Damping system for hydraulic coupling device, hydraulic coupling device and motor vehicle

Abstract

The present invention relates to a damping system for a hydraulic coupling device, comprising: an output hub having a central axis and an annular portion around the central axis, wherein a first track is arranged in the annular portion; a plurality of turbine mass groups evenly distributed around the central axis, each turbine mass assembly comprising a turbine section, each turbine section carrying a plurality of blades and provided with a second track corresponding to the first track; a roller capable of rolling along a roller track defined by the first track and the corresponding second track, so that the turbine mass assembly can move relative to the output hub and apply torque on the output hub; wherein each turbine mass assembly also comprises a mass plate fixedly connected to the turbine section, and the output hub is arranged between the mass plate and the turbine section. The present invention also relates to a hydraulic coupling device comprising such a damping system and a motor vehicle comprising such a hydraulic coupling device.

Description

Technical Field

[0001] The invention relates to a damping system for a hydraulic coupling device, and also to a hydraulic coupling device comprising such a damping system and a motor vehicle comprising such a hydraulic coupling device. Background Art

[0002] In the vehicle transmission system, a hydraulic coupling device is provided between the internal combustion engine and the transmission, which uses fluid as a working medium to transmit the torque from the engine to the input shaft of the transmission, thereby playing the role of transmitting torque, torque conversion and clutch. Generally, the hydraulic coupling device may include a damping system for eliminating the torque fluctuation inherent in the output of the internal combustion engine.

[0003] There is a need to reduce torsional vibration by improving the structure of the hydraulic coupling device.

[0004] However, the damping devices in the prior art are mostly separate devices from the turbine and other components of the hydraulic coupling device, and in such prior art, the turbine is usually completely fixedly connected to the output hub. On the one hand, such damping devices usually have a relatively complex structure and a large number of components, and the installation of such damping devices in the hydraulic coupling device also requires a large number of additional parts and relatively complex processes. On the other hand, such damping devices usually occupy a large axial distance, occupying the axial space of the hydraulic coupling device, which is not conducive to forming a compact hydraulic coupling device.

[0005] It is also known that a damping device is formed by using the structure of the turbine housing itself, as described in German patent application DE102009000068. In this type of technical solution in the prior art, each sub-section constituting the turbine disc is connected to the output member through a roller and can move relative to the output member. In the presence of torque fluctuations, the sub-sections of the turbine disc can be used as swinging masses to attenuate torque fluctuations. However, in this type of technical solution in the prior art, due to the uneven distribution of the swinging mass on both sides of the roller in the axial direction, especially when rotating, this unevenness is particularly obvious, resulting in unbalanced and unstable movement of the roller, and even jamming, etc., which cannot effectively attenuate torque fluctuations. In addition, in this type of technical solution in the prior art, there is no simple, easy to implement and integrated stop component that can effectively limit the relative displacement stroke between the turbine disc and the output hub.

[0006] Therefore, it is desirable to provide a damping system that can attenuate torque fluctuations by using the turbine housing itself, while ensuring smooth movement of the roller and limiting the relative displacement stroke between the turbine disk and the output hub. Summary of the invention

[0007] To this end, according to one aspect of the present invention, a damping system for a hydraulic coupling device is provided, comprising:

[0008] an output hub having a central axis and an annular portion surrounding the central axis, wherein a first track is disposed in the annular portion,

[0009] a plurality of turbine mass assemblies evenly distributed around the central axis, each turbine mass assembly comprising a turbine section, each turbine section carrying a plurality of blades and provided with a second track corresponding to the first track,

[0010] a roller capable of rolling along a roller track defined by said first track and a corresponding second track so that the turbine mass assembly can move relative to an output hub and exert a torque on said output hub,

[0011] Each turbine mass assembly further comprises a mass plate fixedly connected to the turbine section, and the output hub is arranged between the mass plate and the turbine section.

