CN211343919U

CN211343919U - Hydraulic torque converter

Info

Publication number: CN211343919U
Application number: CN201921341493.XU
Authority: CN
Inventors: 胡勋; 王盛璋; S·李; 孟腾
Original assignee: Faroeco Torque Converter Nanjing Co ltd
Current assignee: Faroeco Torque Converter Nanjing Co ltd
Priority date: 2019-08-19
Filing date: 2019-08-19
Publication date: 2020-08-25
Anticipated expiration: 2029-08-19

Abstract

The present disclosure relates to a torque converter, comprising: a housing for receiving an input torque; a pump wheel integral with the housing and rotatable about a rotation axis; a turbine wheel rotatable about an axis of rotation, the turbine wheel being disposed axially opposite the impeller and being hydraulically drivable by the impeller, the turbine wheel comprising a turbine housing and a plurality of turbine blades; a damper including a driving disc, a driven disc, and a plurality of elastic members interposed between the driving disc and the driven disc; an output hub rotatable about an axis of rotation and connected to the turbine housing and a driven disk of the damper for outputting torque; the turbine housing and the driven disc are mounted to the output hub by rivets, wherein the output hub comprises a first centering surface for the driven disc, the first centering surface being an axially extending surface, the driven disc comprising a second centering surface cooperating with the first centering surface.

Description

Hydraulic torque converter

Technical Field

The present disclosure relates to a torque converter, and more particularly to a torque converter having a centering device for a damper and an output hub.

Background

Typically, a torque converter is provided between the engine and the transmission of an automatically shifting motor vehicle. The torque converter serves to transmit driving power of an engine to a transmission by using fluid (usually oil), and functions to transmit torque and convert torque.

A torque converter typically includes a housing, an impeller, a turbine, a lockup clutch, a damper, and an output hub.

The pump impeller and the turbine wheel are axially opposed. The impeller includes an impeller housing that rotates with the casing, and a plurality of impeller blades fixed to the impeller housing. The turbine includes a turbine housing fixedly connected to the output hub and a plurality of turbine blades fixed to a side of the turbine housing facing the impeller.

The damper includes a drive plate connected to the lockup clutch and a driven plate fixedly connected to the output hub, and a circumferentially acting elastic member. A circumferentially acting resilient member is interposed between the drive disc and the driven disc.

The fixed connection of the turbine housing, the driven disc and the output hub is realized through rivets. In production practice it has been found that during riveting, eccentricity problems occur, that is to say radial offsets are often produced between the turbine housing, the driven disk and the output hub, in particular between the driven disk and the output hub. Especially, a hydraulic torque converter with a centrifugal pendulum has higher requirements on dynamic balance. This results in a large unbalance of the torque converter during rotation, which leads to unnecessary dynamic loading of the torque converter, in particular of the output hub, which is detrimental to the proper operation of the torque converter.

SUMMERY OF THE UTILITY MODEL

The present disclosure is directed to solving at least the above problems in the prior art to eliminate radial displacement between the driven disk and the output hub, improving dynamic balance of the torque converter.

The present disclosure presents a torque converter, comprising: a housing for receiving an input torque; a pump wheel integral with the housing and rotatable about a rotation axis; a turbine wheel rotatable about an axis of rotation, the turbine wheel being disposed axially opposite the impeller and being hydraulically drivable by the impeller, the turbine wheel comprising a turbine housing and a plurality of turbine blades; a lockup clutch including an axially displaceable piston disc; a damper including a driving disk, a driven disk, and a plurality of elastic members interposed between the driving disk and the driven disk, the driving disk being connected to a piston disk of the lockup clutch; an output hub rotatable about the axis of rotation and connected to the turbine housing and a driven disk of the damper for outputting torque; the turbine housing and the driven disc are coaxially arranged about the axis of rotation and are mounted to the output hub by rivets, wherein the output hub comprises a first centering surface for the driven disc, the first centering surface being an axially extending surface, the driven disc comprising a second centering surface cooperating with the first centering surface.

The above described centering of the driven disc and the output hub allows a very simple manufacture and operation.

Centering of the driven disk relative to the output hub may be ensured by cooperation of the first and second centering surfaces during the riveting preparation. Also, the cooperation of the first and second centering surfaces may inhibit radial play of the driven disk relative to the output hub during the staking process, thereby improving the centering and dynamic balance of the torque converter.

