DE102019215883A1 - Torsional vibration damper - Google Patents

Abstract

Embodiments of the present invention relate to a torsional vibration damper 100, which has an input-side component 110 and an output-side component 120 arranged parallel thereto. The input-side and output-side components 110 and 120 each have at least one window opening 150 for receiving a helical spring 130. Each window opening 150 has at least one first notch 140-1 made on a circumferential end of the window opening 150. Furthermore, the torsional vibration damper 100 comprises at least one helical spring 130, which is arranged for torque transmission in the circumferential direction in the window opening 150 of the input-side and output-side components 110 and 120. On at least one spring end, the helical spring 130 has a first web 131-1 which engages in the first notch 140-1 of at least one of the window openings 150 to fix the helical spring 130.

Description

The invention relates to a torsional vibration damper. In particular, but not exclusively, the invention relates to a torsional vibration damper for damping torsional vibrations within a drive train of a motor vehicle.

In the automotive sector, for example, drive trains are used to transmit torque generated by an engine. In reciprocating engines, for example, the torque is subject to torsional vibrations, which can cause mechanical stress to act on the drive train. In order to reduce the associated wear of the drive train, the torsional vibrations can be dampened by means of a torsional vibration damper. In order to damp the torsional vibrations, an input side of the torsional vibration damper can be elastically coupled to an output side, for example by means of one or more helical springs.

For a flat support of the helical springs on the input or output side, the spring ends of the helical springs can, for example, be ground off and / or have a spring pitch that is changed towards the spring ends. When the helical spring is compressed to transmit the torque, this can result in twisting, radial and / or axial deflection of the helical springs. As a result, transverse forces can occur which act axially on components of the torsional vibration damper and can lead to additional wear.

A conventional concept for coupling a helical spring to an input side and an output side of a torsional vibration damper is, for example, the laid-open specification DE 10 2015 214 421 A1 set out. Here, the helical spring has an elastic element for providing additional flexibility of the helical spring in the circumferential direction.

A concept for reducing the transverse forces occurring in the torsional vibration damper is not taken into account here.

It can therefore be regarded as an object of the invention to provide an improved concept for reducing transverse forces in a torsional vibration damper.

This object is achieved according to the independent and dependent claims of the present invention.

According to a first aspect, the invention relates to a torsional vibration damper which has an input-side component and an output-side component arranged parallel thereto. The input-side and the output-side component each have at least one window opening for receiving a helical spring. Each window opening has at least one first notch made on a circumferential end of the window opening. Furthermore, the torsional vibration damper comprises at least one helical spring which is arranged for torque transmission in the circumferential direction in the window opening of the component on the input side and the component on the output side. On at least one spring end, the helical spring has a first web which engages in the first notch of at least one of the window openings to fix the helical spring.

The input part of the torsional vibration damper can for example be rotatably arranged on a hub. The output part can be arranged coaxially and rotatably with respect to the input part, so that the input part and the output part can rotate relative to one another. The input part can be designed, for example, as a drive plate, which is arranged axially between two non-rotatably connected cover plates, which for example form the output part. Here, for example, the drive plate and the cover plates can each have at least one window opening.

The window opening of the input part can overlap with the window opening of the output part in such a way that the helical spring arranged therein can reach through the input part and the output part axially.

When a torque is introduced into the input part, for example, the input part can rotate relative to the output part, as a result of which the helical spring arranged therein is compressed. The torque to be transmitted can thereby be introduced into the helical spring. The torque introduced into the helical spring can be passed on to the output part and, proceeding therefrom, can be transmitted to downstream components in the drive train, such as a gearbox.

The first web of the helical spring can, for example, have a finger-like or cylindrical structure and, for example, be connected to the helical spring in a materially or force-locked manner. Furthermore, the first web extends, for example, in the axial direction, so that it engages positively in the first notch of the window openings of the component on the input side and the component on the output side. This allows the coil spring be supported for example in the radial, axial and / or in the circumferential direction. In addition, by means of a form fit between the first web and the first notch of the window openings, it can be achieved that the helical spring is secured against rotation about its coil axis.

In the context of the invention disclosed herein, the coil axis is, for example, an axis around which the individual spring coils of the helical spring are helically wound. The helical spring arranged in the circumferential direction in a clutch disk has, for example, a coil axis oriented tangentially to the circumferential direction.

By connecting the helical spring to the input-side and / or output-side component by means of the first web, it is possible, for example, to design the helical spring in such a way that it has a constant spring pitch at the peripheral spring end on which the first web is arranged. The spring pitch can be characterized, for example, by a distance (winding distance) between individual windings. With a constant spring pitch, the winding spacing is also constant, for example.