[0012] That is, in the damping system for the hydraulic coupling device according to the present invention, the turbine mass assembly including the turbine section carrying multiple blades itself at least constitutes a part of the damping system. Specifically, when there is torque fluctuation, under the action of inertia, the roller rolling along the roller track defined by the first track in the annular portion of the output hub and the second track in the corresponding turbine section provides a torque opposite to the torque fluctuation to achieve the effect of attenuating the torque fluctuation. That is, the damping system for the hydraulic coupling device according to the present invention not only utilizes the turbine section itself to achieve the damping effect, but also utilizes the structure of the component itself to simply achieve the stop of the turbine section in the rotation direction relative to the output hub, which does not require a separate and complex damping system that is usually separated from the turbine section in the prior art, thereby simplifying the structure of the hydraulic coupling device, and at the same time can greatly reduce the number of components, simplify the manufacturing and installation processes, and achieve higher cost-effectiveness.

[0013] Further, in the damping system for the hydraulic coupling device according to the present invention, the mass plate fixedly connected to the turbine section together with the turbine section constitutes a turbine mass assembly that performs a damping function, and the mass plate and the corresponding turbine section are respectively arranged on the axially opposite sides of the output hub, and together with the turbine section, play a role in achieving the attenuation of torque fluctuations, thereby achieving a better attenuation effect. In addition, such a structure enables the roller that guides the turbine mass assembly to move relative to the output hub to have a more uniform swing mass distribution on both sides thereof in the axial direction, thereby ensuring the relatively smooth movement of the roller, and thus achieving a more effective oscillation attenuation effect. Moreover, such a structure is more conducive to the assembly of the turbine section and the mass plate, and can achieve a more stable damping system.

[0014] In a more specific embodiment of the damping system for a hydrodynamic coupling according to the invention, the mass plate has the same weight as the turbine section, thereby ensuring a more uniform axial oscillating mass distribution for the roller, thereby ensuring a more stable movement of the roller and thus ensuring an optimal oscillation damping effect.

[0015] Furthermore, the damping system for a hydraulic coupling device according to the present invention further comprises a first stop member arranged on the output hub and a second stop member arranged on the turbine mass assembly, wherein the first stop member and the second stop member are capable of cooperating to limit the displacement stroke of the turbine mass assembly relative to the output hub.

[0016] That is, in the damping system for a hydraulic coupling device according to the present invention, the arrangement of the first stop member on the output hub and the second stop member on the turbine mass assembly can achieve limitation of the displacement stroke of the turbine mass assembly relative to the output hub with a simple and compact structure, thereby avoiding damage to the roller in the event of torque fluctuations, such as causing it to break, to affect the damping effect or even cause the damping system to fail.

[0017] Optionally, the first stopping component is a first notch provided on the output hub, and the second stopping component is a first protrusion provided on the mass plate.

[0018] Preferably, the first notch is integrally formed with the output hub, and the first protrusion is integrally formed with the mass plate.

[0019] Optionally, the first stopping component is a first notch provided on the output hub, and the second stopping component is a second protrusion provided on the turbine section.

[0020] Preferably, the first notch is made integrally with the output hub, and the second protrusion is made integrally with the turbine section.

[0021] Optionally, the first stopping component is a third protrusion provided on the output hub, and the second stopping component is a second notch provided on the turbine section.

[0022] Preferably, the third protrusion is made integrally with the output hub, and the second notch is made integrally with the turbine section.

[0023] Optionally, the first stopping component is a third protrusion arranged on the output hub, and the second stopping component is a third notch arranged on the mass plate.

[0024] Preferably, the third protrusion is made integrally with the output hub, and the third notch is made integrally with the mass plate.

[0025] That is, by providing the first stop member and the second stop member with simple structures as described above, it is possible to facilitate processing, save materials, and achieve higher cost-effectiveness.

[0026] According to an embodiment of the damping system for a hydrodynamic coupling device according to the invention, the first track is formed by a first roller guide groove provided in the annulus, and the second track is formed by a second roller guide groove provided on the turbine section.

[0027] In a more specific implementation according to this embodiment, the mass plate is provided with a third roller guide groove which is identical to the second roller guide groove, and the roller is also axially inserted into the third roller guide groove.

[0028] That is, the roller passes through the first roller guide groove, the second roller guide groove and the third roller guide groove simultaneously in the axial direction. Such an arrangement is beneficial to the synchronous movement of the turbine section and the mass block in the case of torque fluctuation.