In some embodiments, the output hub includes an axially elongated portion and a radially elongated portion, the first centering surface being formed in the axially elongated portion.

In some embodiments, the output hub includes an axially elongated portion and a radially elongated portion, the first centering surface being formed in the radially elongated portion.

In some embodiments, the driven disk is formed as an annular body annular section including a central bore including an axially extending first cylindrical inner surface, the second centering surface being formed by the first cylindrical inner surface of the central bore.

In some embodiments, the driven disk includes an annular body annular section and a plurality of lugs projecting radially inward from the annular body annular section, each lug including a second cylindrical inner surface, the second centering surface being formed by the second cylindrical inner surface of the plurality of lugs.

In some embodiments, the plurality of lugs are equally circumferentially spaced about the axis of rotation.

In some embodiments, the number of lugs is 3.

In some embodiments, the damper further comprises a pendulum damper comprising a support plate and a plurality of pendulum masses disposed in the support plate, the support plate being connected to the driven disk.

Drawings

The accompanying drawings are incorporated in and constitute a part of this specification. Together with the general description given above, and the detailed description of exemplary embodiments and methods given below, the drawings serve to explain the principles of the disclosure. The objects and advantages of the present disclosure will become apparent upon a study of the following specification in light of the accompanying drawings, in which like elements are given the same or similar reference numerals, and in which:

FIG. 1 is a schematic illustration of a torque converter according to a first exemplary embodiment of the present disclosure;

FIG. 2 is an exploded view of a torque converter according to a first exemplary embodiment of the present disclosure;

FIG. 3 shows in detail the connection of the turbine housing, driven disk and output hub of a torque converter according to a first exemplary embodiment of the present disclosure;

FIG. 4 illustrates in detail the connection of the turbine housing, driven disk and output hub of a torque converter in accordance with a second exemplary embodiment of the present disclosure;

fig. 5 shows in detail a mounting flange of a driven plate of a torque converter according to a third example embodiment of the present disclosure.

Detailed Description

Reference will now be made in detail to the exemplary embodiments and methods of the present disclosure as illustrated in the accompanying drawings, in which like reference numerals designate identical or corresponding parts. It should be noted, however, that the disclosure in its broader aspects is not limited to the specific details, representative apparatus and methods, and illustrative examples shown and described in connection with the exemplary embodiments and methods.

This description of the exemplary embodiments is intended to be read in connection with the accompanying drawings, which are to be considered part of the entire written description. In the description, relative terms such as "upper," "lower," "right," "left," and derivatives thereof (e.g., "downwardly," "upwardly," etc.) should be construed to refer to the orientation as then described or as shown in the drawing under discussion. These relative terms are for convenience of description and are not intended to require a particular orientation. Unless expressly stated otherwise, the terms "connected," coupled, "and the like refer to a relationship wherein structures are secured or attached to one another either directly or indirectly through intervening structures, as well as both movable or rigid attachments or relationships. The term "operatively connected" is a connection that allows the associated structure to have the connection during operation or actual use. In addition, the words "a" and "an" as used in the claims mean "at least one" and the words "two" as used in the claims mean "at least two".

A first exemplary embodiment of a hydrodynamic torque converter 1 is generally shown in fig. 1 and 2. The torque converter 1 receives input torque from an engine and transmits the torque to an input shaft (not shown) of a transmission, such as in a motor vehicle.

It should be understood that the axial and radial orientations are considered relative to the rotational axis X of the hydrodynamic torque converter 1. Relative terms such as "axially", "radially" and "circumferentially" relate to orientations parallel, perpendicular and circularly around the axis of rotation X, respectively. The figures discussed here show only half of the hydrodynamic torque converter 1, i.e. a partial or partial cross section of the hydrodynamic torque converter 1 above the axis of rotation X. As is known in the art, the torque converter 1 is symmetrical about the axis of rotation X.

The torque converter 1 includes a housing 2 as an input member, which is internally filled with a fluid and is rotatable about a rotation axis X. The housing 2 receives torque from the engine as input torque to the torque converter 1. The housing 2 rotates at the same speed as the speed of the output shaft of the engine.

The torque converter 1 further includes an output hub 7 as an output member, which is rotatable about the rotation axis X. The output hub 7 is coupled to and disposed coaxially with the input shaft of the transmission. For example, the output hub 7 may be provided with internal splines for non-rotatably coupling the output hub 7 to an input shaft of a transmission provided with complementary external splines. Alternatively, a weld or other connection may be used to secure the output hub 7 to the input shaft of the transmission.

