CN112196946B

CN112196946B - Torsional vibration damper

Info

Publication number: CN112196946B
Application number: CN202010650577.2A
Authority: CN
Inventors: F·西曼; A·库比什; K·比迪克; C·凯勒; E·霍夫曼; B·科布; A·基里安; T·辛德勒; P·葛斯特; D·比尔; A·艾克
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2019-07-08
Filing date: 2020-07-08
Publication date: 2024-06-25
Anticipated expiration: 2040-07-08
Also published as: CN112196946A; DE102019209997A1

Abstract

The invention relates to a torsional damper (100) comprising an input element (140) and output elements (150-1) and (150-2) arranged axially relative to the input element. The input element (140) and the output element (150-1) and/or (150-2) are arranged movably relative to each other in the axial direction. The torsional damper (100) further comprises at least one helical spring (110) and/or (120) which can be coupled to the input element (140) and the output element (150-1) and/or (150-2) at spring ends (112) which are arranged opposite in circumferential direction. The helical springs (110) and/or (120) are designed and arranged for exerting an axial force (118-1) or (118-2) on at least the output element (150-1) and/or (150-2) or the input element (140) in the event of a deformation in the circumferential direction, said axial force acting on a further component (160) of the torsional damper (100) which axially separates the input element (140) and the output element (150-1) and/or (150-2) from one another.

Description

Torsional vibration damper

Technical Field

The present invention relates to a torsional damper and a clutch disc. In particular, but not exclusively, the invention relates to a torsional damper and a clutch disc for a powertrain of a vehicle.

Background

Torsional vibration dampers, for example, may be used to dampen torsional vibrations within a powertrain of a vehicle, for example. Such torsional vibrations may be caused, for example, by the drive motor of the vehicle. Damping torsional vibrations may be used, for example, to reduce wear of components of the powertrain and/or to improve driving comfort.

Torsional vibration dampers comprise, for example, an input member and an output member, which are elastically coupled to each other (e.g., by means of a coil spring) to dampen torsional vibrations. The helical springs may be elastically deformed against rotation of the input member and the output member with damping of torsional vibrations and/or with transmission of torque. Depending on the winding and/or arrangement of the spiral spring, this spiral spring can introduce axial forces into the input element and/or into the output element. The axial forces may, for example, cause the input element and/or the output element to deflect and/or tilt axially from a position that is advantageous for the function of the torsional damper. Other components of the torsional vibration damper which interact with the input element and/or the output element and are supported axially on the input element and/or the output element, for example, can thus be adversely affected in terms of their function and/or their wear.

A clutch disk is known from DE 10 2013 221 103 A1, which comprises a pressure spring stack having a plurality of helical springs with partially opposite pitches. The invention disclosed in this document, for example, proposes to increase the spring capacity of the coupling between the input element and the output element of the clutch disk.

Furthermore, publication DE 196 11 5051 a1 discloses a torsional vibration damper in which springs, by means of which the input and output parts of the torsional vibration damper are coupled, are supported on a pivotably mounted base. The support of the spring on the pivotably mounted base can for example achieve reduced wear.

Document DE 19638613 A1 discloses a clutch-driven disk mechanism with a driven disk and a cover plate with a plurality of spring openings in each case. The disc mechanism further includes a plurality of springs disposed in the spring openings. A cover section for securing the springs is arranged on each end of each spring, respectively, which cover section comprises a bolt section which engages into the springs. The bolt section, for example, prevents the spring from buckling when it compresses.

An embodiment of a spring assembly for a torsional damper is disclosed in document EP 3 026 293 A1. The spring stack comprises a coil spring and a support element having a disk section and a stepped section for actuating the coil spring. For improved centering, the abutment surface of the step designed on the step section comprises an abutment surface having a first centering surface and a second centering surface corresponding to this first centering surface.

