CN106461004B

CN106461004B - Device for transmitting torque

Info

Publication number: CN106461004B
Application number: CN201580029385.7A
Authority: CN
Inventors: S·马伊恩沙因
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2014-06-03
Filing date: 2015-06-01
Publication date: 2020-03-03
Anticipated expiration: 2035-06-01
Also published as: CN106461004A; WO2015185054A3; DE112015002646A5; WO2015185054A2

Abstract

An apparatus (100) for transmitting torque, comprising: an input (110) side and an output side (115) rotatable about a rotation axis; a torsional vibration damper (115) having an elastic element (145), wherein the torsional vibration damper is arranged in a torque flow between the input side and the output side; and a centrifugal force pendulum (130) which is coupled without play to the torsional vibration damper, wherein the torsional vibration damper is preloaded.

Description

Device for transmitting torque

Technical Field

The present invention relates to a device for transmitting torque. The invention relates in particular to a torque transmission device for use in a drive train on a motor vehicle.

Background

In the drive train, in particular in a motor vehicle, a device for transmitting torque is provided. The device can be arranged in particular between the drive engine and the transmission of the drive train. In order to decouple or dampen rotational irregularities in the drive train, the device can comprise a torsional vibration damper, a centrifugal force pendulum or both.

For assembly purposes and disassembly purposes, the device is usually connected to the drive train by means of a toothed section. However, such torque-locking, but releasable connections are generally gapped. Additional play can occur in the region of the torsional vibration damper, in particular between the rotary element of the torsional vibration damper and the spring element for coupling the rotary element. These gaps or tolerances can overlap and the centrifugal force pendulum can be impaired in its function. In particular, so-called NVH properties (Noise, Vibration, Harshness) are adversely affected. In particular in partial load operation or low load operation, disturbing or wear-promoting noises or vibrations can occur.

Disclosure of Invention

The object of the present invention is to indicate an improved device for transmitting torque, which device exhibits, in particular, improved NVH behavior. The invention solves this task by means of a device having the features of the invention.

The device for transmitting torque according to the invention comprises an input side and an output side which are rotatable about an axis of rotation. The device further comprises a torsional vibration damper having an elastic element, wherein the torsional vibration damper is arranged in the torque flow between the input side and the output side; and a centrifugal force pendulum which is coupled without play to the torsional vibration damper, wherein the torsional vibration damper is preloaded.

This makes it possible to avoid: the play in the region of the torsional vibration damper acts counter to the centrifugal force pendulum and impairs the operating efficiency of the centrifugal force pendulum, or vice versa. In particular, it is possible to prevent: the gaps of the plurality of devices, in particular the first gap in the torsional vibration damper and the second gap in the input side or in the output side, overlap or interact.

In a first variant, the torsional vibration damper comprises an input flange, an output flange and an elastic element, and the centrifugal force pendulum is mounted directly on the input flange. As a result, possible play within the torsional vibration damper is outside the transmission path between the input side and the centrifugal force pendulum. The play of the torsional vibration damper can therefore only further reduce or no longer impair the operation of the centrifugal force pendulum at all.

In a further variant, the torsional vibration damper comprises an input flange, an output flange and an elastic element, and the centrifugal force pendulum is mounted directly on the output flange. As a result, any play within the torsional vibration damper can be counteracted or rendered harmless with respect to the centrifugal force pendulum. The centrifugal force pendulum can be connected directly to the output side, for example. The general design of the device for transmitting torque can be kept unchanged. The change can be effected only in the region of the torsional vibration damper by providing the torsional vibration damper with a preload to ensure that the torsional vibration damper operates without play.

Each flange preferably has two abutments for cooperating with a resilient element, and the resilient element is located between the abutments in such a way that: the spring element is loaded both in the case of a positive torsion of the two flanges relative to one another and in the case of a negative torsion of the two flanges relative to one another. In this case, the spring element remains loaded during the transition between positive and negative torsion.