The torque converter 1 shown in fig. 1 includes a pump impeller 3 rotatable about a rotation axis X, a turbine runner 4 rotatable about the rotation axis X and coaxially aligned with the pump impeller 3, and a stator disposed between the pump impeller 3 and the turbine runner 4.

The impeller 3 includes an impeller housing 31 and a plurality of impeller blades fixed to the impeller housing 31. The pump impeller housing 31 is axially opposed to and integral with the outer casing 2, and the pump impeller housing 31 is fixed to the outer casing 2 by a weld shown in fig. 1, for example.

The turbine 4 is arranged axially opposite the pump wheel 3 and can be hydraulically driven by it. The turbine 4 includes a turbine housing 41 and a plurality of turbine blades 42. The turbine housing 41 is fixedly connected to the output hub 7 by rivets 11. The turbine blades 42 are fixed to the side of the turbine housing 41 facing the pump impeller 3. The pump wheel 3, the turbine wheel 4 and the stator together form a circle of revolution. The pump wheel 3 and the turbine wheel 4 may transmit power through a fluid without a rigid connection, as is known in the art.

The torque converter 1 further comprises a lock-up clutch 5 arranged to transmit torque mechanically when in an engaged (locked) position. The lock-up clutch 5 is normally locked after the start-up procedure of the hydrodynamic transmission of the motor vehicle in order to avoid efficiency losses, for example caused by slip phenomena between the turbine 4 and the pump impeller 3.

The lockup clutch 5 includes a generally annular piston disc 51, the piston disc 51 including an annular friction plate 52, the annular friction plate 52 being securely attached to an engagement surface of the piston disc 51 facing the lock wall 21 of the outer case 2 by suitable means known in the art, for example, by adhesive bonding. As best shown in fig. 1, the friction plates 52 are fixedly attached to the engagement surface of the piston disc 51 at the radially outer peripheral end of the piston disc 51. The piston disc 51 is axially displaceable to move toward the lock-up wall 21 of the housing 2 (corresponding to the engaged position of the lock-up clutch 5) or away from the lock-up wall 21 of the housing 2 (the disengaged position of the lock-up clutch 5).

The damper 6 is disposed between the output hub 7 and the piston disc 51 of the lockup clutch 5. As best shown in fig. 2, the damper 6 includes a driving disc 61, a driven disc 62, and a plurality of elastic members 63 interposed between the driving disc 61 and the driven disc 62. The driving disc 61 constitutes an input member of the damper 6, and the driven disc 62 constitutes an output member of the damper 6. The driving disc 61 and the driven disc 62 are both substantially annular, coaxial to each other and rotatable about a rotation axis X.

As shown in fig. 2, the drive plate 61 includes an annular body 61b, and the annular body 61b is fixed to the piston plate 51 of the lock-up clutch 5 by an appropriate means such as rivets 12 or welding. The driving disc 61 further includes a plurality of pawls 61c extending axially from the outer periphery of the annular body 61b toward the driven disc 62. The plurality of claws 61c are equally spaced in the circumferential direction around the rotation axis X. In the exemplary embodiment shown in fig. 2, the number of jaws 61c is 3, although other numbers of jaws may be envisaged by a person skilled in the art.

With continued reference to fig. 2, the driven plate 62 includes an elastic member holding portion 67 for holding the plurality of elastic members 63. The elastic member holding portion 67 includes an abutting portion (not shown) perpendicular to the circumferential direction. The elastic members 63 are circumferentially arranged in series between the driving disc 61 and the driven disc 62. Specifically, the elastic members 63 are compressed between the abutting portions of the claws 61c of the driving disc 61 and the elastic member holding portions 67 of the driven disc 62, so that the damper absorbs the abrupt torque. During operation of the damper 6, the power input to the driving disc 61 of the damper 6 is transmitted to the output hub 7 via the elastic member 63 and the driven disc 62. Therefore, the variation in the engine rotation can be effectively damped. The driven disc 62 further includes a mounting flange 65 extending radially inward from the elastic member holding portion 67 for mounting the driven disc 62 to the output hub 7. The mounting flange 65 has an annular shape with a central hole 65o, said mounting flange 65 being fixedly connected to the output hub 7 by means of rivets 11.

