CN113738787B

CN113738787B - Input disc carrier for a dual wet clutch, clutch system and mechanism including such a disc carrier, and hybrid transmission chain

Info

Publication number: CN113738787B
Application number: CN202110907154.9A
Authority: CN
Inventors: A.多尔; F.蒂鲍特
Original assignee: Valeo Embrayages SAS
Current assignee: Valeo Embrayages SAS
Priority date: 2016-12-21
Filing date: 2017-12-13
Publication date: 2023-07-14
Anticipated expiration: 2037-12-13
Also published as: CN113738787A; WO2018114549A1; EP3559492A1; FR3060682A1; KR20190099257A; CN110268177B; CN110268177A; KR102471296B1; FR3060682B1

Abstract

The invention relates to a one-piece input disc carrier (34) for a dual wet clutch mechanism (18), comprising: a cylindrical guide bearing surface (36) for guiding the bearing (38) for guiding rotation of the input disc carrier (34) about a reference axis (100) of the input disc carrier (34); a first clutch region (42) including a first set of axially directed input teeth (46) radially facing the reference axis (100) and located a first radial distance from the reference axis (100); and a second clutch region (44) comprising a second set of axially directed input teeth (58) radially facing the reference axis (100) and located a second radial distance from the reference axis (100), the second radial distance being shorter than the first distance. The input disc carrier (34) also includes a ring gear (88).

Description

Input disc carrier for a dual wet clutch, clutch system and mechanism including such a disc carrier, and hybrid transmission chain

The present application is a divisional application of the invention patent application with the application date of 2017, 12, 13 and the application number of 201780084977.8.

Technical Field

The invention relates to a dual wet clutch for a hybrid powertrain. It also relates to an input disc carrier for such a dual wet clutch.

Background

Document US2015083546 describes a hybrid drive comprising an internal combustion engine and a clutch system comprising a double wet clutch and a reversible electric machine, the rotor of which is fixed to the input disc carrier of the double wet clutch and is surrounded by a stator. This architecture requires a large diameter motor, which is particularly expensive and at least its rotor is located within the sump containing the dual wet clutch.

Disclosure of Invention

The present invention aims to overcome the drawbacks of the prior art and proposes a device that allows a less restrictive connection between the motor and the double wet clutch, for example such that a small diameter motor or a motor that is not coaxial with the double wet clutch can be used.

To this end, a first aspect of the invention proposes a one-piece input disc carrier for a dual wet clutch mechanism, comprising a guiding cylindrical bearing surface for a bearing for guiding rotation of the input disc carrier about a reference axis of the input disc carrier, a first clutch region comprising a first set of axially guiding input teeth facing radially towards the reference axis and located at a first radial distance from the reference axis, a second clutch region comprising a second set of axially guiding input teeth facing radially towards the reference axis and located at a second radial distance from the reference axis shorter than the first distance, characterized in that the input disc carrier further comprises a ring gear comprising circumferentially distributed engagement teeth. The ring gear is intended to mesh with a pinion, toothed belt or chain for connection with the motor so that the motor may be offset from the reference axis of the input disc carrier. Thus, a motor can be envisaged whose axis of rotation is parallel to the reference axis and at a distance from the reference axis, or a motor can be envisaged whose axis of rotation is not parallel to the reference axis, for example in a plane perpendicular to the reference axis.

Preferably, the first clutch region radially outside the second clutch region overlaps the second clutch region.

In practice, and in accordance with a preferred embodiment, the ring gear comprises a continuous ring of material having a set of teeth mounted thereon. According to an embodiment, the teeth are intended to mesh with the pinion. According to another embodiment, the teeth are capable of meshing with a toothed belt. According to another embodiment, the teeth are capable of engaging with a chain.

According to an embodiment, the teeth are straight cut (positive) gear teeth. Alternatively, according to a preferred embodiment, the ring gear has helical gear teeth. Such teeth have the significant advantage of not being very noisy.