Publication US 5 626 518 describes a device for damping a torque. The apparatus includes a hub and a disc disposed axially offset from the hub. The apparatus also includes base sections disposed between each of the hub, the disk, and a spring that resiliently couples the hub and the disk. The base section has a side section for contacting an end face of the spring arranged in the circumferential direction for this purpose. Furthermore, the base section comprises a further side section with an extended holding section which can be clamped in a guide section of the hub in order to axially fix the base section relative to the disk and the hub.

No solution is known from the prior art for improving the torsional damper with respect to the function and wear of the components interacting with the input and/or output members.

Disclosure of Invention

It may therefore be seen as an object of the present invention to propose a torsional damper which is improved at least in terms of function or wear.

This object is achieved in accordance with the torsional vibration damper and clutch disc of the present disclosure.

According to a first aspect, the invention relates to a torsional damper comprising an input member and an output member arranged axially opposite the input member. The input member and the output member are movably arranged with respect to each other in an axial direction. The torsional damper further comprises at least one helical spring which can be coupled with the input member and the output member at spring ends which are arranged opposite in circumferential direction. The helical spring is designed and arranged for exerting an axial force on at least the output piece or the input piece in the event of a deformation in the circumferential direction, said axial force acting toward a further component of the torsional damper which axially separates the input piece and the output piece from one another.

The input element may be, for example, a driven disc and the output element may be a metallic cover plate of a clutch disc. The driven disc and the metallic cover plate can be rotatably arranged relative to each other coaxially on the hub. In the case of clutch disks, the driven disk can be rotatably mounted on the hub, for example, and the metal cover plate can be connected to the hub in a rotationally fixed manner. For example, in order to be able to ensure a low-friction relative rotation of the input and output elements, the input and output elements can have a play in relation to each other in the axial direction and thus be movable in relation to each other in the axial direction. Due to the play, axial transverse forces (which in conventional torsional dampers may act on the input element or the output element) may cause tilting and/or axial deflection of the input element and/or the output element.

The helical spring (comprising a plurality of coils about a common spring axis) may be disposed in window openings that are aligned with one another if the input and output members are not rotated relative to one another. In the case of relative rotation, the coincidence of the window openings can be reduced in the circumferential direction. The helical springs arranged in the window openings can be coupled indirectly or directly to the input element or to the output element on the respective side of the window openings which is opposite in the circumferential direction. The helical spring can, for example, bear against the window openings on the sides of the window openings that are opposite in the circumferential direction.

Since the helical spring is coupled to the input element and the output element, it can undergo a deformation in the circumferential direction when the input element and the output element are rotated relative to each other, wherein the helical spring applies a force against the relative rotation to the output element and the input element, for example.

In the event of a deformation of the spiral spring, this generates a torque about its spring axis, whereby the spiral spring exerts an axial force on the component to which it is coupled. Depending on the arrangement of the input and output elements in the torsional damper, the helical springs are designed and arranged such that the axial forces applied to the input and/or output elements upon deformation in the circumferential direction act in the axial direction towards the further components of the torsional damper. Further components are arranged, for example, axially between the input element and the output element, so that the input element and the output element are spaced apart in the axial direction.

In several embodiments of the invention, the output element may be arranged on the transmission side with respect to the input element, and the helical spring may be embodied as a left-hand wound helical spring.

The output element arranged on the transmission side is arranged, for example, on the axial side of the torsional damper facing the transmission. In contrast to this, the input element is arranged, for example, on the motor side, i.e. on the axial side of the torsional damper facing the motor. In case the input and output members are arranged correspondingly, a left-hand wound helical spring may advantageously be used to elastically couple the input and output members. In the case of a deformation of the left-hand coiled spiral spring, this spiral spring can exert an opposite torque and thus an opposite axial force with respect to the right-hand coiled spiral spring.