[0029] In another embodiment of the damping system for a hydraulic coupling device according to the present invention, a fourth roller guide groove is provided in the annular portion, and each turbine mass assembly further comprises a track insert, which passes through the fourth roller guide groove and is inserted into the turbine section and the mass plate respectively through its axial ends, and wherein the first track is formed by the fourth roller guide groove and the second track is formed by the track insert.

[0030] That is, in this other embodiment, the track insert is fixed to the turbine section and the mass plate, whereby the fixed connection between the turbine section and the mass plate is achieved through the track insert, which can further reduce the number of components of the damping system, simplify assembly, and facilitate axial retention between the turbine section, the output hub and the mass plate.

[0031] In a more specific implementation of this other embodiment of the present invention, a first recess is provided in the turbine section, a corresponding second recess is provided in the mass plate, and the axial ends of the track insert are respectively inserted into the first recess and the second recess to form an interference fit, that is, the fixed connection between the turbine section, the track insert and the mass plate can be achieved without any additional components.

[0032] According to another aspect of the present invention, the present invention also relates to a hydraulic coupling device, comprising the above-mentioned damping system.

[0033] According to yet another aspect of the present invention, the present invention also relates to a motor vehicle comprising the above-mentioned hydraulic coupling device. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings of the embodiments of the present invention are introduced below. The drawings are only used to illustrate some embodiments of the present invention, but not to limit all embodiments of the present invention thereto. In the drawings:

[0035] Figure 1 is a schematic cross-sectional view of a hydraulic coupling device according to the present invention;

[0036] Figure 2 is a schematic diagram of a hydraulic coupling device according to the present invention;

[0037] Figure 3 is a perspective schematic diagram of a first embodiment of a damping system for a hydraulic coupling device according to the present invention, viewed from the turbine section side;

[0038] Figure 4 A first embodiment of a damping system for a hydraulic coupling device according to the present invention is shown in a perspective exploded schematic diagram;

[0039] Figure 5 The schematic diagram partially shows Figure 4 A damping system for a hydraulic coupling device is shown wherein the mass plate is removed;

[0040] Figure 6 Another perspective schematic diagram partially shows Figure 4 A damping system for a hydrodynamic coupling device is shown with the turbine section removed;

[0041] Figure 7 A first variant of the first embodiment of the damping system for a hydraulic coupling device according to the present invention is shown in a perspective schematic diagram;

[0042] Figure 8 The three-dimensional schematic diagram shows Figure 7 A turbine section in the variation shown in ;

[0043] Fig. 9 A second variation of the first embodiment of the damping system for a hydraulic coupling device according to the present invention is shown in a perspective schematic diagram;

[0044] Fig.10 yes Fig. 9 A perspective schematic diagram of the second variant shown in FIG. 1 as viewed from the turbine section side;

[0045] Fig.11 The three-dimensional schematic diagram shows Fig. 9 The output hub in the second variation shown in ;

[0046] Fig.12 The three-dimensional schematic diagram shows Fig. 9 A turbine section of a second variation shown in ;

[0047] Fig.13 A second embodiment of a damping system for a hydraulic coupling device according to the present invention is shown in a perspective exploded schematic diagram;

[0048] Fig.14 The three-dimensional schematic diagram shows Fig.13 The assembled damping system of the second embodiment shown in ;

[0049] Fig.15 Another perspective schematic diagram shows Fig.13 A second embodiment is shown in which the mass plate is removed. DETAILED DESCRIPTION

[0050] In order to make the purpose, technical solution and advantages of the technical solution of the present invention clearer, the technical solution of the embodiment of the present invention will be clearly and completely described in conjunction with the drawings of specific embodiments of the present invention. The same figure marks in the drawings represent the same parts. It should be noted that the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the described embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0051] Unless otherwise defined, the technical terms or scientific terms used herein shall have the usual meanings understood by persons of ordinary skill in the field to which the present invention belongs. The words "first", "second" and similar words used in the patent application specification and claims of the present invention do not indicate any order, quantity or importance, but are only used to distinguish different components. Similarly, words such as "one" or "one" do not necessarily indicate a quantity limitation. Words such as "include" or "comprise" mean that the elements or objects appearing before the word include the elements or objects listed after the word and their equivalents, without excluding other elements or objects. Words such as "connect" or "connected" are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "Up", "down", "left", "right" and the like are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0052] In the sense of the present invention, "axial" means the direction along the central axis X of the output hub of the damping system for the hydraulic coupling device, "radial" means the direction orthogonal to and intersecting the central axis X, "radial outer side (portion)" means the portion farther from the central axis X in the radial direction, "radial inner side (portion)" means the portion closer to the central axis X in the radial direction, and "circumferential" means around the central axis X.

