiments and drawings disclosed in the present specification, but various modifications can be made by a general person within the scope of the technical idea of the present invention. Meanwhile, even though the working effects of the structure based on the present invention are not explicitly described or illustrated while the embodiments of the present invention are described, it is considered that the predictable effects by the structure are acceptable.

Claims (10)

1. A hybrid drive module including an electric motor (40) having a rotor (42) and a stator (41), the hybrid drive module comprising:

a housing (80) provided with the stator (41);

a rotor hub (43) provided with the rotor (42) rotatably supported by the housing (80); and

an axial movement prevention portion between the housing (80) and the rotor hub (43) for restricting forward movement and backward movement of the rotor hub (43) with respect to the housing (80).

2. The hybrid drive module according to claim 1, wherein the axial movement prevention portion is provided between the housing (80) and the rotor hub (43) to support bearings (B2, B3) of rotation of the rotor hub (43) relative to the housing (80).

3. The hybrid drive module according to claim 2, wherein the bearing is interposed between a circumferential surface on the housing (80) side and a circumferential surface on the rotor hub (43) side that face each other in a radial direction,

the bearing comprises:

a first ring that contacts a first circumferential surface that is a surface selected from the circumferential surface on the housing (80) side and the circumferential surface on the rotor hub (43) side;

A second ring that is in contact with a second circumferential surface of the other of the circumferential surface on the housing (80) side and the circumferential surface on the rotor hub (43) side; and

a rolling element interposed between the first and second rings,

the axial movement prevention section includes:

a bearing groove formed in a surface of the first ring opposite to the first circumferential surface;

a circumferential surface groove formed in a first circumferential surface at a position corresponding to the bearing groove; and

a gap preventing ring (RR) is inserted across the circumferential groove and the bearing groove.

4. A hybrid drive module according to claim 3, wherein the height (h) of the clearance prevention ring is less than or equal to the depth of the circumferential groove.

5. The hybrid drive module of claim 4, wherein the height of the clearance prevention ring is greater than the depth of the bearing groove.

6. A hybrid drive module according to claim 3, wherein the first circumferential surface is provided with a first bearing boss protruding radially so as to interfere with one side in the axial direction of the first ring.

7. The hybrid drive module according to any one of claims 3 to 6, wherein the second circumferential surface is provided with a second bearing boss protruding radially so as to interfere with the other axial side of the second ring.

8. The hybrid drive module according to claim 7, wherein a bearing fixing portion that interferes with one side in an axial direction of the second ring is provided on the second circumferential surface.

9. The hybrid drive module of claim 8, wherein the bearing fixture comprises:

an annular groove formed in the second circumferential surface at a position not opposed to the second ring; and

a snap ring inserted into the annular groove,

the clasp part protruding radially from the annular groove interferes with one side of the second ring in the axial direction.

10. The hybrid drive module according to claim 8, wherein the bearing fixing portion includes a plastic processed portion that is plastically deformed to protrude in a radial direction in a state where the bearing is axially inserted into the second bearing boss.