CN112343963A - Torsional vibration damping system for a hydrodynamic torque coupling - Google Patents
Torsional vibration damping system for a hydrodynamic torque coupling Download PDFInfo
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- CN112343963A CN112343963A CN201910725335.2A CN201910725335A CN112343963A CN 112343963 A CN112343963 A CN 112343963A CN 201910725335 A CN201910725335 A CN 201910725335A CN 112343963 A CN112343963 A CN 112343963A
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- 238000013016 damping Methods 0.000 title claims abstract description 83
- 230000008878 coupling Effects 0.000 title claims abstract description 26
- 238000010168 coupling process Methods 0.000 title claims abstract description 26
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 26
- 230000000712 assembly Effects 0.000 claims abstract description 32
- 238000000429 assembly Methods 0.000 claims abstract description 32
- 230000001970 hydrokinetic effect Effects 0.000 claims abstract description 15
- 230000014759 maintenance of location Effects 0.000 claims description 16
- 230000000717 retained effect Effects 0.000 claims description 8
- 238000004519 manufacturing process Methods 0.000 description 12
- 230000005540 biological transmission Effects 0.000 description 8
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 238000010276 construction Methods 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 208000032370 Secondary transmission Diseases 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000007667 floating Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/12306—Radially mounted springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
- F16F15/1232—Wound springs characterised by the spring mounting
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Abstract
The present invention relates to a torsional vibration damping system for a hydrokinetic torque coupling device, comprising: a piston disc; a retaining disc fixedly connected with the piston disc; a driven plate; a plurality of primary elastic assemblies held radially outside the holding disc; a plurality of secondary elastic members held radially inward of the holding plate; the primary elastic assembly is capable of receiving torque from the holding disc and transmitting the torque to the driven disc when the piston disc rotates, so that the driven disc can rotate relative to the holding disc by an angular stroke: during a first angular stroke, the primary elastic element is compressed and the secondary elastic element is not compressed; during a second angular stroke, the secondary elastic assembly is compressed between the retaining disc and the driven disc, the primary elastic assembly being further compressed; stop windows are provided in the driven plate, stop lugs are provided on the holding plate, which stop lugs abut against the edges of the respective stop windows at the end of the angular travel. The invention also relates to a related hydrodynamic torque coupling device and a motor vehicle.
Description
Technical Field
The present invention relates to a torsional vibration damping system for a hydrodynamic torque coupling device, to a hydrodynamic torque coupling device comprising such a torsional vibration damping system, and to a motor vehicle comprising such a hydrodynamic torque coupling device.
Background
Prior art torsional vibration damping systems for hydrodynamic torque coupling devices typically include a resilient component for transmitting torque and damping vibration, the arrangement of the resilient component, e.g., its size, distribution, stiffness, etc., having a significant effect on the performance of the torsional vibration damping system. In the prior art, in order to meet different requirements of a torsional vibration damping system, the arrangement of an elastic assembly is required to be changed, and the change of the arrangement of the elastic assembly also causes the change of other components for keeping the elastic assembly, namely, the elastic assembly and other related components are required to be specially designed and manufactured according to specific performances, so that the product standardization degree is low, and the cost efficiency is low. Furthermore, existing torsional vibration damping systems typically have only resilient assemblies acting simultaneously, i.e. such resilient assemblies are arranged in a primary damping structure, so that they do not simultaneously satisfy good damping and efficient torque transmission. Also, the conventional torsional vibration damping system often involves an excessive number of component parts and a complicated assembly process, thereby introducing a greater assembly tolerance, so that the system cannot be stably operated, while the manufacturing costs and assembly costs of the component parts are increased accordingly, and it is not advantageous to realize a compact overall configuration.
The aim of the present invention is to overcome at least these drawbacks of the prior art by proposing a torsional vibration damping system for a hydrodynamic torque coupling device which, while ensuring high damping capacity and torque transmission efficiency, is simpler, more standardized, easier to assemble, more compact and therefore more cost-effective.