[0053] Figure 1 1 is a schematic cross-sectional view of a hydraulic coupling device 10 according to the present disclosure having a central axis X, to illustrate a structure of the hydraulic coupling device. The hydraulic coupling device 10 may be used in a motor vehicle. Figure 1 The cross section shown in is a cross section cut along the central axis X, that is, the central axis X is located in the cross section, and Figure 1 Only the portion of the hydraulic coupling device 10 located on one side of the central axis X in the cross section is shown.

[0054] Figure 2 2 is a schematic diagram of a hydraulic coupling device 10 according to the present disclosure to schematically illustrate a torque transmission path.

[0055] like Figure 1 Shown and referenced Figure 2 The hydraulic coupling device 10 includes a housing 6, which receives torque from the engine, for example, through a lug 61 fixedly arranged on the radially outer side thereof, so that the housing 6 can rotate around the central axis X. The hydraulic coupling device 10 may also include a pump wheel 1, a turbine 2, and a guide wheel 3 arranged between the pump wheel 1 and the turbine 2 along the direction of the central axis X. The pump wheel 1 can be fixedly connected to the housing 6, for example, by welding, so that when the housing 6 rotates, the pump wheel 1 rotates therewith.

[0056] The fluid coupling device 10 may further include a spring damper 4 and a lockup clutch 5 arranged between the turbine 2 and the housing 6 in the direction of the center axis X. The lockup clutch 5 may be engaged and disengaged with the housing 6 in the direction of the center axis X, for example, the lockup clutch 5 may be engaged with the housing 6 through its radially outer portion 51 facing the housing 6, thereby receiving torque from the housing 6. The drive plate 41 of the spring damper 4 may be fixedly connected to the lockup clutch 5, and its output plate 42 may be fixed to the output hub 101. The output hub 101 may be mounted to the turbine 2, which will be described in detail in the following embodiments.

[0057] When the lock-up clutch 5 is separated from the housing 6, there is no torque transmission between the housing 6 and the spring damper 4, and the rotation of the housing 6 drives the pump wheel 1 fixedly connected thereto to rotate, and the pump wheel 1 then drives the turbine 2 to rotate through the fluid, and then transmits the torque to the transmission input shaft (not shown) via the output hub 101 installed on the turbine 2. This is beneficial when the car starts, and can effectively increase the torque.

[0058] When the lock-up clutch 5 is engaged with the housing 6, the torque from the engine is transmitted to the transmission input shaft via the housing 6, the lock-up clutch 5, the spring damper 4 and the output hub 101. In this case, the torque fluctuation of the internal combustion engine is transmitted to the downstream transmission, and although the spring damper 4 can partially absorb this torque fluctuation, there are still problems in terms of vibration, noise and fuel consumption.

[0059] To this end, the present invention proposes a novel damping system for a hydraulic coupling device.

[0060] Figure 3 is a perspective schematic diagram of a first embodiment of the damping system according to the present disclosure as viewed from the inner side of a turbine. Figure 3 As shown, the turbine 2 includes a plurality of turbine sections 105 distributed in the circumferential direction and in a substantially fan-shaped shape, each turbine section 105 being mounted to the output hub 101 and capable of generating circumferential and radial relative displacements relative to the output hub 101. That is, when the torque is transmitted through the locking clutch 5 and the spring damping system, the turbine section itself constitutes a part of the damping system for the hydraulic coupling device. Thus, when the locking clutch 5 is engaged, the turbine section itself can be further utilized for vibration reduction on the basis of the vibration reduction of the spring damper 4, which makes it possible to further attenuate torque fluctuations, reduce noise, and improve the comfort of the entire vehicle.

[0061] The following references Figure 3-12 The damping system 100 according to the first embodiment of the present disclosure will be described in detail.

