阅读说明：本技术 扭振减振器 (Torsional vibration damper ) 是由 B·施托贝尔 于 2018-05-15 设计创作，主要内容包括：本发明涉及一种扭振减振器,尤其是双质量飞轮、带盘解耦器或盘减振器,用于减振机动车驱动系中的扭振,所述扭振减振器具有：构造有环绕的接收通道(14)的初级质量(12)和次级质量(20),所述次级质量能通过能量存储元件(16)、尤其弧形弹簧相对于所述初级质量(12)受限地扭转,其中,所述次级质量(20)具有输出法兰(18),所述输出法兰伸入到所述接收通道(14)中,用于切向止挡在所述能量存储元件(16)上,其中,所述输出法兰(18)具有传递法兰(28)和连接法兰(30),所述传递法兰切向贴靠在所述能量存储元件(16)上,所述连接法兰通过附加减振器(34)可传递扭矩地与所述传递法兰(28)耦合,其中,尤其在所述传递法兰(28)和所述连接法兰(30)之间构造齿部(32)并且所述附加减振器(34)被定位在所述齿部(32)中。通过在转动角度范围的端部处才起作用的附加减振器(34)能够在尽可能长且软的能量存储器元件(16)中在可能的最大转动角度下达到高的卡死力矩,使得能够实现具有软的弹簧特性曲线的扭振减振器(10)。(The invention relates to a torsional vibration damper, in particular a dual mass flywheel, a belt disk decoupler or a disk damper, for damping torsional vibrations in a drive train of a motor vehicle, comprising: a primary mass (12) and a secondary mass (20) which are formed with a circumferential receiving channel (14), the secondary mass can be rotated in a limited manner relative to the primary mass (12) by means of an energy storage element (16), in particular an arc spring, wherein the secondary mass (20) has an output flange (18) which projects into the receiving channel (14) for tangential abutment against the energy storage element (16), wherein the output flange (18) has a transfer flange (28) and a connecting flange (30), the transmission flange bears tangentially against the energy storage element (16), the connection flange being coupled to the transmission flange (28) in a torque-transmitting manner by means of an additional damper (34), wherein, in particular, a toothing (32) is formed between the transmission flange (28) and the connection flange (30) and the additional damper (34) is positioned in the toothing (32). The additional vibration damper (34) which is active only at the end of the range of rotational angles makes it possible to achieve a high blocking torque in the longest possible and soft energy storage element (16) at the maximum rotational angle possible, so that a torsional vibration damper (10) with a soft spring characteristic can be achieved.)

1. A torsional vibration damper, in particular a dual mass flywheel, a tape disc decoupler or a disc damper, for damping torsional vibrations in a drive train of a motor vehicle, the torsional vibration damper having:

a primary mass (12) configured with a surrounding receiving channel (14); and

a secondary mass (20) which can be rotated in a limited manner relative to the primary mass (12) by means of an energy storage element (16), in particular an arc spring, wherein the secondary mass (20) has an output flange (18) which projects into the receiving channel (14) for a tangential stop on the energy storage element (16), wherein the output flange (18) has a transmission flange (28) which bears tangentially against the energy storage element (16) and a connection flange (30) which is coupled to the transmission flange (28) in a torque-transmitting manner by means of an additional damper (34),

wherein, in particular, a toothing (32) is formed between the transmission flange (28) and the connection flange (30) and the additional damper (34) is positioned in the toothing (32).

2. The torsional vibration damper as claimed in claim 1, characterized in that the additional damper (34) is designed to seize before the energy storage element (16) seizes when the relative torsion of the secondary mass (20) relative to the primary mass (12) increases.

3. The torsional vibration damper according to claim 1 or 2, characterized in that the primary mass (12) and the transmission flange (28) bear tangentially against the energy storage element (16), wherein in particular the energy storage element (16) is configured to bear permanently tangentially against the primary mass (12) and the transmission flange (28) during ongoing operation, wherein in particular the energy storage element (16) is prestressed between the primary mass (12) and the transmission flange (28).

