阅读说明：本技术 扭振减振器 (Torsional vibration damper ) 是由 B·施托贝尔 于 2018-06-07 设计创作，主要内容包括：本发明涉及一种扭振减振器(10),尤其双质量飞轮、带盘去耦器或盘减振器,用于机动车的驱动系中的扭转振动的减振,所述扭振减振器具有：构造环绕的接收空间(14)的初级质量(12)；通过储能器元件(16)、尤其弧形弹簧相对所述初级质量(12)能受限地扭转的次级质量(20)；和与所述储能器元件(16)并联的附加减振器(28),用于机动车的驱动系中的扭转振动的减振。通过所述附加减振器(28)的并联,能够容易地添加更硬的减振级,使得能够实现具有软的弹簧特性曲线和在最大可能的旋转角下具有大阻滞力矩的扭振减振器(10)。(The invention relates to a torsional vibration damper (10), in particular a dual mass flywheel, a reel decoupler or a reel damper, for damping torsional vibrations in a drive train of a motor vehicle, comprising: -constructing a primary mass (12) of a surrounding receiving space (14); 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; and an additional damper (28) connected in parallel with the energy storage element (16) for damping torsional vibrations in a drive train of the motor vehicle. By means of the parallel connection of the additional dampers (28), stiffer damping steps can be easily added, so that a torsional vibration damper (10) with a soft spring characteristic and a large damping torque at the maximum possible angle of rotation can be realized.)

1. 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, having:

a primary mass (12) configured with a surrounding receiving space (14),

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, and

-an additional damper (28) connected in parallel with the energy storage element (16) for damping torsional vibrations in a drive train of a motor vehicle.

2. The torsional vibration damper as claimed in claim 1, characterized in that the secondary mass (20) has an output flange (18) projecting into the receiving space (14) for tangentially abutting against the energy accumulator element (16), wherein the additional damper (28) is coupled to the primary mass (12) and to the output flange (18).

3. The torsional vibration damper according to claim 1 or 2, characterized in that the additional vibration damper (28) has an additional energy storage element (34), in particular in the form of a compression coil spring or an arc spring, wherein the additional vibration damper (28) has a first guide housing (30) which is connected to the primary mass (12) and is intended for partially receiving the additional energy storage element (34), and a second guide housing (32) which is connected to the secondary mass (20), in particular to an output flange (18) of the secondary mass (20), wherein the first guide housing (30) and the second guide housing (32) are configured for tangentially abutting against the additional energy storage element (34).

4. The torsional vibration damper as claimed in claim 3, characterized in that the first guide shell (30) and the second guide shell (32) are configured to be movable past one another in a relatively rotatable manner.

5. The torsional vibration damper as claimed in claim 3 or 4, characterized in that the first guide shell (30) and/or the second guide shell (32) are substantially configured as half-shells having substantially semicircular end sides.

6. The torsional vibration damper as claimed in any of claims 3 to 5, characterized in that the first guide shell (30) and the second guide shell (32) are embodied so as to open in the axial direction, wherein in particular the first guide shell (30) and the second guide shell (32) are configured as identical components.

7. The torsional vibration damper as claimed in one of claims 1 to 6, characterized in that the additional damper (28), in particular a guide shell (30, 32), is connected to the primary mass (12) and/or to the secondary mass (20), in particular to an output flange (18) of the secondary mass (20), by means of pressing, riveting and/or pins.

8. The torsional vibration damper as claimed in one of claims 1 to 7, characterized in that the energy accumulator element (16) is embodied so as to be able to stop tangentially on the primary mass (12) and/or on the secondary mass (20) over a free angle in the circumferential direction, wherein the additional damper (28) is designed to act at least over a large part of the free angle of the energy accumulator element (16).

9. The torsional vibration damper according to one of claims 1 to 8, characterized in that the secondary mass (20) has an output flange (18) which projects into the receiving space (14) for tangentially abutting against the energy storage element (16), wherein the output flange (18) has a transmission flange which bears tangentially against the energy storage element (16) and a connection flange which is coupled thereto in a torque-transmittable manner, wherein a free angle in the circumferential direction is formed between the transmission flange and the connection flange, in particular by means of a toothing, and the additional damper (28) is couplable to the primary mass (12) and to either the connection flange or the transmission flange.

10. A reel assembly for driving an auxiliary device of a motor vehicle by means of a traction means, the reel assembly 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 according to any of claims 1-9, wherein the reel is part of the primary mass (12) and the hub (22) is part of the secondary mass (20) of the torsional vibration damper (10).

Technical Field

The invention relates to a torsional vibration damper, in particular a dual mass flywheel, a belt pulley 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 formed by the primary mass and is intended for receiving the arcuate spring.