As a result, when the helical spring is compressed, twisting, axial and / or radial deflection of this and associated transverse forces that can act on components of the torsional vibration damper can be reduced.

In some exemplary embodiments of the torsional vibration damper, the window opening of the input-side component and the window opening of the output-side component can each have a second notch. The second notch can be made on a circumferential end of the window opening opposite the first notch. At a spring end opposite the first web, the helical spring can have a second web which engages in the second notch of at least one of the window openings to fix the helical spring.

By connecting the circumferential spring ends on both sides by means of the first and second webs, the twisting, the axial and / or the radial deflection of the helical spring when it is compressed can be additionally reduced compared to a one-sided connection by means of the first web. Transverse forces acting on the torsional vibration damper, which result from the twisting, axial and / or radial deflection of the helical spring, can thereby be further reduced. In an ideal case, it can be achieved that the torsional vibration damper is free of such transverse forces.

In some exemplary embodiments of the torsional vibration damper, the helical spring can each have a spring coil on opposite spring ends, which is bent towards the coil axis of the helical spring in order to form the first or second web.

The last spring coils towards the spring ends can, for example, each have a straight section which is bent over towards the coil axis, so that it intersects the coil axis, for example. The straight-formed section can be arranged so that it engages in the first or second notch of the input-side component and / or the output-side component in order to thus serve as a first or second web.

In order to ensure that the first and second webs abut with at least one of the input-side component and the output-side component, the last spring turns of the helical spring towards the spring ends can also be designed in such a way that they are pretensioned in the circumferential direction relative to the input-side or component on the output side.

In some exemplary embodiments of the torsional vibration damper, the first and second webs can be arranged parallel to one another.

If the first and second webs are aligned parallel to one another, the helical spring has, for example, an integer number (number of turns) of spring turns. A length of the helical spring can be dependent on the number of turns and the spring pitch. Depending on the extent of the window openings and depending on the spring pitch, an integral number of turns and thus a parallel arrangement of the first and second webs to one another can prove to be advantageous for the arrangement of the helical spring in the window openings.

In some exemplary embodiments of the torsional vibration damper, the first and second webs can be arranged antiparallel to one another.

In the case of an anti-parallel arrangement of the first and second webs, the helical spring can, for example, have a half-integer number of turns. For an arrangement of the helical spring in the window openings, the half-integer number of turns can vary depending on the extent of the window openings compared to the integer number Turn number of turns in some exemplary embodiments to be advantageous.

In some exemplary embodiments of the torsional vibration damper, the first and second webs can be aligned perpendicular to a plane of rotation of the component on the input side and the component on the output side.

If the first and second webs are arranged parallel or antiparallel to one another, it can be advantageous if they are aligned perpendicular to the plane of rotation of the input-side component and the output-side component. Thus, the first and second webs can each reach axially through the first and second notches. In this way it can be achieved, for example, that the helical spring is supported in the radial direction. Furthermore, the twisting of the helical spring about the coil axis can thereby be prevented.

In some exemplary embodiments, the first and second webs can have an angle of rotation with respect to one another.

Compared to other exemplary embodiments, the first and second webs are here neither parallel nor antiparallel.

In order to ensure that the first and second webs engage in the first and second notches, respectively, the first and second notches of the input-side and output-side components can have different radial distances from the axis of rotation of the torsional vibration damper, for example.

Because the first and second webs have the angle of rotation with respect to one another, for example an axial fixation or an axial centering of the helical spring within the torsional vibration damper can be achieved.

In some exemplary embodiments of the torsional vibration damper, the torsional vibration damper can furthermore comprise an inner spring which is arranged coaxially opposite the helical spring in an interior of the helical spring. The circumferential spring ends of the inner spring can be supported in the circumferential direction by at least the first web, second web, input-side component or output-side component in the circumferential direction.

A helically wound wire can, for example, be designed as an internal spring. An outer diameter of the inner spring can be smaller than an inner diameter of the helical spring, so that the inner spring can be guided within the helical spring.

In order to provide an additional spring force directed in the circumferential direction in addition to the spring force of the helical spring, the spring ends of the inner spring can be supported in the circumferential direction, for example on the input-side component and / or output-side component. Additionally or alternatively, the inner spring can rest with the spring ends of the inner spring on the first or second web in order to support the spring ends of the inner spring in the opposite circumferential direction.

Depending on the application of the torsional vibration damper, it can prove to be advantageous to provide the spring force of the inner spring in addition to the spring force of the helical spring.