Disclosure of Invention
To this end, according to one aspect of the present invention, a torsional vibration damping system for a hydrokinetic torque coupling device is presented, having a central axis and comprising:
a piston disc mounted for rotation about the central axis and axially displaceable along the central axis to engage or disengage a torque input housing of the hydrokinetic torque coupling device,
a retaining disc fixedly connected with the piston disc,
a driven disk drivable to rotate about the central axis,
a plurality of primary elastic assemblies retained radially outward of the retention disc, distributed circumferentially about the central axis,
a plurality of secondary elastic assemblies retained radially inward of the retention disc, distributed circumferentially about the central axis,
wherein the primary resilient assembly is capable of receiving torque from the retainer and thereby being compressed between the retainer disc and the driven disc to transmit torque to the driven disc when the piston disc engages the torque input housing such that the driven disc is capable of rotating relative to the retainer disc through an angular stroke in either direction,
within a first angular row of the angular travel, the primary resilient component is compressed and the secondary resilient component is uncompressed,
during a second one of the angular strokes, the secondary resilient assembly is compressed between the retaining disc and the driven disc while the primary resilient assembly is further compressed;
wherein a plurality of stop windows distributed in the circumferential direction are provided in the driven plate, a plurality of stop lugs each protruding into a corresponding stop window are provided on the holding plate, and at the end of the angular stroke, the stop lugs abut against the edges of the corresponding stop windows.
According to such a torsional vibration damping system of the present invention, the configuration in which the retaining plate is fixedly connected with the piston plate while retaining the primary elastic assembly and the secondary elastic assembly reduces the number of component parts of the torsional vibration damping system and ensures an axially more compact configuration to be able to accommodate installation space limitations thereof; at the same time, this also reduces assembly operations and therefore assembly errors that may be introduced, making the torsional vibration damping system more functional, operating more stable and enabling further reduction in manufacturing and assembly costs. In addition, the provision of the secondary damping structure can ensure good vibration damping performance and higher torque transmission efficiency.
And, when transmitting large torque, torque transmission between the holding disc and the driven disc can be achieved by the stop tab abutting against the edge of the stop window, without any longer being achieved by compression of the primary and secondary elastic assemblies, that is, the abutment of the stop tab against the edge of the stop window limits the maximum force exerted on the coil spring, thereby limiting the degree of compression of the coil spring, ensuring that the primary and secondary elastic assemblies are not over-compressed to deteriorate their elastic properties. And, given the arrangement of the primary and secondary elastic assemblies, the stop window and stop tab are configured to be able to define the maximum degree of compression of the primary and secondary elastic assemblies, and the maximum angular travel of the driven disc in either direction relative to the holding disc. In the torsional vibration damping system according to the invention, the maximum angular travel of the holding disk relative to the driven disk can thus be adjusted simply by changing the configuration or arrangement of the stop windows and/or stop tabs, for example by changing the circumferential length of the stop windows and/or stop tabs, and a torsional vibration damping system which meets different requirements is produced without the need for adjustment of the structure of the other components for standardized production, which considerably reduces the design and production costs.
At the same time, such stop windows and stop tabs can be arranged in a simple manner on the driven disk and the holding disk, respectively, without increasing the number of components, are easy to machine, and do not occupy excess space, facilitating a compact arrangement of the torsional vibration damping system.
In a preferred embodiment, a first tab is provided on the outer periphery of the retention disc, the first tab abutting the primary elastic assembly and transmitting torque from the retention disc to the primary elastic assembly; and/or providing a second tab on an outer periphery of the driven disk, the primary resilient assembly transmitting torque to the driven disk through the second tab when compressed.
Further preferably, a retaining window is provided on the retaining disc to retain the secondary resilient assembly, and a third tab is provided on the driven disc radially inward, wherein during the second angular stroke, the secondary resilient assembly is compressed by a circumferential end of the retaining window and the third tab.
The first tab and/or the second tab and/or the retaining window and/or the third tab are structurally simple, easy to manufacture and allow to retain the primary elastic assembly and the secondary elastic assembly in a compact configuration and to allow to effectively achieve a secondary transmission of torque with a simple structure and assembly relationship.
In a further preferred embodiment, the third tab is arranged to extend from a radially inner edge of the stop window. This allows for easy and simple formation of the third tab during formation of the stop window, and allows for full use of the material of the driven disc and contributes to a compact construction, which can save costs.
In a preferred embodiment, the secondary elastic component has a modulus of elasticity which is greater than the modulus of elasticity of the primary elastic component. Such a configuration is advantageous for transmitting torque with higher efficiency while ensuring good damping of torsional vibrations.
In a preferred embodiment, the primary elastic component and/or the secondary elastic component comprises a helical spring. This may ensure that the primary elastic component and/or the secondary elastic component are realized in a simple manner.
Further preferably, the torsional vibration damping system further comprises an intermediate disc including a surrounding portion circumferentially surrounding the primary elastomeric assembly. The intermediate disk can play the role of radial holding and circumferential distribution guiding for the primary elastic component.