In the load mode, this can cause a relative rotation of the input element arranged on the motor side with respect to the output element on the transmission side, wherein the input element rotates clockwise with respect to the output element, for example, depending on the application, from the perspective of the transmission side. In the case of a left-hand wound helical spring which is deformed in the circumferential direction in this case, this helical spring applies an axial force, for example, which is directed toward an input element arranged on the motor side, to an output element arranged on the transmission. Alternatively or additionally, a left-hand wound helical spring can apply a force directed towards an output piece arranged on the transmission side to an input piece on the motor side. Thus, axial forces acting on the input and/or output element act in the axial direction in the direction towards further components which respectively space the input and output element from each other in the axial direction.

In several embodiments of the invention, the axially spaced apart components may include friction means which apply axial pressure to the input and output members, respectively, to generate a friction torque.

In order to damp torsional vibrations, friction devices may generate friction torque between the input member and the output member. The friction device comprises, for example, a friction ring and a preloading device, which can each be arranged axially relative to one another and can be arranged axially between the input part and the output part. The disk spring can be used, for example, as a preloading device. In order to generate a friction torque, the disk spring can be tensioned in the axial direction between the input or output element and the friction ring, and the friction ring can thereby be pressed against the output or input element with an axial pressure.

The pressure of the preloading means (or belleville springs) can be increased by the force exerted by the helical springs on the input and/or output member. An increase in the friction torque acting between the input element and the output element can thereby be achieved. The increase in friction torque may, for example, promote reduced wear and/or better damping of torsional vibrations.

In several embodiments of the invention, the coil springs may each have an abutment section on a spring end that abuts a spring retainer, wherein the spring retainer may be coupled with the input member and the output member.

The abutment section can be designed, for example, as a planar surface, so that the coil spring rests flat against the spring end on one of the spring seats arranged, for example, in the circumferential direction relative to the coil spring. For this purpose, the spring retainer has, on one side oriented in the circumferential direction, for example, a flat receiving section provided for abutment against the spring end. On the opposite side in the circumferential direction, the spring retainer has, for example, protruding holding elements which can engage into recesses for coupling, which recesses are introduced into the side of the window opening arranged opposite the spring retainer.

The indirect coupling of the helical spring to the input and/or output (e.g. by means of a spring race) may be used to advantageously transmit the axial force of the helical spring to the input and/or output.

In several embodiments of the invention, the abutting sections of the spring ends opposite in the circumferential direction may have a mutual overlap in the range of overlap angles of 300 ° to 360 ° in the circumferential direction.

The abutting sections of the spring ends that are opposite in the circumferential direction overlap around the spring axis, for example, from the perspective of the spring axis that points in the circumferential direction, with an overlap angle within the indicated overlap angle range. The axial force applied to the input and/or output members by the coil spring may vary with the angle of overlap. The smaller the overlap angle of the abutment sections, the greater the axial force exerted by the coil spring may be, for example (in otherwise identical designs and installation positions of the coil spring).

In several embodiments of the invention, the helical springs may be arranged such that the spring wire end of each spring end is in an angular range of-45 ° to +45° with respect to an axial direction oriented towards the transmission side.

In several embodiments of the invention, the helical springs may be arranged such that the spring wire end of each spring end is in an angular range of +45° to +135° with respect to the axial direction oriented towards the transmission side.

In several embodiments of the invention, the helical springs may be arranged such that the spring wire end of each spring end is in an angular range of +135° to +225° with respect to the axial direction oriented towards the transmission side.

In several embodiments of the invention, the helical springs may be arranged such that the spring wire end of each spring end is in an angular range of +225° to +315° with respect to the axial direction oriented towards the transmission side.

The spring wire ends of the spring ends that are opposite in the circumferential direction can, for example, advantageously be arranged within the same angular range with respect to the spring axis in order to apply an axial force to the input and/or output element. Depending on the installation position of the helical spring, the spring wire ends can be arranged, for example, in the angular range (-45 ° to +45°), in the radially outer angular range (+45° to +135°), in the motor-side angular range (+135° to +225°), or in the radially inner angular range (+225° to +315°) on the transmission side.