[0062] like Figure 4-6 As shown, the damping system 100 may include an output hub 101 , which also has the central axis X mentioned above and has an annular portion 102 surrounding the central axis X.

[0063] The damping system 100 may include a plurality of turbine mass assemblies 104 evenly distributed around a central axis X. In this embodiment, each turbine mass assembly 104 includes a turbine section 105. For clarity, Figure 4-5 Only one of the turbine sections 105 is shown. Each turbine section 105 may carry a plurality of blades (not shown).

[0064] The damping system 100 may further include a roller 107, Figure 4-6 Two rollers 107 are shown in FIG. 1 , which have a generally cylindrical shape. The rollers 107 can roll along the roller tracks so that the turbine mass assembly 104 can move relative to the output hub 101 and exert torque on the output hub 101. Specifically, a first track may be provided in the annular portion 102 of the output hub 101, such as Figure 4-6 As shown, for example, the first track can be formed by a first roller guide groove 103. Two first roller guide grooves 103 are shown in the figure. The turbine section 105 can be provided with a second track corresponding to the first track, for example, the second track can be formed by a second roller guide groove 106 corresponding to the first roller guide groove 103, and is provided on an annular portion of the turbine section 105 close to the central axis X. The roller track is defined by the above-mentioned first track and the second track.

[0065] In a more specific embodiment, as shown in the figure, the first roller guide groove 103 and the second roller guide groove 106 can be set in the form of a waist-shaped hole, which can have an elongated shape, for example. And the protruding direction of the waist-shaped hole forming the first roller guide groove 103 is oriented oppositely to the protruding direction of the waist-shaped hole forming the second roller guide groove 106 in the radial direction, for example, as shown in the figure, the waist-shaped hole forming the first roller guide groove 103 protrudes radially outward, while the waist-shaped hole forming the second roller guide groove 106 protrudes radially inward. The roller 107 is axially inserted into the waist-shaped hole forming the first roller guide groove 103 and the waist-shaped hole forming the second roller guide groove 106.

[0066] The form and arrangement of the first roller guide groove 103 and the second roller guide groove 106 are described here only by way of example, and other forms are also feasible and within the scope of protection of the present invention, for example, they can be arranged in the form of corrugated holes.

[0067] refer to Figure 4-6 In the damping system 100 according to the first embodiment of the present disclosure, each turbine mass assembly 104 may further include a mass plate 108, and the mass plate 108 is fixedly connected to the turbine section 105, for example, by two rivets 120, and the output hub 101 is axially arranged between the mass plate 108 and the turbine section 105. Such an arrangement enables the roller 107 that guides the movement of the turbine mass assembly 104 relative to the output hub 101 to have a relatively uniform axial swing mass distribution, thereby ensuring relatively stable movement of the roller 107 and thus ensuring a more effective oscillation attenuation effect. Further, the mass plate 108 may have a generally annular fan shape, as shown in the figure. The mass plate 108 and the annular portion of the turbine section 105 close to the central axis X are respectively located on both sides of the annular surface portion 102 of the output hub. Also as shown Figure 4-6 As shown, the annular surface portion 102 of the output hub 101 is provided with windows 130, and two windows 130 are shown in the figure, which are used to allow the fixing parts (rivets 120) for fixing and connecting the mass plate 108 and the turbine section 105 to pass therethrough, so that when the turbine mass assembly 104 moves as a whole relative to the output hub 101, the fixing parts (rivets 120) will not interfere with the relative movement.

[0068] The mass plate 108 may have the same weight as the corresponding turbine section 105. Thus, along the axial direction on both sides of the roller, the mass plate 108 and the corresponding turbine section 105 provide a uniform mass distribution, achieving a balanced and stable movement of the roller. Further, the mass plate 108 may also be provided with a third roller guide groove 109 that is the same as the second roller guide groove 106 on the turbine section 105, and the roller 107 may also be axially inserted into the third roller guide groove 109. That is, the roller 107 simultaneously passes through the first roller guide groove 103, the second roller guide groove 106 and the third roller guide groove 109 in the axial direction. Such a setting is conducive to the synchronous movement of the turbine section 105 and the mass block 108.