4. The torsional vibration damper as claimed in any of claims 1 to 3, characterized in that only the additional damper (34) has a free angle which is arranged between the primary mass (12) and the secondary mass (20) when the relative rotational direction is reversed.

5. The torsional vibration damper according to one of claims 1 to 4, characterized in that the additional vibration damper (34) has an additional energy storage element (36), in particular in the form of a compression coil spring or an arc spring, wherein the additional energy storage element (36) is received on the transmission flange (28) in a manner pretensioned in the tangential direction and/or in the circumferential direction at both axial ends, and the connecting flange (30) that can be twisted relative to the transmission flange (28) can be received on the additional energy storage element (36) via a free-angle tangential stop, and/or the additional energy storage element (36) is received on the connecting flange (30) in a manner pretensioned in the tangential direction and/or in the circumferential direction at both axial ends, and the transmission flange (28) that can be twisted relative to the connecting flange (30) can be received on the connecting flange (30) via a free-angle tangential stop The additional energy storage element (36).

6. The torsional vibration damper as claimed in any of claims 1 to 5, characterized in that the teeth (38) of the transmission flange (28) are arranged offset in the axial direction with respect to the teeth (40) of the connection flange (30).

7. The torsional vibration damper as claimed in any of claims 1 to 6, characterized in that friction means are provided between the transmission flange (28) and the connection flange (30) for damping torsional vibration increases caused by resonance.

8. The torsional vibration damper as claimed in one of claims 1 to 7, characterized in that the connecting flange (30) has two side disks (42) which are spaced apart from one another in the axial direction, wherein the transmission flange (28) projects between the side disks (42) in the toothing (32) or the transmission flange (28) has two side disks (42) which are spaced apart from one another in the axial direction, wherein the connecting flange (30) projects between the side disks (42) in the toothing (32).

9. The torsional vibration damper as claimed in one of claims 1 to 8, characterized in that the roots of the transmission flange (28) in the teeth (32) and/or the roots of the connection flange (30) in the teeth (32) project in the axial direction for guiding the additional damper (34) radially outwards.

10. A reel assembly for driving a motor vehicle auxiliary device by means of a traction means, having a reel for driving the traction means, a hub (22) for introducing a torque, which can be coupled to a drive shaft of a motor vehicle engine, and a torsional vibration damper (10) according to one of claims 1 to 9, wherein the reel is part of a primary mass (12) of the torsional vibration damper and the hub (22) is part of a secondary mass (20) of the torsional vibration damper.

Technical Field

The invention relates to a torsional vibration damper, in particular a dual mass flywheel, a belt disk decoupler or a disk damper, by means of which torsional vibrations in the drive train of a motor vehicle can be damped.

Background

A torsional vibration damper configured as a dual mass flywheel is known, for example, from DE 102015221022 a1, which has a primary mass and a secondary mass which can be rotated in a limited manner relative to the primary mass by means of an arcuate spring, wherein the secondary mass has an output flange which projects into a receiving channel which is formed by the primary mass and serves to receive the arcuate spring.

The following requirements continue to exist for torsional vibration dampers in the drive train of motor vehicles: the spring characteristic curve is as soft as possible in the smallest possible installation space.

Disclosure of Invention

The object of the invention is to provide the following measures: which makes it possible to realize a torsional vibration damper with a soft spring characteristic curve in as small an installation space as possible.

According to the invention, this object is achieved by a torsional vibration damper having the features of claim 1. Preferred configurations of the invention, which can each represent an aspect of the invention individually or in combination, are described in the dependent claims and in the following description.

According to the invention, a torsional vibration damper, in particular a dual mass flywheel, a belt disk decoupler or a disk damper, for damping torsional vibrations in the drive train of a motor vehicle, having a primary mass and a secondary mass which are designed with a circumferential receiving channel, the secondary mass can be rotated in a limited manner relative to the primary mass by means of an energy storage element, in particular an arc spring, wherein the secondary mass has an output flange which projects into the receiving channel for tangential stopping on the energy storage element, wherein the output flange has a transmission flange which bears tangentially against the energy storage element and a connection flange which is coupled to the transmission flange in a torque-transmitting manner via an additional damper, in particular, a toothing is formed between the transmission flange and the connection flange and the additional damper is positioned in the toothing.