In addition to the angle of overlap of the abutment sections and other special features (e.g. spring wire thickness, number of turns, spring length, spring pitch), the strength of the axial force exerted by the coil spring may also depend on the mounting position of the coil spring or on the arrangement of the spring wire ends. The above-described mounting position of the helical spring may prove advantageous depending on the use and/or the embodiment of the torsional vibration damper.

In several embodiments of the invention, the torsional damper may comprise at least one spring stack with a plurality of coil springs arranged in each other. The outermost coil springs of the spring stack can be embodied here as left-hand wound coil springs.

The coils of the respective coil springs of the spring stack may have different outer diameters in order to be able to be arranged in each other. Furthermore, the coil springs of the spring stack may each have opposite winding directions (e.g., right-handed and left-handed winding directions). In an otherwise identical embodiment of the coil springs of the spring stack, the outermost coil springs can exert a greater axial force than the remaining coil springs of the spring stack. Thus, in the case of any partial compensation of the axial forces of the coil springs of the spring stack, the axial forces of the outermost coil springs may exceed the sum of the axial forces of the remaining coil springs. In the above-described arrangement of the output element on the transmission side, it may therefore be advantageous to embody the outermost helical spring as a left-hand wound helical spring, so that the axial forces exerted by the spring stack on the input element and/or on the output element act in the axial direction in the direction towards the other component (or in the direction towards the friction device), respectively.

The spring package can have a smaller spring capacity than a coil spring alone. By arranging a spring stack or a plurality of spring stacks in the torsional damper, for example, the maximum transmissible torque of the torsional damper can be increased relative to other embodiments.

In several embodiments of the invention, the spring retainer may have a receiving section which engages into the helical spring in the circumferential direction for axial fixing.

In order to ensure that axial forces are transmitted from the coil spring or from the spring stack to the input and/or output element, it may be advantageous to fix the coil spring or the spring stack to the spring seat ring at the spring ends arranged in the circumferential direction, at least in the axial direction. Furthermore, axial displacement or deflection of the spring ends during deformation of the spiral spring or the spring stack can thereby be avoided.

For this purpose, the receiving section can have, for example, a fastening element extending in the circumferential direction. The holding element can be designed, for example, cylindrically and can have a smaller outer diameter relative to the inner diameter of the coil spring or the spring stack. The spring end of the helical spring can thus be supported, for example, in the axial direction on a circumferential region of the fastening element. In a further advantageous embodiment, the spring ends can additionally be supported in the radial direction by means of a fastening element.

According to a second aspect, the invention relates to a clutch disc comprising a torsional vibration damper as described above and a friction lining which is connected in a rotationally fixed manner to an input element of the torsional vibration damper. Furthermore, the clutch disk comprises a hub which is connected in a rotationally fixed manner to the output element of the torsional vibration damper.

The friction lining may be arranged, for example, on a circumferential region radially outside the driven disk (serving as input for the torsional damper). The friction lining may be pressed against a motor-driven element (e.g., a flywheel) to direct motor torque into the torsional damper.

The output element of the torsional vibration damper is connected in a rotationally fixed manner to the hub, for example, in order to transmit the motor torque to the hub and to components connected to the hub downstream of the drive train.

The wear of the torsional damper can be reduced by the above-described embodiments of the torsional damper. Thus, for example, the service life of the clutch disc may be longer than conventional clutch discs.

Drawings

Several examples of embodiments of the present invention will be described in detail below, by way of example only, with reference to the accompanying drawings. In the drawings:

FIG. 1a shows a schematic representation of a clutch disc with a torsional damper in an axial top view;

FIG. 1b shows a cross-sectional view of a clutch disc with a spring stack;

FIG. 1c illustrates a cross-sectional view of a clutch disc having a friction device;

Fig. 2 shows a schematic illustration of a left-hand wound spiral spring with a force component acting upon deformation;

FIG. 3a shows a coil spring having spring wire ends disposed radially outward;

FIG. 3b shows a coil spring with spring wire ends disposed toward the transmission side; and

Fig. 3c shows a spiral spring with spring wire ends arranged towards the motor side.