For example, the two flanges can each have a spring window which is located in the circumferential direction about the axis of rotation. In the rest state of the torsional vibration damper, the spring windows of the two flanges are generally aligned in the axial direction, and the spring element rests in the spring windows. The rest state can also be referred to as a neutral state or a rest position. In this rest state, the elastic element is maximally unloaded. By configuring the spring element and/or at least one of the flanges in such a way that the spring element is kept loaded during the transition between positive and negative torsion, the loading of the spring element is therefore always greater than zero, and the play within the torsional vibration damper can be minimized or rendered harmless in its effect on the centrifugal pendulum.

The load of the spring element is preferably continuously maintained above a predetermined value during said transition. Since the spring element acts directly on the two flanges, these flanges are always subjected to a relative restoring force which drives them into the rest state. Then a gap at a relative torsion angle that is not subject to any restoring forces is no longer present. The predetermined value can be selected such that the restoring moment between the flanges is above 0.5 nm, preferably above 2 nm, in particular above 5 nm, at a torsion value of 0.5 degrees.

In one embodiment, the continuous restoring force acting on the flange is caused by: the spring element is not loaded by more than the distance between the abutments on each flange. In the above-described embodiments, it is possible to use, for example, a cylindrical coil spring having an unloaded length greater than the length of each of the spring windows. The spring element can have a corresponding excess length if it is located in the circumferential direction about the axis of rotation and is embodied in particular as an arc spring or circumferential spring.

Additionally or alternatively, the continuous pretensioning force can be achieved by: at least one of the abutments of the flange is shaped in a particular manner. In this case, the abutment can be inclined, in particular with respect to the abutment surface of the spring element, in a plane of rotation about the axis of rotation. In one embodiment, one of the contact surfaces has a surface which is inclined by a predetermined value relative to the assigned contact surface of the unloaded spring element. In particular, in the case of spring elements having a high spring constant, a small restoring force can be maintained precisely by the inclined surfaces in the region between the positive and negative mutual twisting of the flanges.

The abutment of the other flange provided for fitting into the same side of the elastic element comprises a face which is inclined with respect to the face of said abutment. In this case, this surface can be parallel to the contact surface of the spring element or inclined by a predetermined value relative to this contact surface. The values of the two inclinations are preferably different from each other. In one embodiment, the values differ only in sign.

In another embodiment, inclined surfaces are used at different ends of the spring element or at the contact surfaces. The contact surfaces of the different flanges which lie opposite one another with respect to the spring element can in particular each comprise a plurality of surfaces which are inclined with respect to the assigned unloaded contact surface of the spring element.

In a further embodiment, the torsional vibration damper comprises more than one spring element, wherein not all spring elements participate in each other for prestressing the flange. In one embodiment, the torsional vibration damper comprises at least one further spring element which is not loaded during the transition between positive and negative torsion of the flange. For example, a complete spring element arrangement for a torsional vibration damper can comprise only one or more spring elements which are longer than the other corresponding spring element of the arrangement, so that after the spring element has been mounted on the flange, a permanently preloaded and therefore play-free torsional vibration damper is present. The assembly can include resilient elements mounted on different radii about the axis of rotation. The first group of spring elements can in particular lie on a first radius and the second group of spring elements on a second radius, wherein the first radius is smaller than the second radius. The first set contains the inner springs and the second set contains the outer springs.

Drawings

The invention will now be described in more detail with reference to the appended drawings. Wherein:

FIG. 1 illustrates an apparatus for transferring torque;

FIG. 2 shows the elastic element of the device according to FIG. 1, and

fig. 3 shows an end of the elastic element of the torsional vibration damper of the device of fig. 1.

Detailed Description

Fig. 1 shows a device 100 for transmitting torque. The device 100 is provided in particular for installation in a drive train, for example in a motor vehicle. The input side 110 and the output side 115 of the device 100 are arranged rotatably about the rotation axis 105. The input side 110 can be connected to a clutch, for example. The output side 115 is embodied as an example as a hub, which can be connected in a torque-locked manner to another element of the drive train by means of a toothing. Furthermore, a turbine 120 of the hydrodynamic torque converter is mounted on the output side 115 in an exemplary manner.