In some exemplary embodiments, at least the first web or the second web can have a fixing element which is arranged axially next to the component on the output side or the component on the input side. An outer diameter of the fixing element can be larger than an inner diameter of the first and second notches.

The fixing element can, for example, be connected in a materially or force-fit manner to the first or second web, which extend axially through the notches of the window openings. The fixing element can correspond, for example, to a compressed section of the first or second web. By upsetting it can be achieved that the outside diameter of the fixing element is larger than the inside diameter of the first and second notches. The fixing element can, for example, be arranged axially offset in such a way that it rests in the axial direction on the input-side component or the output-side component. For an axial fixation of the first and the second web, these can have fixing elements. As a result, the first and second webs can be secured against axial displacement in the axial direction by means of the fixing elements.

According to a second aspect, the present invention relates to a clutch disc which comprises a friction lining and the torsional vibration damper for absorbing a torque. The input-side component of the torsional vibration damper is coupled to the friction lining in a rotationally fixed manner. Furthermore, the torsional vibration damper comprises a hub which is coupled non-rotatably to the component of the torsional vibration damper on the output side.

By means of a friction torque, a clutch can, for example, transmit a torque originating from an engine to the friction lining. A non-rotatable connection of the component of the torsional vibration damper on the input side, it can introduce the torque into the helical spring. Thus, the torque can be transmitted to the output-side component via an elastic coupling of the input-side component to the output-side component. By coupling the output-side component to the hub in a rotationally fixed manner, the torque can be transmitted, for example, to an output shaft which can transmit the torque to components which, for example, can be located downstream in the drive train of a motor vehicle.

In the following, some exemplary embodiments are explained by way of example and in greater detail with reference to the accompanying figures.

• 1a zeigt eine Kupplungsscheibe mit einem Torsionsschwingungsdämpfer aus einer axialen Perspektive;
• 1 b zeigt die Kupplungsscheibe mit Torsionsschwingungsdämpfer in einer Schnittansicht;
• 2 zeigt die Kupplungsscheibe bei Drehmomentübertragung aus einer axialen Perspektive.

Show it:

• 1a shows a clutch disc with a torsional vibration damper from an axial perspective;
• 1 b shows the clutch disc with torsional vibration damper in a sectional view;
• 2 shows the clutch disc during torque transmission from an axial perspective.

Various embodiments will now be described more fully with reference to the accompanying drawings, in which some embodiments are shown.

Although exemplary embodiments can be modified and changed in various ways, exemplary embodiments are shown in the figures as examples and are described in detail herein. It should be made clear, however, that the intention is not to restrict exemplary embodiments to the forms disclosed in each case, but rather that exemplary embodiments are intended to cover all functional and / or structural modifications, equivalents and alternatives that are within the scope of the invention.

In the case of torsional vibration dampers, an input side is typically elastically coupled to an output side in order to dampen torsional vibrations originating from the engine when a torque is transmitted. An elastic coupling can be achieved, for example, by means of a helical spring, which can be compressed in the circumferential direction for torque transmission when the input side is rotated relative to the output side.

In conventional torsional vibration dampers, the circumferential spring ends of the helical spring can each be supported in the circumferential direction, for example by means of spring plates. For a flat support of the spring ends on the spring plates, the last spring coils can be ground down towards the spring ends. Thus, a spring wire of the last spring turn has, for example, a taper and thus a modulus of elasticity that is different from that of the other spring turns.

When such a helical spring is compressed, it can twist, be axially and / or radially deflected. As a result, the helical spring can, for example, exert transverse forces on components of the conventional torsional vibration damper. If the components tilt with respect to an axis of rotation of the torsional vibration damper due to the transverse forces, for example, they can exhibit additional wear.

It can therefore be regarded as the object of the present invention to design a torsional vibration damper in such a way that the transverse forces occurring when the helical spring is compressed can be reduced. In an ideal case, the torsional vibration damper can be designed in such a way that it can be free of such transverse forces.

To achieve the object, a torsional vibration damper can be used, for example, according to the method shown in FIG 1a and 1b be formed embodiment shown. These show a torsional vibration damper 100 , which is arranged in a clutch disc 200 to reduce torsional vibrations. 1a shows the clutch disc 200 from an axial perspective and 1b a sectional view (along “AA”) of the clutch disc 200.