Detailed Description

The various embodiments will now be described in detail with reference to the drawings in which several embodiments are shown.

While the embodiments may be modified and changed in different ways, embodiments are shown by way of example in the drawings and described in detail herein. It should be understood, however, that there is no intention to limit the embodiments to the forms disclosed, but on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the scope of the invention as defined by the appended claims.

Torsional vibration dampers used in the automotive field generally comprise a helical spring connected in a circumferential direction to an input member and an output member in order to dampen torsional vibrations of a torque to be transmitted when transmitting the torque. Here, the input element and the output element can be rotated relative to one another and the coil spring can be elastically deformed in the circumferential direction. In addition to the restoring forces of the helical springs acting in the circumferential direction, these can also, depending on their embodiment and design, introduce axial forces into the torsional vibration damper and in particular into the input and output elements. The axial force of the helical spring may cause the input element and/or the output element to deflect and/or tilt axially from a position that is advantageous for the function of the torsional damper. For example, components of the torsional damper or the function of the components may be adversely affected by tilting and/or axial deflection, which components are axially supported against or on the input or output element.

In fig. 1a, a torsional vibration damper 100 is shown from an axial perspective, which is implemented in a clutch disc 200. Fig. 1B shows the torsional damper 100 and the clutch disc 200 in a cross-sectional view (along "B-B") and fig. 1C in another cross-sectional view (along "C-C").

Torsional vibration damper 100 includes an input member 140 axially disposed between a first metallic cover plate 150-1 and a second metallic cover plate 150-2. The metallic cover plates 150-1 and 150-2 are embodied as output members and are connected, for example, rotationally fixed to one another and to a hub 170 having internal teeth for connection to elements downstream of the powertrain. The input element (as shown here) can be designed as a driven plate 140 of the clutch plate 200, which has friction linings 210 in the radially outer region. In order to be able to ensure a low-friction relative rotation, the metallic cover plates 150-1 and 150-2 can be arranged movably with respect to each other and/or with respect to the driven disk 140 with a certain axial play or in the axial direction.

Friction means 160 are arranged between the driven disc 140 and the metal cover plate 150-1 to dampen torsional vibrations. The preloading means of the friction means 160 may (as illustrated here) be embodied as a belleville spring 162. The belleville springs 162 are axially tensioned between the metallic cover plate 150-1 and the friction ring 164 to press the friction ring against the driven plate 140 to obtain a friction torque. The friction torque may, for example, help to dampen torsional vibrations. Alternatively, in several embodiments, friction device 160 may be disposed on axially opposite sides of driven disk 140.

Alternatively, driven plate 140 and at least one of metal cover plates 150-1 and 150-2 can be spaced apart from each other, for example, by means of a hub ring, which is arranged, for example, axially between metal cover plate 150-1 and driven plate 140. The hub ring may, for example, be in abutment with the driven plate 140 and the metallic cover plates 150-1 and 150-2, for example, to help dampen torsional vibrations and/or to act as an abutment surface for advantageously positioning the metallic cover plates 150-1 and 150-2 and/or the driven plate 140, for example.

The metal cover plates 150-1 and 150-2 are elastically coupled with the driven plate 140 by means of a spring stack having an outer coil spring 110 and an inner coil spring 120. In order to advantageously make full use of the available installation space, the inner coil spring 120 (as shown here) can be arranged inside the outer coil spring 110. The inner coil spring 120 is implemented as a right-hand wound coil spring, while the outer coil spring 110 is implemented as a left-hand wound coil spring. The coils of a right-hand wound helical spring extend, for example, clockwise along the spring axis. The coils of a left-hand wound helical spring extend, for example, counter-clockwise along the spring axis. In principle, embodiments can include additional, any number of coil springs.

To connect the coil springs 110 and 120, the spring retainer 130 is in abutment with the spring end 112 on the side facing the coil springs 110 and 120 in the circumferential direction. To this end, the spring ends 112 each have a flat surface as abutment sections 114, which are each in contact with one of the spring raceways 130.