Further preferably, the primary elastic assemblies each comprise at least two coil springs in series. That is, such an arrangement of the primary elastic assembly can realize a so-called long stroke damping structure, so that the operational performance of the torsional vibration damping system according to the present invention can be further improved, or by connecting small springs in series to form a large spring, the cost can be greatly reduced while achieving an equivalent operational performance of the torsional vibration damping system.
Further preferably, the intermediate disc is provided with a hook portion that connects the at least two coil springs in series on a radially inner side of the surrounding portion. In this case, the intermediate disk is not in a fixed relationship with other components except for being connected to the coil spring by its hook portion, i.e., the intermediate disk is "floating", which is able to rotate with compression of the coil spring. Such an intermediate disk can serve for radial retention, circumferentially distributed guiding and connecting of the helical springs, while being very simple to manufacture and very easy to assemble, while not occupying additional axial space, so as to further improve the performance of the torsional vibration damping system according to the invention.
According to another aspect thereof, the invention also relates to a hydrokinetic torque coupling device comprising a torsional vibration damping system according to the above.
Preferably, in the hydrodynamic torque coupling device according to the present invention, the driven disk of the torsional vibration damping system is fixed with the turbine.
According to a further aspect thereof, the invention also relates to a motor vehicle comprising a hydrodynamic torque coupling device as described above.
Drawings
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 will be briefly described below. Wherein the drawings are only for purposes of illustrating some embodiments of the invention and are not to be construed as limiting the invention to all embodiments thereof. In the drawings:
FIG. 1 illustrates a partial schematic view, taken along a central axis, of a hydrokinetic torque coupling device including a torsional vibration damping system in accordance with an embodiment of the present invention;
FIG. 2 illustrates a top view of portions of a torsional vibration damping system in accordance with an embodiment of the present invention with the driven disk removed to illustrate the retaining disk, the primary elastic assembly, and the secondary elastic assembly;
FIG. 3 shows an isometric view of the portion shown in FIG. 2;
FIG. 4 illustrates an exploded perspective view of a torsional vibration damping system in accordance with an embodiment of the present invention;
FIG. 5 illustrates a perspective view of a torsional vibration damping system according to an embodiment of the present invention mounted with a turbine wheel of a hydrokinetic torque coupling device, with the turbine wheel and driven disk partially cut away;
FIG. 6 illustrates a perspective view of a torsional vibration damping system according to an embodiment of the present invention installed with a turbine of a hydrokinetic torque coupling device, with the turbine partially cut away;
FIG. 7 illustrates a perspective view of a retaining disk used in the torsional vibration damping system in accordance with an embodiment of the present invention;
FIG. 8 illustrates a perspective view of a driven disk used in the torsional vibration damping system in accordance with an embodiment of the present invention;
FIG. 9a shows an enlarged partial top view of a driven disk used in the torsional vibration damping system according to an embodiment of the present invention, showing the stop windows therein;
9b-9c illustrate two embodiments of driven discs that may be used in the torsional vibration damping system of embodiments of the present invention;
FIG. 10 shows a schematic of secondary damping by a torsional vibration damping system according to an embodiment of the invention;
FIG. 11 illustrates a perspective view of a driven disk and turbine subassembly including a driven disk used in a torsional vibration damping system in accordance with an embodiment of the present invention;
FIG. 12 shows an exploded perspective view of the subassembly according to FIG. 11;
FIG. 13 illustrates an exploded perspective view of a hydrokinetic torque coupling device including a torsional vibration damping system according to the present invention, in accordance with an embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings of specific embodiments of the present invention. Like reference symbols in the various drawings indicate like elements. It should be noted that the described embodiments are only some embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the invention without any inventive step, are within the scope of protection of the invention.
Unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this invention belongs. The use of "first," "second," and similar terms in the description and claims of the present application do not denote any order, quantity, or importance, but rather the terms are used to distinguish one element from another. Also, the use of the terms "a" or "an" and the like do not necessarily denote a limitation of quantity. The word "comprising" or "comprises", and the like, means that the element or item listed before the word covers the element or item listed after the word and its equivalents, but does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
In the sense of the present invention, "axial" means a direction along the central axis X of the torsional vibration damping system 2, "radial" means a direction orthogonal to and intersecting the central axis X, "radially outer (portion)" means a portion farther from the central axis X in the radial direction, "radially inner (portion)" means a portion closer to the central axis X in the radial direction, "circumferential" means a portion surrounding the central axis X.
Fig. 1 shows a schematic representation of a hydrodynamic torque coupling device 1 according to an embodiment of the invention, comprising a torque input housing 8, a torsional vibration damping system 2 according to the invention arranged inside the torque input housing 8, a hydrodynamic torque converter 11.