The torsional vibration damper 100 has an input-side component 110 , which rotatably with a friction lining 160 is connected, and an output-side component 120 on, which comprises, for example, two coaxially non-rotatably connected cover plates and non-rotatably with a hub 170 connected is. In spring openings 150 the input-side and the output-side component 110 and 120 are for example coil springs 130 arranged. A first bridge 131-1 the coil springs 130 engages, for example, as shown herein, in first notches 140-1 a, which at a peripheral end of the window openings 150 of the component on the input side 110 and component on the output side 120 are introduced. In addition, embodiments of the invention, as in 1a and 1b shown on a circumferentially opposite end of the window openings 150 second notches 140-2 have which a second web 131-2 the coil springs 130 reaches through in the axial direction.

Last spring turns to the circumferential spring ends of the coil springs 130 are each as the first bridge 131-1 , or as a second bridge 131-2 , educated. These each have a straight-shaped section, which is bent in the direction of a winding axis, so that the straight-shaped section intersects this. The coil axis is here an axis around which a spring wire of the coil springs 130 is helically wound.

The first and second bridge 131-1 and 131-2 are antiparallel to one another and perpendicular to a plane of rotation of the torsional vibration damper 100 arranged. The coil springs 130 therefore have, for example, a half-integer number (number of turns) of turns. Depending on the design of the window openings 150 or the coil springs 130 with regard to their spring pitch, the first and second webs can prove to be advantageous 131-1 and 131-2 parallel to each other so that the coil springs 130 have an integer number of turns.

The first and the second bridge 131-1 and 131-2 can, as in 1a and 1b shown fixing elements 133 include for axial fixation. The fixing elements 133 are here, for example, axially with one of the cover plates of the component on the output side 120 in Appendix. The fixing element 133 can for example by compressing the first web 131-1 , or the second web 131-2 be created. As a result, the fixing element has an outer diameter which is greater than an inner diameter of the notches 140-1 and 140-2 . With anti-parallel arrangement of the bars 131-1 and 131-2 , for example, the coil springs 130 be secured against axial displacement, both to a drive side and to an output side.

The embodiment of the torsional vibration damper shown here 100 , or the clutch disc 200, comprises five helical springs arranged rotationally symmetrically in the circumferential direction 130 . Depending on the requirements of the torsional vibration damper 100 can be a number of coil springs 130 be adapted, for example, to a maximum torque, which is maximum in the torsional vibration damper 100 can be initiated to increase or decrease.

When the clutch disc 200 transmits torque, the torque can be fed into the friction lining via a frictional torque 160 and thus in the input-side component connected therewith in a rotationally fixed manner 110 be initiated. As in 2 shown, the input-side component 110 thereby relative to the component on the input side 120 twist. In the event of a relative rotation between the component on the input side 110 and the component on the output side 120 As shown herein, these can each exert a circumferentially opposing force on the helical springs 130 exercise so that this is used to transmit the torque to the hub 170 be compressed. Here, the first web 131-1 for example with the component on the input side 110 and the second bridge 131-2 with the component on the output side 120 stand in plant. In the case of an opposite relative rotation, there may be a change of contact, so that the first web 131-1 with the component on the output side 120 and the second bridge 131-2 with the component on the input side 110 comes to the plant. 1a for example, shows the torsional vibration damper at the time of a system change.

Both in the compressed state (see 2 ), as well as when changing the system (see 1a) grip the first and second web 131-1 and 131-2 positively in the first or second notch 140-1 and 140-2 . This allows the first and second web 131-1 and 131-2 the coil springs 130 support in the radial direction against centrifugal forces which, when the clutch disc 200 is in operation, act on the helical springs 130 can work.

As in 1a , 1b and 2 shown, reaches through at least the first web 131-1 or the second bridge 131-2 at least two notches 141-1 or 141-2 arranged axially next to one another. Thus, the coil springs 130 be secured against twisting about their winding axis.

The first and the second bridge 131-1 and 131-2 can, as an alternative to the in 1a , 1b and 2 embodiment shown, each have a twist angle. Here are the first bridge 131-1 and 131-2 aligned neither parallel nor anti-parallel to each other. Due to the angle of rotation of the first and second web 131-1 and 131-2 can the coil springs 130 can be secured against axial displacement. Therefore, the first and the second web 131-1 and 131-2 alternatively or in addition to the fixing element 133 have the angle of rotation for axial fixation.

Additionally, embodiments of the present invention can include one or more internal springs. The inner springs can be coaxial with the coil springs winding axes 130 be arranged. Because, for example, an outer diameter of the inner springs is smaller than an inner diameter of the coil springs 130 is selected, the inner springs inside can each be one of the coil springs 130 be arranged.