During vehicle operation, when the lock-up clutch 5 is in the engaged position, the torque converter 1 is operated in a rigid transmission mode, with torque first transmitted from the engine to the outer case 2, then transmitted to the damper 6, and further to the output hub 7, by frictional engagement between the friction plate 52 of the lock-up clutch 5 and the lock-up wall 21 of the outer case 2. In the rigid transmission mode, a transmission path of torque is transmitted to the output hub 7 via the lock-up clutch 5 and the damper 6.

When the lock-up clutch 5 is in the disengaged position, the torque converter 1 operates in a hydrodynamic transmission mode, torque being transmitted first from the engine to the outer casing 2 and the impeller housing 31 integral with the outer casing 2, and then to the output hub 7 via the impeller 3 and the turbine runner 4. In the hydrodynamic transmission mode, the transmission path of the torque is transmitted through the impeller 3, the turbine 4 and the output hub 7.

With continued reference to fig. 2, in some embodiments, the damper 6 further includes a pendulum damper 8 that is rotatable about the axis of rotation X. The pendulum absorber 8 comprises a generally annular support plate 81 and a plurality of pendulum masses 82 mounted to the support plate 81, the pendulum masses 82 being movable relative to the support plate. The bearing plate 81 is connected to the driven plate 62, for example by means of the rivet 13 shown in fig. 2. A plurality of pendulum masses 82 are arranged at the radially outer periphery of the support plate 81 to receive the maximum centrifugal force during rotation of the damper 6 about the rotation axis X to effectively absorb vibrations.

As shown in fig. 1 and 2, the output hub 7 comprises a substantially cylindrical axial extension 71 and a radial extension 72 extending radially from one end of the axial extension 71. The axial extension 71 may be provided with internal splines for non-rotatably coupling the output hub 7 to an input shaft (not shown) of a transmission provided with complementary external splines. Alternatively, a weld or other connection may be used to secure the output hub 7 to the input shaft of the transmission.

The turbine housing 41 and the driven disc 62 are coaxially disposed about the rotation axis X, and are mounted to the output hub 7 by rivets 11. For this purpose, as shown in fig. 2, the turbine housing 41, the mounting flange 65 of the driven disk 62 and the radial extension 72 of the output hub 7 may each be provided with rivet holes equally spaced apart in the circumferential direction. The rivet holes of the turbine housing 41 are indicated by reference numeral 43, the rivet holes of the driven disk 62 are indicated by reference numeral 66, and the rivet holes of the output hub 7 are indicated by reference numeral 73.

Fig. 3 is a partially enlarged view of fig. 1, showing in detail the connection portion between the turbine housing 41, the driven plate 62 and the output hub 7 of the torque converter according to the first exemplary embodiment of the present disclosure. As can be seen in fig. 3, the rivet holes 43 of the turbine housing 41, the rivet holes 66 of the driven plate 62 and the rivet holes 73 of the output hub 7 are correspondingly aligned in the axial direction. The riveted deformed end is provided on the output hub 7 side, for example. To facilitate the filling of the deformed end, it is known practice to set the sizes of the rivet hole 43 of the turbine housing 41, the rivet hole 66 of the driven plate 62, and the rivet hole 73 of the output hub 7 to become gradually larger from left to right, also referred to as "flare hole". That is, the size of the rivet hole 43 of the turbine housing 41 substantially coincides with the size of the rivet, the size of the rivet hole 66 of the driven disc 62 is slightly larger than the size of the rivet hole 43 of the turbine housing 41, and the size of the rivet hole 73 of the output hub 7 is slightly larger than the size of the rivet hole 66 of the driven disc 62.

In the riveting preparation process, it is necessary to first align the rivet holes 43 of the turbine housing 41, the rivet holes 66 of the driven plate 62, and the rivet holes 73 of the output hub 7 in the axial direction. However, due to the above-described sizing of the rivet hole 43 of the turbine housing 41, the rivet hole 66 of the driven plate 62, and the rivet hole 73 of the output hub 7, there may be caused problems in that: errors in the radial direction may occur between the rivet hole 43 of the turbine housing 41, the rivet hole 66 of the driven disk 62, the rivet hole 73 of the output hub 7, particularly the rivet hole 66 of the driven disk 62, the rivet hole 73 of the output hub 7. Further, during caulking, the driven plate 62 may further undergo radial play with respect to the output hub 7 due to the deformation stress of the deformed end. After the riveting is completed, the centering of the driven plate 62 may be imperfect, which may result in unbalance of the torque converter 1 during rotation. The presence of dynamic balance problems results in unnecessary dynamic loading of the torque converter 1, and in particular the output hub 7, which may damage the internal splines of the output hub 7 or the external splines of the input shaft of the transmission, adversely affecting the proper operation of the torque converter 1. Furthermore, the dynamic balance problem caused by non-ideal centering of the driven disc 62 will be more pronounced due to the presence of the movable pendulum mass 82 in the pendulum absorber 8.