As shown in fig. 1-8, according to this embodiment, the torsional vibration damping system 2 has a central axis X and includes:
a piston disc 3 located inside the torque input housing 8 and mounted to be rotatable about the central axis X, and the piston disc 3 being axially displaceable along the central axis X to engage or disengage the torque input housing 8 of the hydrokinetic torque coupling device 1 and to receive torque therefrom when the piston disc 3 is engaged with the torque input housing 8 and thus rotate integrally therewith;
a retaining disc 4, which is fixedly connected with the piston disc 3. In a particular embodiment, the retaining disc 4 is located on the opposite side of the piston disc 3 relative to the torque input housing 8 and may be fixed to the piston disc 3 by any fixing means so as to be rotatable and axially displaceable integrally with the piston disc 3. For example, as in the particular embodiment shown in fig. 2-7, axially opposed apertures 25 and 26 are provided in the retaining disc 4 and the piston disc 3, respectively, with rivets 24 passing through the opposed apertures 25 and 26 to secure the retaining disc 4 to the piston disc 3. Preferably, a plurality of orifices 25 and 26 are provided, respectively, regularly distributed around the central axis X on the retention disc 4 and on the piston disc 3, in order to fixedly connect the retention disc 4 with the piston disc 3 in a simple and stable manner;
a driven disc 5 which can be driven in rotation about said central axis X,
a plurality of primary elastic assemblies 6, preferably three to six primary elastic assemblies 6, more preferably four primary elastic assemblies 6, which are retained radially outside retaining disc 4, are distributed circumferentially around central axis X, i.e. the primary elastic assemblies 6 so arranged are able to act circumferentially, as shown in fig. 2-6;
a plurality of secondary elastic assemblies 7, preferably three to six secondary elastic assemblies 7, more preferably four secondary elastic assemblies 7, which are retained radially inside the retaining disc 4, are distributed circumferentially around said central axis (X), i.e. the secondary elastic assemblies 7 so arranged are able to act circumferentially, as shown in fig. 2-5.
In a particular embodiment, as shown in fig. 2-8, the primary elastic assembly 6 and/or the secondary elastic assembly 7 comprise a helical spring. That is, in such an embodiment, at least one of the primary elastic assembly 6 and the secondary elastic assembly 7 may be constituted by a coil spring. This may ensure that the primary elastic assembly 6 and/or the secondary elastic assembly 7 are realized in a simple manner.
In this embodiment, the torsional vibration damping system 2 according to the present invention is constructed such that, upon axial displacement of the piston disc 3 relative to the torque input housing 8 and engagement of the torque input housing 8 to receive torque therefrom and rotate integrally therewith, the retaining disc 4 fixedly connected to the piston disc 3 therefore also receives torque from the torque input housing 8 with the piston disc 3 and rotates integrally therewith, so that the primary elastic assembly 6 held by the holding disc 4 can receive torque from the holding disc 4 and is thereby compressed between the holding disc 4 and the driven disc 5 to transmit torque to the driven disc 5, so that the driven disc 5 can be rotated in either direction by an angular stroke a (figures 9a-9c) relative to the holding disc 4, during a first angular travel α 1 of the angular travel α, which is passed by the previous rotation, the primary elastic element 6 is compressed, the secondary elastic element 7 is not compressed; during a second angular stroke α 2 of this angular stroke α, following the angular stroke α 1, the secondary elastic assembly 7 is compressed between the holding disk 4 and the driven disk 5, while the primary elastic assembly 6 is further compressed. That is, during the second angular stroke α 2, both the primary elastic assembly 6 and the secondary elastic assembly 7 are compressed.
Here, the angular stroke α is the maximum angular stroke by which the driven disk 5 can be driven to rotate in either direction with respect to the holding disk 4, and α ═ α 1+ α 2.