On the circumferentially opposite side of the spring retainer 130, the spring retainer each comprises at least one retaining element 132 protruding in the circumferential direction. To couple the spring retainer 130 to the driven disk 140 and the metal cover plates 150-1 and 150-2, the retaining element 132 can be engaged into the introduced recess of the window openings of the driven disk 140 and the metal cover plates 150-1 and 150-2. Depending on the direction of rotation of the driven disk 140 relative to the metal cover plates 150-1 and 150-2, one of the spring retainer 130 may be coupled with the metal cover plates 150-1 and 150-2 or the driven disk 140, respectively, upon relative rotation. In the state of the clutch disk 200 shown in fig. 1a, the driven disk 140 and the metallic cover plates 150-1 and 150-2 are not rotated relative to one another, for example, wherein the spring retainer 130 can be coupled to both the metallic cover plates 150-1 and 150-2 and the driven disk 140.

During load operation, the driven disk 140 may rotate in a pulling direction relative to the metallic cover plates 150-1 and 150-2. In the top view of the clutch disc 200 shown in fig. 1a, rotation in the pulling direction corresponds to, for example, a clockwise rotation of the driven disc 140 relative to the metallic cover plates 150-1 and 150-2. In a push operation, driven disk 140 and metal cover plates 150-1 and 150-2, for example, have relative rotation in a push direction opposite to rotation in a pull direction.

In the case of relative rotation, the spring retainer 130 acts on the coil springs 110 and 120 in the circumferential direction, so that the spring group is elastically compressed in the circumferential direction. As the coil springs 110 and 120 are elastically deformed, they exert a restoring force against the relative rotation on the spring retainer 130 and the metal cover plates 150-1 and 150-2 or the driven plate 140 coupled thereto.

As the spring set compresses, torque may build up within each of the coil springs 110 and 120. Depending on the installation position and the winding direction as well as the rotational direction of the coil springs 110 and 120, an axial force 118-1 directed toward the motor side or an axial force 118-2 directed toward the transmission side opposite the motor side can thereby be exerted on the driven disk 140 and/or the metal cover plates 150-1 and 150-2 (as schematically illustrated in fig. 2). For the sake of simplifying the description of the illustrated embodiments, it can be assumed here, without limiting the invention: in fig. 1b and 1c, the right side of the driven disc 140 corresponds to the transmission side and the left side of the driven disc corresponds to the motor side. During rotation of the clutch disk 200, a radially outwardly directed force 119 can additionally act on the coil springs 110 and/or 120.

This results in overlapping of the abutment sections 114 arranged in the circumferential direction from the perspective of the spring axis along the coil springs 110 and 120. The size of the overlap can be determined by means of the angle of overlap. This may affect, for example, the direction and magnitude of the axial forces 118-1 and 118-2 exerted by the coil springs 110 and 120. In this embodiment, the coincidence has a coincidence angle of 330 °, for example. This angle of coincidence has proved advantageous, for example, for the application of the torsional vibration damper 100 in the clutch disk 200.

In this embodiment, the driven disk 140 may be axially fixedly arranged in comparison to the metallic cover plates 150-1 and 150-2, so that the axial forces 118-1 and 118-2 may have an influence on the position of the metallic cover plates 150-1 and 150-2, in particular, depending on the design and installation position of the coil springs 110 and 120.

The outer spiral spring 110 has, for example, the installation position shown in fig. 2, in which the spring wire end 116 of the spring end 112 is arranged in an angular range 117-1 lying radially inward (between 225 ° and 315 ° with respect to the axial direction 115 oriented toward the transmission side).

In the installed position shown in fig. 2, upon relative rotation in the pulling direction, the outer coil spring 110 applies an axial force 118-1, for example, to at least the metallic cover plate 150-1. Upon opposite relative rotation in the pushing direction, the outer coil spring 110 applies an axial force 118-2 to at least one of the metal cover plates 150-1 and 150-2.