By means of an additional damper which is additionally provided in addition to the energy storage element, a desired free angle can be provided in the additional damper, so that the additional damper acts from a different rotational angle between the primary mass and the secondary mass than the rotational angle provided in the energy storage element. Thereby, the vibration damping characteristic varying over the rotation angle can be easily realized. Thus, when the range of rotation angles covers only a small rotation angle, the spring characteristic determined solely by the energy storage element can be set when the primary mass is twisted slightly relative to the secondary mass, while the spring characteristic determined by the energy storage element and the additional damper can be set automatically when the rotation angle is greater than the rotation angle at which the free angle provided in the additional damper is exceeded and the damping function of the pre-damper is activated. The additional spring force of the additional damper makes it possible to set a spring characteristic curve with a sectionally different overall spring constant in comparison to a torsional vibration damper without the additional damper. At the same time, a relatively soft damping can be achieved over a sufficiently large range of rotation angles, which is perceived as particularly comfortable. The free angle in the region of the energy storage element can be reduced or even completely avoided, so that more space is left for the energy storage element in the circumferential direction. This can enable the energy storage element to extend more in the circumferential direction and thus achieve a greater distance in order to enable the energy storage element to be compressed by that distance. In this way, a softer spring characteristic curve of the energy storage element can be achieved than in the otherwise identical torsional vibration damper, in which the free angle to be provided engages the energy storage element in the circumferential direction.

By positioning the additional damper spaced apart from the energy storage element, the additional damper is arranged non-coaxially to the energy storage element and can therefore easily be operated independently of the energy storage element. This makes it easier to operate the additional damper in a different range of angles of rotation than the energy storage element and to achieve a total spring characteristic curve with regions of different spring constants. The energy storage element with the softer spring characteristic is already compressed and jammed to the maximum before the maximum possible angle of rotation is reached, so that, with a further increase in the angle of rotation, only the additional damper or only the energy storage element with the harder spring characteristic is still active. This makes it possible to set a particularly large blocking torque at which the maximum possible angle of rotation of the primary mass relative to the secondary mass is achieved. Due to the at least two-part design of the output flange of the secondary mass, a free angle for the additional damper can be easily provided by the torque-transmitting coupling of the transmission flange to the connection flange of the multi-part output flange. Relative rotation of the transmission flange relative to the connection flange can take place in the output flange of the secondary mass substantially independently of the compression of the energy storage element, so that relative rotation of the transmission flange relative to the connection flange is not limited by the energy storage element. The additional vibration damper can be connected in series to the energy storage element and for this purpose integrated in the multi-part output flange. The additional damper is coupled only indirectly to the primary mass via the transmission flange and the energy storage element. The additional damper can be easily positioned in the circumferential direction between the teeth of the toothing, wherein the free angle for the additional damper can be set by the distance of the teeth of the transmission flange in the circumferential direction from the teeth of the connection flange. In this way, a particularly large free angle for the additional damper can be easily achieved. There is no need for a separate window configured to be surrounded by only one member to receive the additional damper. Alternatively, the teeth which are connected in the circumferential direction can form tooth intermediate spaces which are open in the radial direction for receiving the additional damper, wherein the side which is open in the radial direction can be delimited by the tooth root of the component of the output flange which is opposite in the tooth section. This results in a receiving region for the additional damper which can be produced in a simple manner, without the need for a further component having a circumferential window for guiding and/or stabilizing the additional damper. By means of the additional damper, which is arranged in particular in the tooth intermediate space of the toothing of the multi-part output flange, a torsional vibration damper with a soft spring characteristic curve can be realized in a small installation space.