[0069] In a more specific embodiment, a first stop member is provided on the output hub 101 , and a second stop member is provided on the turbine mass assembly 104 . The first stop member and the second stop member can cooperate to limit the displacement stroke of the turbine mass assembly 104 relative to the output hub 101 .

[0070] In the first embodiment, the first stop member is a first notch 110 provided on the output hub 101. The first notch 110 may be a circumferential notch provided radially outside the output hub 101, which is radially open outward. A second stop member may be provided on the turbine mass assembly 104. Specifically, the second stop member is a first protrusion 111 provided on the mass plate 108. The first protrusion 111 may be formed integrally with the mass plate 108. The first protrusion 111 may protrude from the radial outer edge of the mass plate 108 toward the first notch 110 on the output hub 101, for example, axially protrude into the first notch 110. Thus, the circumferential edge of the first protrusion 111 may be mutually stop-matched with the circumferential edge of the first notch 110 to limit the displacement stroke of the turbine mass assembly 104 relative to the output hub 101. The displacement stroke is less than the stroke of the roller 107 in the roller track.

[0071] Furthermore, the first tab 111 may protrude into the first notch 110 regardless of whether the turbine mass assembly 104 moves radially or circumferentially relative to the output hub 101 .

[0072] In the damping system 100 for a hydraulic coupling device according to the present disclosure, the turbine 2 is divided into a plurality of turbine sections 105 in a roughly fan-shaped shape, for example, three to six turbine sections 105, preferably four turbine sections 105. And when the torque is transmitted through the locking clutch path, the turbine section 105 itself constitutes a component of the damping system 100 for attenuating torque fluctuations. Specifically, when there is torque fluctuation, under the action of inertia, the roller 107 rolling along the roller track defined by the first track provided by the output hub 101 and the second track provided by the turbine mass assembly 104 provides a torque opposite to the torque fluctuation, thereby achieving the effect of attenuating torque fluctuations. And the first stop member provided by the output hub cooperates with the second stop member provided by the turbine mass assembly to limit the relative displacement stroke between them. Thus, when the first stop member and the second stop member cooperate with each other to achieve the stop, the torque is transmitted, and the roller is prevented from being subjected to a strong impact due to collision with the two ends of the rolling track, which may cause damage to the roller, for example, fracture, thereby affecting the attenuation effect or causing the damping system to fail.

[0073] At the same time, in the damping system for the hydraulic coupling device according to the present disclosure, the first stop component is set on the output hub 101 and the second stop component is set on the turbine mass assembly 104. Both are carried out by utilizing the structure of the components themselves, and the manufacturing is simple, ingenious and compact, thereby reducing the number of components and reducing the manufacturing cost.

[0074] Furthermore, in this embodiment, in addition to being fixedly connected to the turbine section 105 , the mass block 108 itself also plays a role in attenuating torque fluctuations together with the turbine section 105 , thereby achieving a better attenuation effect.

[0075] Therefore, in the damping system for the hydraulic coupling device according to the present invention, the first stop component and the second stop component can be simple in structure, easy to process, and save material, thereby achieving higher cost-effectiveness while ensuring effective operation of the damping system.

[0076] Reference below Figure 7-12 A modification of the damping system according to the first embodiment will be described.

[0077] Figure 7 and 8 A first variation of the damping system 100 according to the first embodiment of the present disclosure is shown. Specifically, Figure 7 is a schematic perspective view of the assembled damping system according to the first variant, Figure 8 Only a perspective view of the turbine section is shown to clearly illustrate the second stop member.

[0078] Specifically, Figure 7-8As shown, the first stop member may still be a first notch 110 provided on the output hub 101, and the second stop member may be a second protrusion 112 provided on the turbine section 105. The second protrusion 112 protrudes into the first notch 110. Preferably, the second protrusion 112 may be integrally formed with the turbine section 105, for example, integrally formed by stamping.

[0079] Figure 9-12 A second variation of the damping system 100 of the first embodiment of the present disclosure is shown. Fig. 9 and 10 The assembled damping system 100 according to this second variant is shown in perspective views, respectively from the mass plate 108 side and from the turbine section 105 side. Fig.11 The output hub 101 in the second modification is only schematically shown in a perspective view to clearly show the stopper component on the output hub side. Fig.12 Only one of the turbine sections 105 in the second variant is schematically shown in order to clearly illustrate the stop member on the turbine section side that cooperates with the stop member on the output hub side.