For a structurally overlapping or additive combination of the axial forces 118-1 and 118-2, the inner, right-hand wound coil spring 120 can be arranged opposite the outer coil spring 110, for example, such that the spring wire ends of the inner coil spring 120 are arranged in the radially outer region of the inner coil spring 120.

Upon relative rotation in the pulling direction, the metal cover plate 150-1 can thus be pressed against (i.e., for example against the friction device 160) in the direction toward the spaced-apart, further component and thus increase the pressure exerted by the disk spring 162 on the friction ring 164. The consequent increase in friction torque between the friction ring 164 and the driven disk 140 may have a beneficial effect on damping of torsional vibrations and/or on wear of the torsional damper 100.

The axial force 118-2 generated upon relative rotation in the pushing direction may be smaller than the axial force 118-1 acting upon relative rotation in the pulling direction. The resulting friction torque can therefore be smaller than the friction torque applied when the relative rotation is performed in the pulling direction. This may prove advantageous if, for example, during a push operation, a smaller friction torque is desired than during a load operation.

Furthermore, the axial force 118-1 may depend on the mounting position of the coil springs 110 and 120, which acts on the metallic cover plate 150-1 and/or 150-2 in an advantageous manner as described previously. Thus, the axial force 118-1 may be adapted to the torsional vibration damper due to a change in the mounting position, e.g., according to the requirements for the application.

Fig. 3a, 3b and 3c each show an alternative mounting position of the coil springs 110 and 120 to that shown in fig. 2.

In fig. 3a, a possible installation position is shown, in which the spring wire end 116 is arranged in an angular range 117-2 located radially outside of +45° to +135° with respect to the axial direction 115. In this installed position, coil spring 110 may exert axial forces 118-1 and 118-2 on driven disk 140 and/or metal cover plates 150-1 and 150-2 (with reference to the embodiment illustrated in FIG. 2) in correspondingly opposite relative rotational directions. Such a mounting location may prove advantageous if axially spaced apart components (e.g., friction device 160) are disposed on the motor side (i.e., axially between, for example, metal cover plate 150-2 and driven disk 140).

Fig. 3b and 3c show further mounting positions in which the spring wire ends 116 (for example, as shown in fig. 3 b) are arranged axially on the transmission side in an angular range 117-3 on the transmission side of-45 ° to +45° relative to the axial direction 115, or axially on the motor side (for example, as shown in fig. 3 c) in an angular range 117-4 on the motor side of +135° to +225° relative to the axial direction 115. This installed position of the coil springs 110 and 120 can cause additional radial force components that can be exerted by the coil springs 110 and 120 on the spring retainer 130, the driven disk 140, and/or the metallic cover plates 150-1 and 150-2. Thus, for example, radial forces (e.g., the radially outwardly directed forces 119 acting on the coil springs 110 and 120) can be counteracted.

The spring packs illustrated in fig. 1a, 1b and 1c may have different combinations of mounting positions of the coil springs 110 and 120 to meet the requirements of the application, e.g. torsional damper. The coil springs 110 and 120 can, for example, have a defined mounting position that differs from one another in such a way that the axial forces 118-1 and 118-2 exerted by the coil springs 110 and 120 interact together in an additive manner or, for example, partially compensate one another.

Aspects and features described in connection with one or more of the foregoing detailed examples and the drawings may also be combined with one or more other examples to replace the same features of the other examples or to introduce such features into the other examples as well.

Furthermore, the following claims are hereby incorporated into the detailed description, with each claim standing on its own as a separate example. Although each claim itself may represent a separate example, it should be noted that: although in the claims dependent claims may refer to particular combinations with one or more other claims, other examples may include combinations of the dependent claims with the subject matter of each other dependent or independent claim. Such combinations are expressly set forth herein unless it is noted that a particular combination is not intended to be used. Furthermore, the features of a claim should also be included in relation to any other independent claim even if such claim is not directly dependent on said independent claim.