The torsional vibration damping system 2 according to the invention is thus constructed as a secondary damping system comprising a primary damping consisting of a primary elastic component 6 and a secondary damping consisting of a secondary elastic component 7. As shown in fig. 10, wherein the abscissa of fig. 10 represents the relative angular travel (as evidenced by the counterclockwise direction indicated by arrow F in fig. 2, and negative in the clockwise direction) between driven disk 5 and holding disk 4, the ordinate represents the torque transmitted by primary elastic assembly 6 and secondary elastic assembly 7 with this relative angular travel. As represented by the curve P1 in fig. 10, the first segment P11 thereof shows the primary damping process, corresponding to the above-mentioned first angular stroke α 1, in which only the primary elastic assembly 6 is compressed and transmits torque; the second segment P12 of the curve P1 illustrates a secondary damping process, corresponding to a second segment angular travel α 2, in which the secondary elastic assembly 7 is compressed and at the same time the primary elastic assembly 6 continues to be compressed together, as shown, the slope of this second segment P12 being greater than the first segment P11. Curve P2 also has a two-stage configuration similar to curve P1, but with a different angular travel, spring assembly stiffness coefficient than that represented by P1. This configuration makes it possible to activate, in the initial phase of the torque transmission, only the primary damping process, i.e. only the primary elastic assembly 6 is active, in which case the relative angular travel between the driven disc 5 and the holding disc 4 is less than or equal to the first angular travel α 1; when the torque increases, a secondary damping process is activated, the relative angular travel between the driven disc 5 and the holding disc 4 exceeds a first angular travel α 1, the secondary elastic assembly 7 is activated and compressed, while the primary elastic assembly 6 is further compressed, so that the driven disc 5 continues to rotate with respect to the holding disc 4 to produce a total relative angular travel less than or equal to the angular travel α.
Furthermore, the retaining disc 4 is fixedly connected to the piston disc 3 and at the same time the retaining disc 4 retains the primary and secondary elastic assemblies 6, 7, which embodiment reduces the number of component parts of the torsional vibration damping system 2 and ensures an axially more compact construction to be able to accommodate installation space limitations thereof; at the same time, this also reduces assembly operations and therefore assembly errors that may be introduced, making the torsional vibration damping system 2 more functional, operating more stable and enabling further reductions in manufacturing and assembly costs. The torsional vibration damping system 2 according to the invention thus enables good vibration damping and efficient torque transmission with a simple construction and low costs.
In a preferred embodiment, the modulus of elasticity of the secondary elastic component 7 is greater than the modulus of elasticity of the primary elastic component 6. I.e. the secondary elastic component 7 has a greater stiffness than the primary elastic component 6. Such a configuration is advantageous for transmitting torque with higher efficiency while ensuring good damping of torsional vibrations.
Of course, the elastic modulus of the secondary elastic member 7 may be set to be as large as or smaller than the elastic modulus of the primary elastic member 6 according to actual needs. The preferred embodiments described above are merely exemplary.
In a particular embodiment, as shown in fig. 2-7, a first tab 12 is provided on the outer periphery of the retention disc 4, the first tab 12 abutting the primary elastic assembly 6 and being capable of transmitting torque from the retention disc 4 to the primary elastic assembly 6. Preferably, the first tab 12 is integrally formed with the retention tray 4. As shown, for example, a plurality of first tabs 12 are provided along the outer periphery of the retention disc 4, each of which is located between two adjacent primary elastic assemblies 6 and abuts, at each circumferential end, a circumferential end of one of the two adjacent primary elastic assemblies 6. Optionally, the primary elastic assembly 6 is arranged to be retained by the piston disc 3 in one axial direction. As a further alternative, as shown in fig. 2-6 and 8, second tabs 13 are provided on the outer periphery of driven disk 5, primary elastic assembly 6 transmitting torque to driven disk 5 through second tabs 13 when compressed. Preferably, the second tab 13 is integrally formed with the driven disc 5. As shown, for example, a plurality of second tabs 13 are provided along the outer periphery of the driven disk 5, each second tab 13 being placed between two adjacent primary elastic assemblies 6.
Thus, when the piston disc 3 engages the torque input housing 8, the retention disc 4 fixedly connected with the piston disc 3 receives torque from the torque input housing 8 with the piston disc 3 and thereby rotates, for example, in a counterclockwise direction (shown by arrow F in fig. 2) such that the first tabs 12 press against the primary resilient assembly 6 in the counterclockwise direction through the first circumferential end 6a (shown in fig. 2 and 5) of the primary resilient assembly 6 in abutment therewith, thereby transmitting torque to the primary resilient assembly 6 in the counterclockwise direction, the primary resilient assembly 6 being correspondingly loaded and compressed in the counterclockwise direction such that the second circumferential end 6b (shown in fig. 2 and 5) of the primary resilient assembly 6 abuts the immediately adjacent second tabs 13, thereby transmitting torque to the driven disc 5 through the second tabs 13.