The following requirements have been met in torsional vibration dampers in the drive train of motor vehicles: for high comfort, the most flexible spring characteristic is provided, while for large regions of action, the most resistant moment is provided at the maximum possible angle of rotation.

Disclosure of Invention

The object of the present invention is to provide measures which make it possible to implement a torsional vibration damper having a soft spring characteristic and a large damping torque at the maximum possible angle of rotation.

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 are capable of showing one aspect of the invention individually or in combination, are given 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, is provided for damping torsional vibrations in a drive train of a motor vehicle, having: a primary mass constituting a surrounding receive channel; a secondary mass which can be rotated in a limited manner relative to the primary mass by means of an energy storage element, in particular an arc spring; and an additional damper connected in parallel with the energy storage element for damping torsional vibrations in the drive train of the motor vehicle.

By connecting the energy storage element and the additional vibration damper in parallel, a spring characteristic curve can be generated which is stiffer than the spring characteristic curve of the energy storage element alone or of the additional vibration damper alone. By providing the energy storage element and/or the additional damper with a free angle, a rotational angle range of the relative rotation of the secondary mass with respect to the primary mass can additionally be specified, in which rotational angle range only the energy storage element or only the additional damper is active. In this rotational angle range, a damper stage with a soft spring characteristic is thus formed. In the event of a sufficiently strong relative rotation of the secondary mass with respect to the primary mass, the provided free angle is exceeded, so that a correspondingly stiff spring characteristic is acted upon above the free angle by the parallel connection of the energy storage element and the additional damper. In this way, a hard damper stage with a stiff spring characteristic can be connected to a soft damper stage. A soft damper stage is perceived as particularly comfortable by the driver of the motor vehicle. The hard damper stage can damp hard stops when the maximum possible angle of rotation is reached. Furthermore, the maximum possible angle of rotation is only achieved with a correspondingly large retardation torque, so that vibration damping over a correspondingly large torque range is possible. By connecting additional dampers in parallel, stiffer damper stages can easily be added, so that a torsional vibration damper with a soft spring characteristic and a large damping torque at the maximum possible angle of rotation can be realized.

The additional vibration damper can be easily positioned at a distance from the energy storage element, so that free installation space can be used for the additional vibration damper. This makes it possible to keep the installation space requirement low. Furthermore, it is easier to operate the additional vibration damper in a different angle of rotation range than the energy storage element, and a total spring characteristic curve profile with a different range of spring constants is achieved. If the secondary mass is twisted relative to the primary mass in the first circumferential direction or in a second circumferential direction opposite the first direction starting from a neutral zero position, for example, no damping can be provided first of all due to 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 low-pass filter type. However, it is also possible that at the beginning of the relative rotation only the energy storage element or only the additional damper is active first.

The primary mass and the secondary mass, which can be coupled to the primary mass in a rotationally limited manner via the energy accumulator element, which is in particular formed as a curved spring, can form a spring-mass system 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 certain frequency range. In this case, the mass 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 (Motorordnungen) of the motor vehicle engine can be damped. The mass moment of inertia of the primary mass and/or the secondary mass can be influenced in particular by the additional mass installed. The primary mass can have a disk to which a cover can be connected, whereby a substantially annular receiving space for the energy storage element can be delimited. The primary mass can, for example, tangentially stop against the energy storage element by means of a recess projecting into the receiving space. An output flange of the secondary mass projects into the receiving space and can tangentially stop against an opposite end of the energy storage element. If the torsional vibration damper is part of a dual mass flywheel, the primary mass can have a flywheel disk that can be coupled to the drive shaft of the motor vehicle engine. If the torsional vibration damper is part of a reel assembly as a reel decoupler for driving auxiliary devices of a motor vehicle by means of a traction means, the primary mass can form a reel on the radial outer circumference of which the traction means, in particular a wedge belt, can act for torque transmission.

The energy accumulator element can be designed in multiple stages, for example by providing a further bow spring in the bow spring. The outer and inner arcuate springs can act via different free angles and/or have different spring characteristic curves. In addition or alternatively, the additional vibration damper can have an additional energy storage element, which can be designed as a single stage or as a multi-stage. This increases the number of different damping regions for the torsional vibration damper. The overall spring characteristic of the torsional vibration damper can have a plurality of subregions with different spring constants, so that the torsional vibration damper can be individually adapted to different applications including different damping requirements.