According to an embodiment, the meshing teeth of the ring gear are radially outward relative to the reference axis. This arrangement provides a great degree of freedom in terms of the positioning of the connection between the ring gear and the motor. However, an opposite arrangement with teeth facing radially towards the reference axis is equally possible.

According to an embodiment, the ring gear is located radially outside the first clutch region and radially outward. The ring may in particular axially overlap the first clutch region and, where applicable, the second clutch region. This arrangement would be preferable when there is not much axial space available between the input disc carrier and the clutch control.

According to another embodiment, the ring gear is axially offset relative to the first clutch region. More specifically, to increase the compactness in the radial direction, the ring gear does not axially overlap the first clutch region. The diameter of the ring gear is then independent of the diameter of the first clutch region. Preferably, the ring gear also does not axially overlap the second clutch region.

Preferably, the engagement teeth have free ends closer to the reference axis than the first clutch region.

Preferably, the ring gear may be located in particular between the first clutch region and the second clutch region.

According to one embodiment, the input disc carrier has a transverse wall extending radially from at least the guide support surface to the first clutch region, and the ring gear is located on a side of the transverse wall opposite the first and second clutch regions. In practice, the transverse wall comprises one or more first openings for inserting lugs of the first force transmitting member for controlling the clutch discs located in the first clutch area, and one or more second openings for inserting lugs of the second force transmitting member for controlling the clutch discs located in the second clutch area.

In practice, the input disc carrier includes a connecting arm that connects the transverse wall and the ring gear. The connecting arms may be distributed around a reference axis of the input disc carrier and form openings. These openings allow the lugs of the first force transmitting member to pass through, where applicable, and the lugs of the second force transmitting member to pass through, where applicable. The connecting arms may have ribs and/or stiffeners. These ribs or stiffeners allow, where applicable, to transmit very high torques provided by the motor.

The guide bearing surface may be radially outwardly facing, but preferably radially inwardly facing.

According to another aspect of the invention, the invention relates to a subassembly of an input disc carrier and a rotary guide bearing shrink fit or secured to a guide support surface by any other means. The guide bearing may in particular be a rolling contact bearing, such as an angular contact ball bearing. For some applications it may be advantageous to select a rolling bearing, such as a deep groove ball bearing, that is capable of withstanding bi-directional axial loads. This is especially true if the teeth of the ring gear are helical gear teeth.

According to another aspect of the invention, the invention relates to a dual wet clutch mechanism comprising:

an input disc holder as described above,

an input flange which rotates with the input disc holder,

a first output flange comprising a first set of axially directed output teeth, located facing and at a distance from the first set of input teeth, and a first interface for rotational attachment to a gearbox first input shaft,

a second output flange comprising a second set of axially directed output teeth, located facing and at a distance from the second set of input teeth, and a second interface for rotational attachment to a gearbox second input shaft,

a first multi-plate clutch assembly located between the first set of input teeth and the first set of output teeth,

-a second multi-plate clutch assembly located between the second set of input teeth and the second set of output teeth.

The first set of output teeth is preferably located between the first set of input teeth and the second set of input teeth. The first multi-plate clutch assembly is preferably located radially outside of the second multi-plate clutch assembly.

According to another aspect of the invention, the invention relates to a dual wet clutch system comprising: the dual wet clutch mechanism and clutch control as described above includes a first annular actuator, a second annular actuator located radially inward of the first annular actuator, a first force transfer member transferring force from the first actuator to the first multi-plate clutch assembly through one or more first passage openings in the input plate carrier, and a second force transfer member transferring force from the second actuator to the second multi-plate clutch assembly through one or more second passage openings in the input plate carrier. The two actuators are coaxial. The two actuators may be axially positioned to overlap each other, with the first actuator surrounding the second actuator.

According to an embodiment, the first force transmitting member and the second force transmitting member extend between the input disc carrier and the ring gear. The ring gear is axially offset relative to the first and second force transfer members.

According to an embodiment, the ring gear is located radially outside the first ring actuator.