The torque converter 1 according to the present disclosure is provided with a centering device of the driven plate 62 and the output hub 7 to improve the pre-positioning of the driven plate 62 relative to the output hub 7 during the caulking preparation.

In contrast to the prior art, on the one hand, the radially elongated portion 72 of the output hub 7 has formed therein a first centring surface S1, which is an axially extending cylindrical outer surface S1. More specifically, the radially elongated portion 72 of the output hub 7 may have an axial thickened portion 74, the first centering surface S1 being formed, for example, by machining this axial thickened portion 74. On the other hand, the driven plate 62 has a mounting flange 65 that widens radially inward. As seen in the cross-sectional view of fig. 3, the mounting flange 65 of the driven disc 62 extends to a first centering surface S1 in the radially extending portion 72 of the output hub 7. The center hole 65o of the driven plate 62 includes an axially extending first cylindrical inner surface 65i that forms a second centering surface S2 that cooperates with the first centering surface S1. The outer diameter of the first centering surface S1 and the inner diameter of the second centering surface S2 are substantially the same. Thereby, in the caulking preparation process, centering of the driven plate 62 with respect to the output hub 7 can be ensured by cooperation of the first centering surface S1 and the second centering surface S2. Also, the cooperation of the first centering surface S1 and the second centering surface S2 suppresses the radial play of the driven plate 62 relative to the output hub 7 during the caulking process, thereby improving the centering and dynamic balance of the torque converter 1.

Fig. 4 shows the connection of the turbine housing 41, the driven plate 62, and the output hub 7 of the torque converter according to the second example embodiment of the present disclosure. As shown in fig. 4, the axially elongated portion 71 of the output hub 7 has a first centering surface S1 formed therein, the first centering surface S1 being an axially extending cylindrical outer surface. In contrast to the first embodiment shown in fig. 3, the driven disc 62 has a mounting flange 65 which widens further radially inwards. As seen in the cross-sectional view of fig. 4, the mounting flange 65 of the driven disc 62 extends to a first centering surface S1 located in the axial extension 71 of the output hub 7. That is, the center hole 65o of the driven disk 62 in fig. 4 has a smaller size than that of the center hole 65o of the driven disk 62 in fig. 3. The center hole 65o of the driven plate 62 includes an axially extending first cylindrical inner surface 65i that forms a second centering surface S2 that cooperates with the first centering surface S1. The outer diameter of the first centering surface S1 and the inner diameter of the second centering surface S2 are substantially the same.

In fig. 4, the mounting flange 65 of the driven disk 62 may include a first annular portion 65f and a second annular portion 65s coaxially disposed about the rotational axis X. The first annular portion 65f and the second annular portion 65s each extend in the radial direction. The first annular portion 65f is located radially outward of the second annular portion 65s and is axially offset relative to the second annular portion 65 s. The first annular portion 65f and the second annular portion 65s are connected by a transition portion 65t inclined with respect to the radial direction to adapt in shape to an axial thickening 74 of the radial extension 72 of the output hub 7.

In a third embodiment according to the present disclosure, the mounting flange 65 of the driven disk 62 may have a segmented second centering surface S2. Fig. 5 shows the mounting flange 65 of the driven disc 62 viewed axially (with rivet holes not shown). The mounting flange 65 includes an annular section 65b and a plurality of lugs 64 projecting radially inwardly from the annular section 65 b. The plurality of lugs 64 are, for example, equally spaced circumferentially about the axis of rotation X. The number of lugs 64 is 3, although other numbers of lugs 64 are also contemplated. Each lug 64 includes a second cylindrical inner surface 64i located radially inward. The second cylindrical inner surfaces 64i of the respective lugs 64 are located on the cylindrical surface of the same cylinder and together form a second centering surface S2 that cooperates with the first centering surface S1. With such a configuration, the driven disc 62 can have less material and weight, and still be able to ensure centering of the driven disc 62 relative to the output hub 7.