The primary mass and the secondary mass can form a spring-mass system, which is coupled to the primary mass in a torsionally limited manner via an energy storage element, in particular in the form of an arc spring, and which can damp rotational irregularities in the rotational speed and in the torque of the drive power generated by the motor vehicle engine in a specific frequency range. In this case, the moments of inertia of the primary and/or secondary masses and the spring characteristic of the energy storage element can be selected such that vibrations in the frequency range of the dominant engine stage of the motor vehicle engine can be damped. In particular, the moment of inertia of the primary mass and/or the secondary mass can be influenced by the additional mass installed. The primary mass can have a disk to which a cover can be connected, as a result of which an essentially annular receiving space for the energy storage element can be delimited. The primary mass can be stopped tangentially on the energy storage element, for example, by a stamp projecting into the receiving space. An output flange of the secondary mass can project into this receiving space, which can tangentially stop against the opposite end of the energy storage element. When the torsional vibration damper is part of a dual-mass flywheel, the primary mass can have a flywheel that can be coupled to a drive shaft of the motor vehicle engine. When the torsional vibration damper is part of a reel assembly as a reel decoupler (which serves to drive motor vehicle auxiliaries by means of a traction means), the primary mass can form a reel on the radially outer surface of which a traction means, in particular a wedge belt, acts for transmitting torque.

Preferably, the additional damper is designed to jam before the energy storage element jams when the relative rotation of the secondary mass relative to the primary mass increases. If the secondary mass is twisted starting from the neutral zero relative to the primary mass in a first circumferential direction or in a second circumferential direction opposite the first circumferential direction, for example, no damping can be provided first of all because of the free angle provided for the energy store and the additional damper, so that particularly high frequencies with low amplitudes can be filtered out in the manner of a low-pass filter. However, it is also possible for only the energy storage element or both the energy storage element and the additional damper to be active initially with the start of the relative rotation. The energy storage element has, in particular, a softer spring characteristic than the additional vibration damper. In the relative rotation in which both the energy storage element and the additional damper connected in series are active, a damper class is obtained with a particularly soft damping, which is perceived as particularly comfortable by the driver of the motor vehicle. However, the additional damper can jam and essentially appear as a solid before the maximum possible rotation angle is reached. In this way, a damping range determined solely by the spring characteristic curve of the energy storage element, which spring characteristic curve is present as a stiffer spring characteristic curve than a series connection of the energy storage element and the spring portion of the additional damper, is achieved for torsional angles exceeding the above-mentioned rotation angle. By locking the additional damper before the maximum possible rotation angle is reached, a soft damping stage can be realized up to the locking of the additional damper, after which the hard damping stage engages the soft damping stage. The soft damping stage enables a comfortable damping, while the hard damping stage enables a hard impact to be damped when the maximum possible rotation angle is reached. It is also possible to provide the energy storage element with such a large free angle that at the beginning of the relative rotation only the additional damper is activated until the locking or vice versa before the energy storage element is activated. It is also possible for the spring element, which is in particular embodied as an arc spring, of the additional vibration damper to cover a longer extension and/or a greater angular range in the circumferential direction than the energy storage element or vice versa. Furthermore, the spring element of the additional damper can be prevented from being compressed too strongly by jamming of the additional damper before the maximum possible rotation angle is reached.

In particular, the primary mass and the transmission flange bear tangentially against the energy storage element, wherein in particular the energy storage element is designed to bear permanently tangentially against the primary mass and the transmission flange during ongoing operation, wherein in particular the energy storage element is prestressed between the primary mass and the transmission flange. In this way, it is possible to avoid the provision of a free angle in the radial region of the energy storage element, so that more installation space can be provided for the energy storage element in the circumferential direction. The pretensioning of the energy storage element ensures that the energy storage element is not lifted from the primary mass or from the transmission flange even in the event of forces during ongoing operation. This also makes it possible to avoid unnecessary material stresses by the stop of the energy storage element on the primary mass or on the transmission flange.

Preferably, only the additional damper has a free angle which is arranged between the primary mass and the secondary mass when the relative rotational direction is reversed. The damping action of the additional damper is switched off by this free angle, so that only the damping action of the energy storage element is active. The damping action of the additional damper only acts towards the end of the possible angle of rotation range when the free angle provided in the additional damper is exceeded. In a range of rotation angles greater than this free angle up to the maximum possible rotation angle, the spring action of the energy storage element and the additional damper can be superposed. In this case, the energy storage element can be formed without a free angle, so that the damping effect of the energy storage element can be initially effective.