List of reference numerals

100. Torsional vibration damper

110. External helical spring

112. Spring end

114. Abutment section

115. Axial direction

116. Spring wire end

117-1 Are located at a radially inner angular extent

117-2 Are located at a radially outer angular extent

117-3 Angular range on the transmission side

117-4 Angular range on the motor side

118-1 Directed axially towards the motor side

118-2 Directed axially towards the transmission side

119. Force directed radially outward

120. Internal helical spring

130. Spring retainer

132. Holding element

140. Driven plate

150-1 Metallic cover plate arranged on the transmission side

150-2 Metal cover plate arranged on the Motor side

160. Friction device

162. Belleville spring

164. Friction ring

170. Hub

200. Clutch disc

210. Friction lining

Claims

1. A torsional damper (100), comprising:

An input member (140) and an output member (150-1, 150-2) axially arranged relative to the input member, wherein the input member (140) and the output member (150-1, 150-2) are movably arranged relative to each other in an axial direction;

At least one helical spring (110, 120) which can be coupled to the input element (140) and the output element (150-1, 150-2) at spring ends (112) which are arranged opposite in the circumferential direction, wherein the helical spring (110, 120) is designed and arranged for applying an axial force (118-1, 118-2) to at least the output element (150-1, 150-2) or the input element (140) in the event of a deformation in the circumferential direction, said axial force acting toward a further component of the torsional vibration damper which axially separates the input element (140) and the output element (150-1, 150-2) from one another,

Wherein the output element (150-1, 150-2) is arranged on the transmission side relative to the input element (140), the input element (140) is arranged on the motor side, and wherein the helical springs (110, 120) are embodied as left-hand wound helical springs,

Wherein the axially spaced apart components include friction means (160) which apply axial pressure to the input member (140) and the output member (150-1, 150-2) respectively to generate a friction torque.

2. The torsional damper (100) of claim 1, wherein the coil springs (110, 120) each have an abutment section (114) at the spring end (112) that abuts a spring race (130), wherein the spring race (130) is coupleable with the input member (140) and the output member (150-1, 150-2).

3. The torsional vibration damper (100) of claim 2, wherein the abutment sections (114) of the spring ends (112) arranged opposite in the circumferential direction have an overlap with each other in an overlap angle range of 300 ° to 360 ° in the circumferential direction.

4. The torsional damper (100) of claim 2, wherein the coil springs (110, 120) are arranged such that the spring wire end (116) of each spring end (112) is within an angular range (117-3) of-45 ° to +45° with respect to an axial direction (115) oriented toward the transmission side.

5. The torsional damper (100) of claim 2, wherein the coil springs (110, 120) are arranged such that the spring wire end (116) of each spring end (112) is within an angular range (117-2) of +45° to +135° with respect to an axial direction (115) oriented toward the transmission side.

6. The torsional damper (100) of claim 2, wherein the coil springs (110, 120) are arranged such that the spring wire end (116) of each spring end (112) is within an angular range (117-4) of +135° to +225° with respect to an axial direction (115) oriented toward the transmission side.

7. The torsional damper (100) of claim 2, wherein the coil springs (110, 120) are arranged such that the spring wire end (116) of each spring end (112) is within an angular range (117-1) of +225° to +315° with respect to an axial direction (115) oriented toward the transmission side.

8. Torsional damper (100) according to one of claims 1, 3 to 7, wherein the torsional damper (100) comprises at least one spring stack having a plurality of coil springs (110, 120) arranged in one another, wherein the outermost coil springs (110) of the spring stack are embodied as left-hand wound coil springs.

9. The torsional damper (100) of claim 2, wherein the spring retainer (130) has a receiving section that engages into the helical spring (110, 120) in a circumferential direction for axial fixation.

10. A clutch disc (200), comprising:

Torsional damper (100) according to one of claims 1 to 9;

-a friction lining (210) connected in a rotationally fixed manner to an input element (140) of the torsional vibration damper (100);

A hub (170) which is connected in a rotationally fixed manner to the output element (150-1, 150-2) of the torsional vibration damper (100).