The secondary mass has in particular an output flange projecting into the receiving space for tangentially abutting against the energy storage element, wherein the additional damper is coupled to the primary mass and to the output flange. The output flange of the secondary mass usually extends substantially parallel to a disk-shaped region of the primary mass, via which the primary mass can be fastened to a drive shaft of a motor vehicle engine, for example. The additional damper can thus be easily positioned in the axial gap between the disk-shaped region of the primary mass and the output flange. In this case, the additional damper can be arranged in particular in a receiving space formed by the primary mass for receiving the energy storage element, where the additional damper can be protected from external influences. The additional vibration damper can be arranged offset in the radial direction and in the axial direction from the energy storage element. This makes it possible to keep the installation space requirement low.

The additional vibration damper preferably has an additional energy storage element, in particular in the form of a compression coil spring or an arc spring, wherein the additional vibration damper has a first guide housing connected to the primary mass for partially receiving the additional energy storage element and a second guide housing connected to the secondary mass, in particular to an output flange of the secondary mass, for partially receiving the additional energy storage element, wherein the first guide housing and the second guide housing are formed for tangential abutment on the additional energy storage element. Due to the relative rotation of the secondary mass relative to the primary mass, the guide housing can also execute a relative rotation and tangentially stop against the additional energy storage element. This enables a torque exchange between the primary mass and the secondary mass via a torque flow extending parallel to the energy storage element. The guide housing can in particular have in each case a stop acting in the tangential direction on its end face, between which stops an additional energy accumulator element is received, so that torques can be transmitted in each case in different circumferential directions during the relative movement. In particular, the guide shell has not only a tangentially acting stop, but also a guide surface which is directed in the radial direction and/or in the axial direction and on which the additional energy storage element can slide and be guided. The additional energy storage element can be prevented from bending under load by the guide shell. Additionally or alternatively, the guidance of the additional energy storage element can also be achieved by the primary mass and/or the output flange, for example by: a recess with a partially circular cross section is formed in the primary mass and/or in the output flange for receiving an additional energy storage element. The guide housing can thus be formed integrally with the primary mass or with the output flange.

Particularly preferably, the first guide shell and the second guide shell are configured to be able to move past each other in a rotationally fixed manner. This reliably prevents mutual stops of the guide shells. Alternatively, it can be achieved that the additional energy storage element between the guide shells can be maximally compressed into the jammed state. For this purpose, the additional energy storage element can project partially into the region of the first guide shell and partially into the region of the second guide shell in order to form a tangential stop surface for the respective guide shell.

In particular, the first guide shell and/or the second guide shell are substantially configured as half-shells having substantially semicircular end faces. The guide housing can thus have an inner contour which is adapted to the outer contour of the additional energy storage element, which is in particular also configured as a curved helical spring. The guide shells can be positioned at a distance from one another over as small an air gap as possible in order to avoid a jamming stop. At the same time, almost the entire additional energy storage element can be covered by the guide shell. The semicircular end side of the respective guide shell at the end of the rail pointing towards the inner contour of the additional energy storage element can form a significantly larger contact surface with the additional energy storage element than the narrow side of the disk, as a result of which a correspondingly lower surface pressure can be achieved.

Preferably, the first guide shell and the second guide shell are embodied so as to open in the axial direction, wherein the first guide shell and the second guide shell are configured as identical components. The guide housing can thus bear with an axial rear side against the primary or secondary mass, as a result of which good force support and a secure fastening can be achieved. By the guide shells opening not in the radial direction but in the axial direction, the centrifugal forces acting on the additional energy storage element can be supported by two guide shells instead of only one. Thereby avoiding force peaks in the guide housing. Alternatively, the forces occurring can be distributed more lightly between the guide shells.

In particular, the additional damper, in particular the guide shell, is preferably connected to the primary mass and/or to the secondary mass, in particular to the output flange of the secondary mass, by means of a press fit, a rivet connection and/or a pin. A connection with high strength is produced by elastic and/or plastic deformation at the connection point, which connection is also able to withstand large shear forces.

In particular, the energy storage element is designed to be able to stop tangentially at the primary mass and/or at the secondary mass via a free angle in the circumferential direction, wherein the additional damper is designed to act at least over a large part of the free angle of the energy storage element. In the relative angle of rotation of the secondary mass relative to the primary mass, in which the energy storage element is not yet active due to the provided free angle, only the additional damper is active, if necessary also after the free angle is exceeded. In this rotational angle range, therefore, a soft damper stage can be formed, to which a stiffer damper stage is connected after exceeding the free angle provided for the energy storage element by the parallel connection of the additional damper and the subsequently active energy storage element, said damper stage having a greater total spring constant.