As shown in fig. 2-5 and 7, in a particular embodiment, a retaining window 14 is provided on the retaining disc 4, which retaining secondary elastic component 7 is preferably formed integrally with retaining disc 4. Optionally, in a state in which the secondary elastic assembly 7 is not compressed, the secondary elastic assembly 7 is jammed in the respective retaining window 14 by means of a first circumferential end 7a and a second circumferential end 7b (shown in fig. 2). Optionally, the secondary elastic component 7 is arranged to be retained by the piston disc 3 in one axial direction. Further optionally, a third tab 15 is provided on the driven disc 5 radially inside, preferably the third tab 15 is provided integrally with the driven disc 5. During a second angular stroke α 2 of driven disc 5 with respect to retaining disc 4, secondary elastic assembly 7 is compressed between the respective circumferential end of retaining window 14 and third tab 15. I.e. in a first angular stroke α 1 of driven disc 5 with respect to retaining disc 4, third tab 15 does not contact secondary elastic assembly 7, at the end of first angular stroke α 1, third tab 15 contacts secondary elastic assembly 7, and after the start of a second angular stroke α 2 of driven disc 5 with respect to retaining disc 4, secondary elastic assembly 7 is compressed between third tab 15 and the corresponding circumferential end of retaining window 14.
Thus, still taking the example in which the piston disc 3 rotates in the counterclockwise direction, when the transmission torque is sufficiently large, the relative rotational stroke of the driven disc 5 with respect to the holding disc 4 becomes sufficiently large, i.e. enters the second angular stroke α 2, so that the second circumferential ends 7b of the secondary elastic assemblies 7 held by the holding windows 14 of the holding disc 4 abut against the respective third tabs 15, and thereby the secondary elastic assemblies 7 are compressed between the third tabs 15 and the first circumferential ends 7a of the holding windows 14 holding the secondary elastic assemblies 7, so that a part of the torque is transmitted from the holding disc 4 to the driven disc 5 by the secondary elastic assemblies 7, while the primary elastic assemblies 6 are further compressed and transmit another part of the torque from the holding disc 4 to the driven disc.
The first tab 12 and/or the second tab 13 and/or the retaining window 14 and/or the third tab 15 are structurally simple, easy to manufacture and allow to retain the primary elastic assembly 6 and the secondary elastic assembly 7 in a compact configuration and to allow to effectively achieve a secondary transmission of torque with a simple structure and assembly relationship.
In a preferred embodiment, as shown in fig. 6 and 8, a plurality of circumferentially distributed stop windows 9, preferably three to six, more preferably four, are provided in the driven disk 5, and a plurality of stop tabs 10, preferably formed integrally with the holding disk 4, each projecting into a respective stop window 9, are provided on the holding disk 4, the stop tabs 10 stopping against the edges 9a,9b of the respective stop windows 9 at the end of the angular travel α. Thus, when a large torque is transmitted, the torque transmission between the retaining disk 4 and the driven disk 5 is achieved by the abutment of the stop tabs 10 against the edges 9a,9b, without being achieved by the compression of the primary elastic assembly 6 and the secondary elastic assembly 7, that is to say, the abutment of the stop tabs 10 against the edges of the stop windows 9 limits the maximum force exerted on the helical springs, thus limiting the degree of compression of the helical springs, ensuring that the primary elastic assembly 6 and the secondary elastic assembly 7 are not excessively compressed to deteriorate their elastic properties.
And, as shown in fig. 9a-9c, given the arrangement of the primary and secondary elastic assemblies 6 and 7, the stop window 9 and the stop tab 10 are configured so as to be able to define the maximum angular travel a of the driven disc 5 with respect to the holding disc 4 in either direction, and the maximum degree of compression of the primary and secondary elastic assemblies 6 and 7. Fig. 9a shows a driven disk 5 ' shown in fig. 9b and a driven disk 5 ″ shown in fig. 9c superimposed for comparison, the driven disk 5 ″ being located below the driven disk 5 ' and the stop window of the driven disk 5 ″ being substantially opposite to the stop window of the driven disk 5 ' in the viewing angle in fig. 9 a. As shown in fig. 9a, the circumferential length of the stop window 9 "is greater than the circumferential length of the stop window 9'. Thus, with the same stop tab 10, the maximum angular travel obtainable with a driven disc 5 "having a stop window 9" is greater than that obtainable with a driven disc 5 'having a stop window 9'. Similarly, in the case of using driven discs with the same stop window, varying the length of the stop tab 10 also makes it possible to obtain different maximum angular strokes. The stop window and stop tab may both be adjusted. Thus, in the torsional vibration damping system 2 according to the invention, the maximum angular travel a of the holding disk 4 relative to the driven disk 5 can be adjusted simply by changing the configuration or arrangement of the stop windows 9 and/or the stop tabs 10, for example by changing the circumferential length of the stop windows 9 and/or the circumferential length of the stop tabs 10, producing a torsional vibration damping system which meets different requirements, while the structure of the other components does not need to be adjusted for standardized production, which greatly reduces the design and production costs.