[0080] like Figure 9-12 As shown, the difference between the second variant and the first variant lies in the arrangement of the first stop member and the second stop member that cooperate with each other. In the second embodiment, the first stop member is a third protrusion 113 arranged on the output hub 101, and the second stop member is a second notch 114 arranged on the turbine section 105.

[0081] The third protrusion 113 can be arranged on the radially outer side of the annular portion 102 of the output hub 101, and protrude into the second notch 114 of the turbine section 105. The third protrusion 113 can be formed by bending a portion of the radially outer portion of the annular portion 102 toward the turbine section 105, thereby utilizing the material of the output hub 101 itself. The second notch 114 can be formed by cutting out a portion of the turbine section 105, thereby also utilizing the turbine section itself. Thus, the relative displacement stroke of the two is achieved without adding new parts. Moreover, the output hub 101 and the turbine section 105 can be formed integrally by stamping, and no additional operation of manufacturing the stopper component is required.

[0082] In a third variation not shown according to the first embodiment of the present invention, the first stop member is still the third protrusion 113 arranged on the output hub 101, and the second stop member is a third notch (not shown) arranged on the mass plate 108, and the third protrusion 113 protrudes into the third notch.

[0083] Reference below Figure 13-15A damping system 200 for a hydraulic coupling device according to a second embodiment of the present disclosure is described. The main difference between the damping system 200 and the first embodiment lies in the connection method between the turbine section and the mass plate and the method of forming the roller track. These differences will be emphasized below.

[0084] See also Fig.13 , which is an exploded perspective view of the damping system 200 . Fig.14 is a schematic perspective view of the damping system 200 after assembly. Fig.15 is a schematic perspective view of the damping system 200 with the mass plate 208 removed to clearly illustrate how the roller track is formed.

[0085] In the damping system 200 according to the second embodiment, a fourth roller guide groove 203 may be provided in the annular surface portion 202 of the output hub 101. Fig.13 As shown, a radially outer portion of the fourth roller guide groove 203 may have a shape that is curved radially outward, and a radially inner portion thereof may have a straight shape.

[0086] Each turbine mass assembly 204 may further include a mass plate 208, with the output hub 201 being axially disposed between the turbine section 205 and the mass plate 208. The turbine mass assembly 204 further includes a track insert 206 that passes through the fourth roller guide groove 203. The track insert 206 may be boat-shaped and may have a radially outwardly facing concave surface 2061 that forms a second track and forms a roller track together with the first track formed by the radially outer portion of the fourth roller guide groove 203 disposed in the annular portion 202 of the output hub 201.

[0087] Furthermore, a first recess 221 is provided in the turbine section 205 , and a corresponding second recess 222 is provided in the mass plate 208 . The track insert 206 is inserted into the first recess 221 and the second recess 222 through its axial ends, respectively, to form an interference fit.

[0088] Thus, the first track is formed by the fourth roller guide groove 203, and the second track is formed by the track insert 206, which together define a roller track. The roller 207 can move on such a roller track, and when torque fluctuation occurs, the roller 207 rolling along the roller track provides a torque opposite to the torque fluctuation, thereby achieving the effect of attenuating the torque fluctuation.

[0089] Furthermore, in the second embodiment, the track insert 206 is fixed to the corresponding turbine section 205 and the mass plate 208 by interference fit without other fixing parts, which can further reduce the number of components of the damping system and simplify assembly.

[0090] Further, in the second embodiment, the first stop member is a first notch 210 provided on the output hub 201, and the second stop member is a first protrusion 211 provided on the mass plate 208, which protrudes into the first notch 210. The first protrusion 211 can be formed integrally with the mass plate 208, for example, by stamping.

[0091] The second embodiment may also have different variations. Specifically, the arrangement of the first stop member and the second stop member in the first to third variations of the first embodiment may be applied to Figures 13 to 15 The second embodiment is shown.