According to an embodiment, the first actuator is axially offset towards the input disc support relative to the second actuator. This arrangement makes it possible to use the available volume constituted by a recess in the gearbox housing, which surrounds the opening through which the gearbox input shaft passes. The first force transmitting member is preferably arranged radially outside the second force transmitting member. According to an embodiment, the force transmitting member extends axially between the first and second clutch areas and the ring gear.

Preferably, a guide bearing is provided which is shrink fit or fixed to the guide support surface in any way and which provides rotational guidance for the clutch mechanism relative to a body common to the first and second annular actuators. It is also conceivable that the guide bearing is mounted between the input disc carrier and one of the gearbox input shafts or a component fixedly attached to one of the gearbox input shafts.

According to a particularly compact and small diameter ring gear compatible embodiment, the connecting arm of the input disc carrier passes through an opening formed by the first force transmitting member. If it is desired to further reduce the diameter of the ring gear, it may be provided that the connecting arm of the input disc holder passes through an opening formed in the second force transmitting member.

According to another aspect of the invention, the invention relates to a hybrid powertrain comprising an electric motor and a dual wet clutch mechanism or dual clutch system as described above and a kinematic connection between the electric motor and a ring gear. The motor may advantageously be reversible and allow for the generation of electricity when operating under load. Preferably, the kinematic connection comprises a gear, a toothed belt or a chain engaged with the ring gear.

Drawings

Other features and advantages of the present invention will become apparent upon reading the following description with reference to the accompanying drawings in which:

-fig. 1: a hybrid propulsion assembly according to the present invention includes an input disc carrier according to a first embodiment of the present invention;

-fig. 2: an isometric view of a disk holder according to a first embodiment of the present invention;

-fig. 3: a disk holder according to a second embodiment of the present invention;

-fig. 4: a disk holder according to a third embodiment of the present invention; and

-fig. 5: a disk holder according to a fourth embodiment of the present invention.

For purposes of clarity, the same or similar elements are identified by the same reference numbers throughout the drawings.

Detailed Description

Fig. 1 shows a hybrid powertrain 10 between a first electric motor 12 (in this case an internal combustion engine) and two coaxial

gearbox input shafts

22, 24, the hybrid powertrain comprising a reversible electric machine forming a second electric motor 14, a clutch system 16 comprising a dual wet clutch mechanism 18 and a clutch control 20, the dual wet clutch mechanism 18 rotating about a reference axis 100, the reference axis 100 also being the axis of the two

shafts

22, 24.

The hybrid powertrain 10 may include a first kinematic connection 28 for connecting the first electric motor 12 to the input flange 26 of the dual wet clutch mechanism 18, which first kinematic connection 28 may suitably include a mechanism 30 for filtering out torque fluctuations, such as a dual mass flywheel, and a coupling clutch 32.

The input flange 26 rotates integrally with the input disc carrier 34 of the dual wet clutch 18. The input disc carrier 34 is suitably a one-piece component obtained by welding together several pressed metal plates and comprises a guiding cylindrical bearing surface 36 for guiding the rolling bearing 38 facing the reference axis 100, a transverse wall 40 extending radially from the guiding bearing surface 36 to an outer skirt forming the first clutch zone 42 and an inner skirt forming the second clutch zone 44, the second clutch zone 44 being located radially inside the first clutch zone 42. The two

clutch areas

42, 44 are located axially on the same side of the transverse wall 40.

The first clutch region 42 of the input disc carrier is provided with a first set of input teeth 46 radially facing the reference axis 100. The dual wet clutch mechanism 18 further comprises a first output flange 48, the first output flange 48 comprising a first set of output teeth 50 and a first interface 52, the first set of output teeth 50 being located facing and at a distance from the first set of input teeth 46, the first interface 52 for rotational attachment to the first input shaft 22 of the gearbox. Housed within the annular volume radially defined by the first clutch region 42 and the first output flange 48 of the input disc carrier 34 is a first multi-disc clutch assembly E1 that includes a first set of input discs 54 and a first set of output discs 56. The discs of the first set of input discs 54 mesh with the first set of input teeth 46 for rotation therewith but are capable of axial translational movement relative to the input disc carrier 18. The discs of the first set of output discs 56 mesh with the first set of output teeth 50 for rotation therewith but are capable of axial translational movement relative to the first output flange 48. The discs of the first set of output discs 56 are interleaved with the discs of the first set of input discs 54. The spring washers are located between the