Further preferably, as shown in fig. 6 and 8, the third tab 15 is arranged to extend from a radially inner edge 17 of the respective stop window 9. This allows for easy and simple formation of the third tab during formation of the stop window 9, and enables full use of the material of the driven disc 5 and contributes to a compact construction, which can be cost-effective.
In a further specific embodiment, as shown in fig. 7, the retention disk 4 has an annular surface portion 27, and the first tab 12 is disposed along an outer periphery 27a of the annular surface portion 27 and may extend to protrude outward from the outer periphery 27 a. More specifically, the holding window 14 is provided along the inner periphery 27b of the ring surface portion 27 and may protrude inward from the inner periphery 27 b. Further, the stop tab 10 may also be disposed along the inner periphery 27b of the ring surface portion 27 and may protrude from the inner periphery 27 b. Such a configuration ensures a compact construction of the holding pan 4 with a higher material utilization and enables the first tab 12 and/or the holding window 14 and/or the stop tab 10 to be easily made, reducing material and manufacturing costs.
A specific embodiment of the primary elastic assembly 6 and the secondary elastic assembly 7 will now be described with reference to fig. 2-6. The torsional vibration damping system 2 according to this embodiment preferably further comprises an intermediate disc 18, which intermediate disc 18 comprises a surrounding portion 19 that circumferentially surrounds the primary elastic assembly 6. The intermediate disk 18 thus acts as a radial holding and circumferentially distributed guide for the primary elastic component 6.
In one embodiment, as shown in fig. 2-6, the primary elastic assembly 6 comprises at least two helical springs 20,21 in series, i.e. this arrangement of the primary elastic assembly 6 allows a long stroke damping structure to be achieved at low cost. The long spring is expensive, and the small springs are connected in series to form the spring assembly, so that the cost can be greatly reduced under the condition of realizing the working performance of the same torsional vibration damping system.
Of course, other configurations of the primary elastic assembly 6 and/or the secondary elastic assembly 7 are possible. For example, in a variant not shown, each helical spring of the primary elastic assembly 6 and/or of the secondary elastic assembly 7 may be formed by a large-diameter external helical spring and a small-diameter helical spring arranged inside the large-diameter external helical spring.
It is also preferred that the intermediate disc 18 further comprises a hook 22 arranged radially inside the surrounding part 19, as shown in fig. 2-6, the hook 22 being intended to connect and hold together said at least two helical springs 20,21 in series. In this case, the intermediate disk 18 is not in a fixed relationship with other components except for being connected to the coil springs 20,21 by its hook 22, i.e., the intermediate disk 18 is "floating" and is able to rotate with compression of the coil springs 20, 21. Such an intermediate disk 18, while providing the radial retention, circumferentially distributed guiding and connecting action for the helical springs 20,21, is at the same time very simple to manufacture and very easy to assemble, while at the same time not taking up additional axial space, thus further improving the performance of the torsional vibration damping system 2 according to the invention.
According to a further preferred embodiment, as shown in fig. 2 to 7, the first tabs 12 of the retention disc 4 are configured so as to prevent the intermediate disc 18 from being axially offset with respect to the primary elastic assembly 6. For example, as shown in fig. 2 and 7, the first tab 12 is configured to have an axially extending portion 12c and a bent portion 12b bent radially outward from the axially extending portion 12c, and in the assembled state, the axially extending portion 12c of the first tab 12 abuts against the corresponding primary elastic assembly 6 to apply a force to the primary elastic assembly 6, and at this time, the bent portion 12b is axially opposite to the surrounding portion 19 of the intermediate disc 18 to be able to axially retain the retaining disc 18. This embodiment enables a relatively stable holding of the disc 18 in a simple manner, in a compact construction, thereby facilitating a stable operation of the torsional vibration damping system 2 according to the invention.
It should be noted that the various embodiments described above are merely illustrative and should not be construed as limiting the invention. And combinations between the various embodiments described above are possible unless technically such combinations are not allowed.
According to another aspect of the invention, the invention also relates to a hydrokinetic torque coupling device 1 comprising the torsional vibration damping system 2 described above, as shown in fig. 11-13. As shown in fig. 11, the driven plate 5 of the torsional vibration damping system 2 described above is fixedly connected, for example by riveting, to the turbine 23 of the torque converter 11. The turbine 23 can thereby be displaced axially with the piston disc 3 together with the driven disc 5.
The invention also relates to a motor vehicle comprising a hydrodynamic torque connection 1 as described above.