Particularly preferably, the additional damper is arranged within the receiving channel. The additional damper can thereby be positioned over a relatively large radius region, which enables a correspondingly large free angle for the additional damper.

In particular, the additional vibration damper has an additional energy storage element, in particular in the form of a compression coil spring or a bow spring, wherein the additional energy storage element is received on the transmission flange in a manner pretensioned in the tangential direction and/or in the circumferential direction at both axial ends, and a connection flange that can be rotated relative to the transmission flange can be held against the additional energy storage element by a free-angle tangential stop, and/or the additional energy storage element is received on the connection flange in a manner pretensioned in the tangential direction and/or in the circumferential direction at both axial ends, and a transmission flange that can be rotated relative to the connection flange can be held against the additional energy storage element by a free-angle tangential stop. The additional energy storage element is thus not supported on the one hand on the transfer flange and on the other hand on the connection flange, but rather only on one of these components. The additional energy storage element can be extended and supported with a pretensioning force in the entire tooth interspace of either the transmission flange or the connection flange by means of the teeth arranged between the transmission flange and the connection flange. When the transmission flange is rotated so strongly relative to the connection flange that the set free angle is swept over, a part of the respective further component moves past the component supporting the additional energy storage element and tangentially stops on the additional energy storage element in order to compress the additional energy storage element. The additional energy storage element can be lifted on the side where the stop is located and is supported on the component that performs the relative movement. The tooth intermediate spaces of the coupling flange or the teeth of the transmission flange which do not receive the additional energy storage element are embodied in particular so large that two teeth of the transmission flange or the coupling flange which receive the additional energy storage element can be received. Thereby, the additional energy storage element received in the smaller tooth intermediate space is positioned completely in the larger tooth intermediate space together with the tooth supporting the additional energy storage element. Depending on the relative direction of rotation, one tooth of the larger tooth intermediate space stops tangentially on one side of the additional energy storage element or the other tooth of the larger tooth intermediate space stops tangentially on the other side of the additional energy storage element.

Preferably, the teeth of the transfer flange are arranged offset in the axial direction from the teeth of the connection flange. The teeth of the transfer flange and the teeth of the connecting flange do not overlap in a straight line as seen in the circumferential direction. Thereby avoiding that the teeth directly stop against each other. Alternatively, it is ensured that the torque transmission can take place only via the additional damper connected in between, which for this purpose can tangentially stop at the teeth of the transmission flange and the teeth of the connection flange at different positions offset in the axial direction from one another.

Particularly preferably, a friction device is provided between the transmission flange and the connection flange for damping torsional oscillations arising from resonance vibrations. The spring-mass system of the torsional vibration damper can be sufficiently damped by the intentionally provided friction, so that excessively strong deflections in the resonance region can be avoided. For this purpose, a relative movement with friction can be generated by means of a relative movement of the transmission flange relative to the connection flange. The friction device can have a first friction partner fixed to the transmission flange and a second friction partner fixed to the connection flange, which are pressed frictionally against one another, for example by means of a spring. These friction partners can be represented, for example, by axial friction rings.

In particular, it is provided that the connecting flange has two side disks spaced apart from one another in the axial direction, wherein the transmission flange projects between the side disks in the toothing, or that the transmission flange has two side disks spaced apart from one another in the axial direction, wherein the connecting flange projects between the side disks in the toothing. Thereby, the teeth of the transfer flange and the connection flange can easily be moved past each other in order to compress the additional damper, while at the same time a substantially centered stress of the additional damper can be achieved upon compression. This prevents unnecessary bending and bending moments and shear loads of the additional damper.