Furthermore, the device 100 comprises a torsional vibration damper 125 and a centrifugal force pendulum 130. The torsional vibration damper 125 comprises an input flange 135, which is embodied here as a separate element by way of example, an output flange 140, which is embodied here in combination with an element of the centrifugal force pendulum 130, and an elastic element 145, which acts between the input flange 135 and the output flange 140 in order to press the two

flanges

135, 140 into the opposite rest state.

The centrifugal force pendulum 130 comprises a pendulum flange 150 on which a pendulum mass 155 is mounted in a movable manner in a plane of rotation about the axis of rotation 105. The pendulum flange 150 is embodied integrally with the output flange 140 of the torsional vibration damper 125.

In the embodiment shown, the torsional vibration damper is located upstream of the centrifugal force pendulum 130 with respect to the torque flow from the input side 110 to the output side 115. The torsional vibration damper 125 is designed without play, i.e., the spring elements 145 exert a restoring force on the

flanges

135 and 140 continuously if the

flanges

135 and 140 are not exactly in their rest state. In another embodiment, the centrifugal force pendulum 130 is located upstream of the torsional vibration damper 125 with respect to the illustrated torque flow. In this case, the centrifugal force pendulum 130 is preferably mounted directly on the input side 110. Particularly preferably, the pendulum flange 150 is connected to the input side 110 without play and rigidly. In this case, the input side 110 can also overlap with the pendulum flange 150.

Fig. 2 shows the elastic element 145 on the device 100 according to fig. 1. In the embodiment shown, the spring element 145 comprises a cylindrical helical spring, although in a corresponding manner, other spring types, in particular a curved spring, are also possible. Three axial views about the axis of rotation 105 are shown from top to bottom. In the upper region of fig. 2, the

flanges

135 and 140 are in their rest state, in the middle region they are twisted with respect to one another by a positive value, and in the lower region they are twisted with respect to one another by a negative value.

Even though the

flanges

135 and 140 do not necessarily have a disk shape and can in particular be provided with additional recesses, they are based on the disk-shaped

flanges

135 and 140 in the following for better understanding. The input flange 135 includes a first spring window 205 and the output flange 140 includes a second spring window 210. The elastic element 145 includes two ends having a first abutment surface 215 or a second abutment surface 220. The first abutment 225 of the input flange 135 and the second abutment 230 of the output flange 140 are provided for mating with the first abutment surface 215. In a corresponding manner, the third abutment 235 of the input flange 135 and the fourth abutment 240 of the output flange 140 are provided for cooperation with the second abutment surface 220. In the illustration of fig. 2, the abutments 225 to 240 are shown spaced apart from the abutment surfaces 215 and 220 at all times. If the spacing does exist, the torsional vibration damper 125 has a clearance that allows the input flange 135 to twist relative to the output flange 140 without a restoring force caused by the spring element 145. In order to minimize or reduce this play to 0 or to render it harmless, it is proposed that the spring element 145 be mounted on the

flanges

135 and 140 or on the abutments 225 to 240 of the

spring windows

205 and 210 in such a way that: in the case of the greatest relaxation of the spring element 145 in the region of the rest state, as shown in the upper region of fig. 2, the load of the spring element 145 is also retained.

In one embodiment, the spring element 145 is dimensioned, for example, such that it is longer in the unloaded state than the respective width of the

spring windows

205 and 220. In this case, the elastic element 145 is longer than a first distance between the first abutment 225 and the third abutment 235 and also longer than a second distance between the second abutment 230 and the fourth abutment 240. Depending on the spring rate of the spring element 145, the length of the spring element can be increased such that the load of the spring element does not fall below a predetermined value. In an exemplary embodiment, the value is in the range of about 0.5 to 5 newtons. Higher loads, for example in the range of 5 to 15 newtons or higher, are also possible.