While the exemplary embodiment of the torsional vibration damping system for hydrokinetic torque connections proposed by the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art will appreciate that numerous variations and modifications may be made to the specific embodiments described above and that numerous combinations of the various features and structures proposed by the present invention may be made without departing from the concepts of the present invention without departing from the scope of the invention.
Claims (12)
1. A torsional vibration damping system (2) for a hydrokinetic torque coupling device (1), having a central axis (X) and comprising:
a piston disc (3) mounted to be rotatable about the central axis (X) and axially displaceable along the central axis (X) to engage or disengage a torque input housing (8) of the hydrokinetic torque coupling device (1),
a retaining disc (4) which is fixedly connected to the piston disc (3),
a driven disc (5) drivable in rotation about said central axis (X),
a plurality of primary elastic assemblies (6) retained radially outside the retaining disc (4), distributed circumferentially around the central axis (X),
a plurality of secondary elastic assemblies (7) retained radially inside the retaining disc (4), distributed circumferentially around the central axis (X),
wherein the primary elastic assembly (6) is capable of receiving torque from the holding disc (4) and thereby being compressed between the holding disc (4) and the driven disc (5) to transmit torque to the driven disc (5) when the piston disc (3) engages the torque input housing (8) such that the driven disc (5) is capable of rotating relative to the holding disc (4) by an angular stroke (a) in either direction,
during a first angular stroke (a 1) of the angular stroke (a), the primary elastic assembly (6) is compressed and the secondary elastic assembly (7) is not compressed,
-during a second angular stroke (a 2) of said angular stroke (a), said secondary elastic assembly (7) is compressed between said retaining disc (4) and said driven disc (5), while said primary elastic assembly (6) is further compressed;
wherein a plurality of stop windows (9) distributed in the circumferential direction are provided in the driven plate (5), a plurality of stop tabs (10) each protruding into a respective stop window (9) are provided on the holding plate (4), and at the end of the angular travel (α), the stop tabs (10) stop against the edges (9a,9b) of the respective stop windows (9).
2. The torsional vibration damping system (2) of claim 1,
-providing a first tab (12) on the outer periphery of the retaining disc (4), said first tab (12) abutting the primary elastic assembly (6) and transmitting a torque from the retaining disc (4) to the primary elastic assembly (6); and/or
-providing a second tab (13) on the outer circumference of the driven disc (5), the primary elastic assembly (6) transmitting a torque to the driven disc (5) through the second tab (13) when compressed.
3. The torsional vibration damping system (2) according to claim 1 or 2,
-a retaining window (14) for retaining the secondary elastic component (7) is provided on the retaining disk (4), a third tab (15) is provided on the driven disk (5) radially on the inside,
wherein, in the second angular stroke, the secondary elastic assembly (7) is compressed by the circumferential end of the retention window (14) and the third tab (15).
4. The torsional vibration damping system (2) of claim 3,
the third tab (15) is arranged to extend from a radially inner edge (17) of the stop window (9).
5. The torsional vibration damping system (2) according to claim 1 or 2,
the secondary elastic component (7) has a modulus of elasticity which is greater than the modulus of elasticity of the primary elastic component (6).
6. The torsional vibration damping system (2) according to claim 1 or 2,
the primary elastic assembly (6) and/or the secondary elastic assembly (7) comprise a helical spring.
7. The torsional vibration damping system (2) of claim 6,
further comprising an intermediate disc (18), the intermediate disc (18) comprising a surrounding portion (19) circumferentially surrounding the primary elastic assembly.
8. The torsional vibration damping system (2) of claim 7,
the primary elastic assemblies (6) each comprise at least two helical springs (20,21) connected in series.
9. The torsional vibration damping system (2) of claim 8,
the intermediate disc (18) is provided with a hook (22) on the radially inner side of the surrounding part (19) connecting the at least two helical springs (20,21) in series.
10. A hydrokinetic torque coupling device (1) comprising a torsional vibration damping system (2) according to any of the preceding claims.
11. Hydrodynamic torque coupling device (1) according to claim 10,
wherein the driven disk (5) of the torsional vibration damping system (2) is fixed with a turbine (23).
12. A motor vehicle comprising a hydrokinetic torque coupling device (1) as defined in claim 10 or 11.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910725335.2A CN112343963A (en) | 2019-08-07 | 2019-08-07 | Torsional vibration damping system for a hydrodynamic torque coupling |
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| CN201910725335.2A CN112343963A (en) | 2019-08-07 | 2019-08-07 | Torsional vibration damping system for a hydrodynamic torque coupling |
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