disks

54, 56 and tend to separate them from one another. Thus, the first multi-plate clutch assembly E1 constitutes a first kinematic connection between the input plate carrier 34 and the first output flange 48 in a known manner.

The second clutch region 44 is provided with a second set of input teeth 58 that face radially toward the reference axis. The dual wet clutch mechanism 18 further comprises a second output flange 60, the second output flange 60 comprising a second set of output teeth 62 and a second interface 64, the second set of output teeth 62 being located facing and at a distance from the second set of input teeth 58, the second interface 64 for rotational attachment to a second gearbox input shaft. Housed within the annular volume radially defined by the second clutch region 44 and the second output flange 60 of the input disc carrier 34 is a second multi-disc clutch assembly E2 that includes a second set of input discs 66 and a second set of output discs 68. The discs of the second set of input discs 66 mesh with the second set of input teeth 58 for rotation therewith, but are capable of axial translational movement relative to the input disc carrier 34. The discs of the second set of output discs 68 engage the second set of output teeth 62 for rotation therewith but are capable of axial translational movement relative to the second output flange 60. The discs of the second set of output discs 68 are interleaved with the discs of the second set of input discs 66. The spring washers are located between the

disks

66, 68 and tend to separate them from one another. Thus, the second multi-plate clutch assembly E2 constitutes a first kinematic connection between the input plate carrier 34 and the second output flange 60 in a known manner.

The transverse wall 40 includes first passage openings 70 that are circumferentially distributed and open to the volume defined by the first clutch region 42 and the first output flange 48, and second passage openings 72 that are circumferentially distributed and open to the volume defined by the second clutch region 44 and the second output flange 60.

The clutch control 20 includes a first annular actuator 74 (in this case a hydraulic actuator), a first rotary thrust member 76, and a first force transfer member 78, the first force transfer member 78 having an annular body 78.1 and a tab 78.2 against the rotary thrust member 76, the tab 78.2 passing through the first passage opening 70 in the input disc carrier 34 to allow force to be transferred from the first actuator 74 to the first set of input discs 54 and the first set of output discs 56.

The clutch control 20 also includes a second annular actuator 80 (in this case a hydraulic actuator, which is located radially inside the first annular actuator 74), a second rotary thrust member 82, and a second force transfer member 84, the second force transfer member 84 having an annular body 84.1 and a lug 84.2 that bear against the rotary thrust member 82, the lug 84.2 passing through the second passage opening 72 in the input disc carrier 34 to allow force to be transferred from the second actuator 80 to the second set of input discs 66 and the second set of output discs 68.

The two

actuators

74, 80 are formed in a common housing 86, which housing 86 is for attachment to the gearbox housing. The first actuator 74 is axially offset towards the input disc carrier 34 relative to the second actuator 80, the second actuator 80 being intended to be received in a recess in the gearbox housing surrounding the

input shafts

22, 24.

The inner ring of the guide roller bearing 38 for the input disc carrier 34 is shrink-fit or fixed to the housing 86 of the

actuator

74, 78 or to an annular connection 87 by any means, which annular connection 87 is fixed to the housing 86 of the

actuator

74, 78.

The input disc carrier 34 also includes a ring gear 88 for connection to the motor 14 through a second kinematic connection 90, which second kinematic connection 90 may include gears, toothed belts, chains, or any other kinematic connection member as shown in fig. 1.