Fig. 3 shows one end of the elastic element 145 of the torsional vibration damper 125 of the device 100 of fig. 1. The first variant is shown in the upper region and the second variant is shown in the lower region. These views correspond, furthermore, substantially to the views in fig. 2. For illustration reasons, the distance between the axial end of the spring element 145 or the contact surface 220 and the

corresponding contact surface

235 or 240 is also shown here.

In the upper variant, the fourth abutment 240 of the output flange 140 is inclined relative to the assigned abutment surface 220 of the spring element 145, more precisely preferably in a plane of rotation about the axis of rotation 105. The inclination can alternatively be positive or negative. In this embodiment, the third abutment 235 of the input flange 135 is implemented parallel to the assigned abutment face 220.

In the variant shown in the lower part, in addition to the inclination of the fourth abutment 240, the third abutment 235 is also inclined. The two inclinations can correspond to one another or, as illustrated, different inclinations can be provided relative to the contact surface 220. In one embodiment, the inclinations differ only in their sign.

The inclined or

non-inclined abutments

235 and 240 on the side of the second abutment surface 220 can be combined with the inclined or

non-inclined abutments

225 and 230 in the region of the first abutment surface 215.

List of reference numerals

100 device for transmitting torque

105 axis of rotation

110 input side for connection with a drive motor

115 output side for connection to a transmission

120 turbine

125 torsional vibration damper

130 centrifugal force pendulum

135 input flange

140 output flange

145 elastic element

150 pendulum flange

155 pendulum mass

205 first spring window (input flange 135)

210 second spring window (output flange 140)

215 first contact surface (elastic element 145)

220 second contact surface (elastic element 145)

225 first contact portion (input flange 135)

230 second abutting portion (output flange 140)

235 third leaning part (input flange 135)

240 fourth attachment (output flange 140)

Claims

1. Device (100) for transmitting torque, wherein the device (100) comprises the following parts:

-an input side (110) and an output side (115) rotatable around a rotation axis;

-a torsional vibration damper (125), the torsional vibration damper (125) comprising an input flange (135), an output flange (140) and an elastic element (145), wherein the torsional vibration damper (125) is arranged in the torque flow between the input side (110) and the output side (115), wherein each flange (135, 140) has one spring window each, each spring window having two abutments for cooperating with the elastic element (145), the elastic element (145) being located between the two abutments of each spring window, and

a centrifugal force pendulum (130) which is coupled without play to the torsional vibration damper (125),

-wherein the torsional vibration damper (125) is preloaded, the unloaded length of the elastic element (145) being greater than the distance of the corresponding abutments (225) and 240) on each of the flanges (135, 140).

2. The device (100) of claim 1, wherein the centrifugal force pendulum (130) is mounted directly on the input flange (135).

3. The device (100) according to claim 1, wherein the centrifugal force pendulum (130) is directly mounted on the output flange (140).

4. The apparatus (100) of claim 2 or 3,

the spring element (145) is located between the abutments in such a way that it is loaded both when the two flanges (135, 140) are positively twisted with respect to one another and when the two flanges are negatively twisted with respect to one another,

-wherein the elastic element (145) remains loaded at the transition between positive and negative torsion.

5. The device (100) according to claim 4, wherein the load of the elastic element (145) is continuously maintained above a predetermined value at the transition.

6. Device (100) according to claim 4, wherein one of the abutments (225) of one of the flanges (135, 140) comprises a first face inclined by a predetermined value with respect to the assigned abutment face (215, 220) of the unloaded resilient element (145).

7. Device (100) according to claim 6, wherein the abutment (225) of the other of the flanges (135, 140) provided for fitting into the same side of the elastic element (145) comprises a second face inclined with respect to the first face of the abutment of the one flange.

8. Device (100) according to claim 6 or 7, wherein the abutments (225) of the different flanges (135, 140) which are opposite with respect to the spring element (145) each comprise a plurality of faces which are inclined with respect to the assigned unloaded abutment faces (215, 220) of the spring element (145).

9. The device (100) according to claim 4, wherein the torsional vibration damper (125) comprises a further elastic element (145) which is unloaded at the transition between positive and negative torsion of the flange (135, 140).