Preferably, the tooth root of the transmission flange projects in the axial direction in the toothing and/or the tooth root of the connection flange projects in the toothing for guiding the additional damper radially to the outside. The guidance of the additional vibration damper, in particular of the additional energy storage element, can thereby be improved, for example, in order to avoid longitudinal bending of the additional energy storage element under load. The raised region can in particular abut against the outer contour of the additional damper or the additional energy storage element. In particular, when the transmission flange or the connection flange is formed by two side disks, the portion protruding from the tooth root can be produced simply by stamping and non-cutting forming.

The invention also relates to a reel assembly for driving a motor vehicle auxiliary device by means of a traction means, having a reel for driving the traction means, a hub for introducing a torque, which can be coupled to a drive shaft of a motor vehicle engine, and a torsional vibration damper, which can be designed and expanded as described above, wherein the reel is part of a primary mass of the torsional vibration damper and the hub is part of a secondary mass of the torsional vibration damper. The additional vibration damper, which is arranged in particular in the tooth intermediate space of the toothing of the multi-part output flange, makes it possible to realize a torsional vibration damper with a soft spring characteristic curve in a small installation space.

Drawings

The invention is elucidated below by way of example with reference to the accompanying drawings, in which the features presented below can present an aspect of the invention both individually and in combination. The figures show:

FIG. 1 is a schematic cross-sectional side view of a torsional vibration damper, an

Fig. 2 is a schematic sectional top view of the torsional vibration damper of fig. 1.

Detailed Description

In fig. 1 and 2, a torsional vibration damper 10 is illustrated by way of example as a spool decoupler in a spool assembly for driving auxiliary devices of a motor vehicle by means of a traction means, said torsional vibration damper having a primary mass 12 in the form of a spool which delimits an annular receiving channel 14 for an energy storage element 16 in the form of an arc spring. The outlet flange 18 of the secondary mass 20 projects from the radial inside outwards into the receiving channel 14. The energy storage element 16 is tensioned at its tangential ends between the primary mass 12 and the output flange 18 with a pretension, without play in the circumferential direction, i.e. without a free angle. The secondary mass 20 has, for example, a two-part hub 22, to which the output flange 18 is fastened. Additionally, a rubber bumper 24 is fixed to the hub 22. The fastening means 26 provided for fastening the rubber buffer 24 and configured as screws also fasten the output flange 18, which extends centrally to the energy storage element 16, to the hub 22 and hold the multi-part hub 22 together. The fastening means 26 may be configured, for example, as a screw connection, a pin connection and/or an interference fit. The rubber bumper 24 can be easily positioned on the hub 22 by configuring the fixing means 26 as positioning pins.

The output flange 18 of the secondary mass 20 has a radially outer transfer flange 28 and a radially inner connecting flange 30, between which teeth 32 are formed. As shown in fig. 2, an additional damper 34 having an additional energy storage element 36 in the form of a compression coil spring is arranged in the toothing 32. The additional energy storage element 36 is mounted with a preload in the tooth interspace between the two first teeth 38 of the transmission flange 28. The tooth interspace between the two second teeth 40 of the connecting flange 30 is so large that the additional damper 34, which is composed of the two first teeth 40 and the additional energy storage element 36, can be received.

As shown in fig. 1, the connecting flange 30 is composed of two side disks 42, which are arranged offset from the transmission flange 28 in the axial direction, so that the second tooth 40 can move past the first tooth 38 during relative rotation, in order to be able to come into tangential abutment against the additional energy storage element 36 of the additional vibration damper 34 after overcoming the free angle. As a result, the additional energy storage element 36 can be compressed between the transmission flange 28 and the connection flange 30 and can transmit torque between the transmission flange 28 and the connection flange 30. Furthermore, in the root region of the side disk 42 of the connecting flange 30, a wing 44 can project, which can guide the additional energy storage element 36 and/or can support against bending.

List of reference numerals

10 torsional vibration damper

12 primary mass

14 receiving channel

16 energy storage element

18 output flange

20 secondary mass

22 hub

24 rubber vibration damper

26 securing device

28 transfer flange

30 connecting flange

32 tooth part

34 additional vibration damper

36 additional energy storage element

38 first tooth

40 second tooth

42 side plate

44 wing part