The ring gear 88 preferably comprises a continuous material ring 88.2 having engagement teeth 88.1 formed or attached thereto. According to the embodiment of fig. 1, the teeth 88.1 of the ring gear 88 are radially outwardly facing with respect to the reference axis 100 and are axially positioned on the opposite side of the transverse wall 40 from the first and second

clutch areas

42, 44 and radially closer to the reference axis 100 than the first and second

clutch areas

42, 44 of the input disc carrier 34. Further, the teeth 88.1 of the ring gear 88 are located radially outside the first actuator 74. The input disc carrier 34 includes a connecting arm 92 that connects the transverse wall 40 and the ring gear 88 and the opening between the connecting arms. The connecting arm 92 passes through

openings

94, 96 formed in the first force transmitting member 78 and the second force transmitting member 84. After the first force transmitting member 78 and the second force transmitting member 84 have been positioned, the connecting arm 92 is welded to the transverse wall 40 using a transparent weld through the transverse wall 40, as shown in FIG. 2. The connecting arms 92 are also welded to the continuous ring 88.2 of ring gear 88.

The hybrid powertrain 10 thus described allows the

input shafts

22, 24 of the gearboxes to be driven indifferently from the first electric motor 12 (by closing the coupling clutch 32) or from the second electric motor 14 (by opening the coupling clutch 32). It also allows the reversible electric machine constituting the second electric motor 14 to be used as a power source in a regenerative braking mode (the coupling clutch 32 is open and one stage of the double wet clutch 18 is closed) or in a charging mode (the coupling clutch 32 is closed and the first electric motor 12 drives the reversible electric motor 14 through the input disc carrier 34, the double wet clutch 18 being able to be opened or closed).

Fig. 3 to 5 show an embodiment of the input disc carrier 34 which differs from the embodiment of fig. 1 mainly in the positioning of the ring gear 88. Thus, the ring gear 88 is positioned radially outside of the first clutch region 42 of the input disc carrier 34 and axially overlaps the two

clutch regions

42, 44 of the input disc carrier 34 in fig. 3. The ring gear 88 may be secured to the input disc carrier 34 by any means, particularly by welding or shrink fitting. This embodiment will be particularly suitable for cases where the axial compactness of the assembly is more desirable than the radial compactness. According to the embodiment of fig. 4, the ring gear 88 is located at an axial distance from the transverse wall 40 on the side of the transverse wall 40 opposite the first and second

clutch areas

42, 44 and radially outside the

first passage openings

70, 72. In addition, the teeth 88.1 of the ring gear 88 are oriented radially inward relative to the reference axis 100. In this case, a kinematic connection 90 to the motor can be achieved via the drive shaft. According to the embodiment of fig. 5, the connecting arms 92 connecting the ring gear 88 to the transverse wall 40 are located radially between the first passage opening 70 and the second passage opening 72. More specifically, the input disc holder 34 is formed by an assembly of two annular parts 34.1, 34.2 (one external and the other internal) made of pressed sheet metal and welded together. The connecting arm 92 is formed directly in the outer part 34.1, which outer part 34.1 also comprises the first clutch region 42, while the second clutch region 44 is formed on the inner part 34.2. After the force transfer member 78 is positioned between the arms 92, the ring gear is attached to the outer portion of the arms 92.

The guide bearing surface 36 may form a raceway for the guide bearing 38.

Naturally, the examples depicted in the drawings and discussed above are given by way of non-limiting illustration only. It is expressly contemplated that the various embodiments shown may be combined with one another to form other embodiments.

It may be particularly desirable for the ring gear (shown in the figures as having straight cut spur gear teeth) to have helical gear teeth to reduce noise levels. Ring gears with bevel gear teeth are also contemplated to provide a connection to the motor with the axis of rotation of the motor lying in a plane perpendicular to the reference axis.

The connecting arm 92 may be crimped or otherwise attached to the input disc carrier 34 in any manner. They may be secured to the ring gear 88 by any means.

It is emphasized that all of these features, such as disclosed to a person skilled in the art on the basis of the present description, the figures and the appended claims, even if they are described only in specific terms in relation to other determined features, whether alone or in any combination, can be combined with other features or groups of features disclosed herein, as long as such combination is not explicitly excluded or the technical environment makes such combination impossible or meaningless.