[0092] Specifically, in a first modification (not shown) of the second embodiment, the first stopping component may be a first notch provided on the output hub 201 , and the second stopping component may be a second protrusion provided on the turbine section 205 .

[0093] In a second modification (not shown) of the second embodiment, the first stop member is a third protrusion provided on the output hub 201 , and the second stop member is a second notch provided on the turbine section 205 .

[0094] In a third variation (not shown) of the second embodiment, the first stop member is a third protrusion provided on the output hub 201 , and the second stop member is a third notch provided on the mass plate 208 .

[0095] The exemplary implementation scheme of the damping system for a hydraulic coupling device proposed in the present invention is described in detail above with reference to the preferred embodiments. However, it can be understood by those skilled in the art that, without departing from the concept of the present invention, various modifications and variations can be made to the above-mentioned specific embodiments, and various technical features and structures proposed in the present invention can be combined in various ways without exceeding the scope of protection of the present invention.

Claims

1. A damping system for a hydraulic coupling device, comprising: An output hub (101, 201) has a central axis (X) and an annular portion (102, 202) surrounding the central axis (X), wherein a first track is arranged in the annular portion (102, 202). a plurality of turbine mass assemblies (104, 204) uniformly distributed around the central axis (X), each turbine mass assembly (104, 204) comprising a turbine section (105, 205), each turbine section (105, 205) carrying a plurality of blades and provided with a second track corresponding to the first track, a roller (107, 207) capable of rolling along a roller track defined by the first track and a corresponding second track so that the turbine mass assembly (104, 204) can move relative to the output hub (101, 201) and exert a torque on the output hub (101, 201), Each turbine mass assembly (104, 204) further comprises a mass plate (108, 208) fixedly connected to the turbine section (105, 205), and the output hub (101, 201) is arranged between the mass plate (108, 208) and the turbine section (105, 205).

2. The damping system for a hydraulic coupling device according to claim 1, wherein: The mass plate (108, 208) has the same weight as the turbine section (105, 205).

3. The damping system for a hydraulic coupling device according to claim 1, further comprising: A first stop member, arranged on the output hub (101, 201); and A second stop member is disposed on the turbine mass assembly (104, 204), The first stop member and the second stop member can cooperate to limit the displacement stroke of the turbine mass assembly (104, 204) relative to the output hub (101, 201).

4. The damping system according to claim 3, wherein: The first stop component is a first notch (110, 210) arranged on the output hub, and the second stop component is a first protruding piece (111, 211) arranged on the mass plate (108, 208).

5. The damping system according to claim 3, wherein: The first stop component is a first notch (110, 210) arranged on the output hub, and the second stop component is a second protrusion (112) arranged on the turbine section.

6. The damping system according to claim 3, wherein: The first stop component is a third protruding piece (113) arranged on the output hub, and the second stop component is a second notch (114) arranged on the turbine section.

7. The damping system according to claim 3, wherein: The first stop component is a third protruding piece (113) arranged on the output hub, and the second stop component is a third notch arranged on the mass plate (108, 208).

8. The damping system of the hydraulic coupling device according to any one of claims 1 to 7, wherein: The first track is formed by a first roller guide groove provided in the annular portion, and the second track is formed by a second roller guide groove provided on the turbine section.

9. The damping system according to claim 8, wherein: The mass plate is provided with a third roller guide groove (109) identical to the second roller guide groove, and the roller is also axially inserted into the third roller guide groove (109).

10. The damping system for a hydraulic coupling device according to any one of claims 1 to 7, wherein: A fourth roller guide groove (203) is provided in the annular portion. Each turbine mass assembly further comprises a track insert (206), the track insert passing through the fourth roller guide groove (203) and inserted into the turbine section and the mass plate through its axial ends, And wherein, the first track is formed by the fourth roller guide groove (203), and the second track is formed by the track insert (206).

11. The damping system for a hydraulic coupling device according to claim 10, wherein: A first recess (221) is provided in the turbine section, a corresponding second recess (222) is provided in the mass plate, and axial ends of the track insert (206) are respectively inserted into the first recess (221) and the second recess (222) to form an interference fit.

12. A hydraulic coupling device comprising a damping system according to any one of the preceding claims.

13. A motor vehicle comprising a hydraulic coupling device according to claim 12.

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