Of course, it is also envisaged by the skilled person that the output hub 7 may have a segmented centring surface, for example the axial extension 71 of the output hub 7 may comprise a plurality of lugs projecting radially outwards. A plurality of lugs are for example equally spaced circumferentially around the axis of rotation X. Each lug includes a cylindrical outer surface located radially outward. The outer surfaces of the respective lugs lie on the cylindrical surface of the same cylinder and together form a first centering surface S1 which cooperates with a second centering surface S2.

Various modifications, changes, and variations may be implemented with the above-described embodiments.

In accordance with the provisions of the patent statutes, the foregoing description of exemplary embodiments of the present disclosure has been presented for the purpose of illustration. It is not intended to be exhaustive or to limit the disclosure to the precise form disclosed. The embodiments disclosed above were chosen in order to best explain the principles of the disclosure and its practical application to thereby enable others skilled in the art to best utilize the disclosure in various embodiments and with various modifications as are suited to the particular use contemplated, as long as the principles described herein are followed. This application is therefore intended to cover any variations, uses, or adaptations of the disclosure using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this disclosure pertains. Accordingly, changes may be made in the above disclosure without departing from the intent and scope of the disclosure. It is also intended that the scope of the disclosure be defined by the claims appended hereto.

Claims

1. A torque converter (1), characterized in that the torque converter (1) comprises:

a housing (2) for receiving an input torque;

a pump wheel (3) integral with the casing (2) and rotatable about a rotation axis (X);

a turbine wheel (4) rotatable about an axis of rotation (X), the turbine wheel (4) being arranged axially opposite the pump wheel (3) and being hydraulically drivable by the pump wheel (3), the turbine wheel (4) comprising a turbine housing (41) and a plurality of turbine blades (42);

a lock-up clutch (5) comprising an axially displaceable piston disc (51);

a damper (6) including a driving disc (61), a driven disc (62), and a plurality of elastic members (63) interposed between the driving disc (61) and the driven disc (62), the driving disc (61) being connected to a piston disc (51) of the lockup clutch (5);

an output hub (7) rotatable about the axis of rotation (X) and connected to the turbine housing (41) and to a driven disc (62) of the damper (6) for outputting a torque;

the turbine housing (41) and the driven disc (62) being coaxially arranged around the rotation axis (X) and being mounted to the output hub (7) by rivets (11), wherein,

the output hub (7) comprises a first centering surface (S1) for the driven disc (62), the first centering surface (S1) being an axially extending surface, the driven disc (62) comprising a second centering surface (S2) cooperating with the first centering surface (S1).

2. A hydrodynamic torque converter (1) according to claim 1, characterized in that said output hub (7) comprises an axial extension (71) and a radial extension (72), said first centring surface (S1) being formed in said axial extension (71).

3. A hydrodynamic torque converter (1) according to claim 1, characterized in that said output hub (7) comprises an axial extension (71) and a radial extension (72), said first centring surface (S1) being formed in said radial extension (72).

4. A hydrodynamic torque converter (1) according to any one of claims 1 to 3, characterized in that the driven plate (62) is formed in an annular shape including a central hole (65o), the central hole (65o) including a first cylindrical inner surface (65i) extending axially, the second centering surface (S2) being formed by the first cylindrical inner surface (65i) of the central hole (65 o).

5. The torque converter (1) according to any one of claims 1 to 3, wherein the driven plate (62) includes an annular section (65b) and a plurality of lugs (64) that protrude radially inward from the annular section (65b), each lug (64) including a second cylindrical inner surface (64i), the second centering surface (S2) being formed by the second cylindrical inner surfaces (64i) of the plurality of lugs (64).

6. A hydrodynamic torque converter (1) according to claim 5, characterized in that the plurality of lugs (64) are equally circumferentially spaced around the rotation axis (X).

7. A hydrodynamic torque converter (1) as claimed in claim 5, characterized in that the number of lugs (64) is 3.

8. A hydrodynamic torque converter (1) according to any one of claims 1 to 3, characterized in that the damper (6) further comprises a pendulum damper (8), the pendulum damper (8) comprising a bearing plate (81) and a plurality of pendulum masses (82) mounted to the bearing plate (81), the bearing plate (81) being connected to the driven disc (62).