Claims

1. A one-piece input disc carrier (34) for a dual wet clutch mechanism (18) comprising a guiding cylindrical bearing surface (36) for a bearing (38) for guiding rotation of the input disc carrier (34) about a reference axis (100) of the input disc carrier (34), a first clutch region (42) comprising a first set of axially guiding input teeth (46) facing radially towards the reference axis (100) and located at a first radial distance from the reference axis (100), a second clutch region (44) comprising a second set of axially guiding input teeth (58) facing radially towards the reference axis (100) and located at a second radial distance from the reference axis (100) shorter than the first distance, characterized in that the input disc carrier (34) further comprises a ring gear (88) comprising circumferentially distributed engagement teeth (88.1) located radially outside the first clutch region (42) and radially outwards.

2. The input disc carrier of claim 1, wherein the meshing teeth (88.1) of the ring gear (88) are radially outward relative to a reference axis (100).

3. The input disc carrier of any of claims 1 and 2, wherein the ring gear (88) comprises a continuous ring of material having a set of teeth (88.1) mounted thereon, the ring gear having helical gear teeth.

4. Input disc carrier according to claim 1, characterized in that it is an integral part obtained by welding together several pressed metal plates and comprises a transverse wall (40) extending radially from the guiding cylindrical bearing surface (36) to an outer skirt forming a first clutch zone (42), and an inner skirt forming a second clutch zone (44) radially inside said first clutch zone (42).

5. A dual wet clutch mechanism (18), comprising:

the input disc support (34) as claimed in any one of the preceding claims,

an input flange (26) which rotates with the input disc holder (34),

a first output flange (48) comprising a first set of axially directed output teeth (50) located facing and at a distance from the first set of input teeth (46), and a first interface (52) for rotational attachment to a gearbox first input shaft (22),

a second output flange (60) comprising a second set of axially directed output teeth (62) located facing and at a distance from said second set of input teeth (58), and a second interface (64) for rotational attachment to a gearbox second input shaft (24),

a first multi-plate clutch assembly (E1) located between the first set of input teeth (46) and the first set of output teeth (50),

a second multi-plate clutch assembly (E2) located between the second set of input teeth (58) and the second set of output teeth (60).

6. A dual wet clutch system (16), comprising: the dual wet clutch mechanism (18) as set forth in claim 5 and a clutch control (20) including a first annular actuator (74), a second annular actuator (80) radially inboard of said first annular actuator (74), a first force transfer member (78) transferring force from the first actuator (74) to the first multiple disc clutch assembly (E1) through one or more first passage openings (70) in said input disc carrier (34), and a second force transfer member (84) transferring force from the second actuator (80) to the second multiple disc clutch assembly (E2) through one or more second passage openings (72) in the input disc carrier (34).

7. The dual wet clutch system as set forth in claim 6 wherein said ring gear (88) is located radially outboard of said first annular actuator (74).

8. A dual wet clutch system according to any of claims 6 and 7, wherein the first actuator (74) is axially offset relative to the second actuator (80) towards the input disc carrier (34).

9. A dual wet clutch system according to claim 6, further comprising a guide bearing (38) shrink fit or fixed to the guide cylindrical support surface (36) in any manner and providing rotational guidance for the clutch mechanism (18) relative to a body (86) common to the first and second annular actuators (74, 80).

10. A hybrid powertrain comprising an electric motor (14), characterized in that it further comprises a dual wet clutch mechanism (18) according to claim 5 or a dual wet clutch system (16) according to any of claims 6 to 9 and a kinematic connection (90) between the electric motor (14) and a ring gear (88).

11. Hybrid powertrain according to the preceding claim, characterized in that it further comprises a first kinematic connection (28) for connecting the first electric motor (12) to an input flange (26) of said double wet clutch mechanism (18), the first kinematic connection (28) comprising means (30) for filtering torque fluctuations.