Peripheral spring ends of the inner spring can, for example, on the first and on the second web 131-1 and 131-2 are supported in the circumferential direction towards each other. Alternatively or additionally, the spring ends of the inner spring can be on the input-side component 110 and on the component on the output side 120 are supported in the opposite direction in the circumferential direction. As a result, for example, a maximum force can be applied to the torsional vibration damper in the circumferential direction 100 can be initiated, increased.

Compared to conventional torsional vibration dampers, the in 1a , 1b and 2 The embodiments shown do not have spring plates or spring receptacles for the peripheral connection of the helical springs 130 on. Thus, for example, compared to conventional torsional vibration dampers, a number of components and the associated assembly effort can be reduced.

The aspects and features that are described together with one or more of the previously detailed examples and figures can also be combined with one or more of the other examples in order to replace an identical feature of the other example or to add the feature in the other example to introduce.

Furthermore, the following claims are hereby incorporated into the detailed description, where each claim can stand on its own as a separate example. While each claim may stand on its own as a separate example, it should be noted that although a dependent claim in the claims may refer to a particular combination with one or more other claims, other examples also combine the dependent claim with the subject matter of each other dependent or independent claims. Such combinations are explicitly suggested here unless it is indicated that a particular combination is not intended. Furthermore, features of a claim are also intended to be included for any other independent claim, even if that claim is not made directly dependent on the independent claim.

List of reference symbols

100

Torsional vibration damper

110

Input-side component

120

Output component

130

Coil springs

131-1

First bridge

131-2

Second bridge

133

Fixing element

140-1

First notch

140-2

Second notch

150

Window opening

160

Friction lining

170

hub

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102015214421 A1 [0004]

Claims (10)

A torsional vibration damper (100) comprising: an input-side component (110) and an output-side component (120) arranged parallel to it, each having at least one window opening (150) for receiving a helical spring (130), each window opening (150) being at least one first introduced at a peripheral end of the window opening Has notch (140-1); at least one helical spring (130) which is used to transmit torque in the circumferential direction in the window opening (150) of the input-side and of the component (110, 120) on the output side, the helical spring (130) having a first web (131-1) on at least one spring end, which for fixing the helical spring (130) in the first notch (140-1) at least engages one of the window openings (150). Torsional vibration damper (100) according to Claim 1 wherein the window opening (150) of the input-side component (110) and the window opening (150) of the output-side component (120) each have a second notch (140-2) which is located on a circumferential end opposite the first notch (140-1) the window opening (150) is introduced, and wherein the helical spring (130) has a second web (131-2) at a spring end opposite the first web (131-1) to the circumferential direction, which in the second notch (140-2) at least engages one of the window openings (150). Torsional vibration damper (100) according to Claim 2 wherein the helical spring (130) has a spring turn at opposite spring ends, which is bent towards the winding axis of the helical spring (130) in order to form the first and second webs (131-1, 131-2), respectively. Torsional vibration damper (100) according to Claim 2 or Claim 3 , wherein the first and the second web (131-1, 131-2) are arranged parallel to one another. Torsional vibration damper (100) according to Claim 2 or Claim 3 , wherein the first and the second web (131-1, 131-2) are arranged antiparallel to one another. Torsional vibration damper (100) according to the Claim 4 or Claim 5 , wherein the first and the second web (131-1, 131-2) are aligned perpendicular to a plane of rotation of the input-side component (110) and the output-side component (120). Torsional vibration damper (100) according to Claim 2 , wherein the first and the second web (131-1, 131-2) have an angle of rotation with respect to one another. Torsional vibration damper (100) according to one of the preceding claims, wherein the torsional vibration damper (100) further comprises an inner spring which is arranged opposite the helical spring (130) coaxially in an interior of the helical spring (130), the peripheral spring ends of the inner spring in the circumferential direction each from at least the first web (131-1), second web (131-2), input-side component (110) or output-side component (120) are supported in the circumferential direction. Torsional vibration damper (110) according to one of the preceding claims, wherein at least one of the first or second web (131-1, 131-2) has a fixing element (133) which is axially adjacent to the output-side component (110) or the input-side component (120) is arranged, wherein an outer diameter of the fixing element (133) is larger than an inner diameter of the first and second notches (141-1, 141-2). A clutch disc (200) comprising: a friction lining (160) for absorbing a torque; a torsional vibration damper (100) according to FIGS Claims 1 to 9 wherein the input-side component (110) of the torsional vibration damper (100) is coupled to the friction lining (160) in a rotationally fixed manner; a hub (170) which is non-rotatably coupled to the component (120) of the torsional vibration damper on the output side.

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