Preferably, the secondary mass has an output flange projecting into the receiving space for tangentially abutting against 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, wherein a free angle in the circumferential direction is formed between the transmission flange and the connection flange, in particular by means of the toothing, and can be coupled either to the connection flange or to the transmission flange. Thereby, the additional damper can be attached via a free angle. Depending on whether the additional damper is connected to the connection flange or to the transmission flange, the time during which the free angle formed between the connection flange and the transmission flange is to be effective can be adjusted, as a result of which the overall spring characteristic curve can be adapted accordingly. Particularly, the following steps are set: the additional damper is only active when the free angle provided for the additional damper is exceeded when the secondary mass is twisted relative to the primary mass. This enables, for example, the construction of a low-pass filter in which high frequencies with low amplitudes can be filtered out. In this case, however, the free angle is not formed in the additional damper, but in the at least two-part output flange. As a result, the free angle provided in the radial region of the additional damper can be avoided, so that more installation space can be provided in the circumferential direction for the additional energy storage element. The additional energy storage element of the additional vibration damper can thus be brought into permanent contact (in particular with a preload) with the tangentially acting stop, so that after overcoming the free space, the respective stop can be brought into contact with the additional energy storage element, avoiding a hard stop. The pretensioning of the additional energy storage element ensures that the additional energy storage element does not lift off the stop even in the event of forces occurring during operation. The extension of the additional energy storage element in the circumferential direction can also be increased, as a result of which a softer spring characteristic curve can be achieved.

Particularly preferably, a friction device is provided between the transmission flange and the connection flange, which friction device serves to provide damping against resonance-induced oscillations of the torsional vibrations. By means of the intentionally provided friction, the spring-mass system of the torsional vibration damper can be sufficiently damped, so that excessively strong deflections in the resonance region can be avoided. For this purpose, a relative movement of the transmission flange relative to the connection flange can be used in order to generate a relative movement that contains friction. The friction device can have a first friction pair fixed to the drive flange and a second friction pair fixed to the connection flange, which are pressed against one another with friction, for example by means of a spring. The friction pair can be formed, for example, by an axial friction ring.

The additional damper is arranged in particular in the receiving space. The additional damper can thus be positioned in a larger radius region, which can achieve a correspondingly large extension in the circumferential direction for the additional damper. The additional damper can thus have a correspondingly soft spring characteristic.

The invention also relates to a reel assembly for an auxiliary device for driving a motor vehicle by means of a traction means, having: a reel for driving the traction means; a hub for torque introduction, couplable with a drive shaft of a motor vehicle engine; and a torsional vibration damper, which can be configured and expanded as described above, wherein the reel is part of the primary mass and the hub is part of the secondary mass of the torsional vibration damper. By connecting the additional dampers in parallel, stiffer damping stages can be easily added, so that a torsional vibration damper with a soft spring characteristic and a large damping torque at the maximum possible angle of rotation can be realized.

Drawings

The invention is exemplarily described below according to preferred embodiments with reference to the accompanying drawings, wherein the features shown below can constitute one aspect of the invention both individually and in combination. It shows that:

FIG. 1: a schematic cross-sectional side view of a torsional vibration damper.

Detailed Description

The torsional vibration damper 10, which is illustrated in fig. 1 by way of example as a reel decoupler in a reel assembly for driving auxiliary devices of a motor vehicle by means of a traction means, has a primary mass 12 in the form of a reel, which delimits an annular receiving space 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 radially inner side into the receiving space 14. The secondary mass 20 has, for example, a two-part hub 22 to which the output flange 18 is fixed. Additionally, a rubber bumper 24 is fixed to the hub 22. The fixing means 26, which are provided for fixing the rubber buffer 24 and are configured as positioning pins, also fix 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 can be configured, for example, as a screw connection, a pin connection and/or a press fit. By configuring the securing means 26 as locating pins, the rubber bumper 24 can be easily located on the hub 22.

An additional damper 28 connected in parallel with the energy storage element 16 is connected to the primary mass 12 and the output flange 18. To this end, the additional vibration damper 28 has a first guide shell 30 connected to the primary mass 12 and a second guide shell 32 connected to the output flange 18 and spaced apart from the first guide shell 30 by an air gap, which each receive half of an additional energy accumulator element 34 in the form of a helical compression spring. The axially open guide shells 30, 32 can be stopped tangentially on the inside of their end faces on an additional energy storage element 34 in order to transmit torque. In order to provide the damping characteristics with a soft first damper stage and a hard second damper stage, a free angle can be provided for the energy storage element 16 and/or for the additional damper 28, so that, in the event of a relative rotation of the secondary mass 20 relative to the primary mass 12 within a range of rotation angles, firstly only the energy storage element 16 or only the additional damper 28 is active, and in a range of rotation angles up to the maximum possible rotation angle, both the energy storage element 16 and the additional damper 28 are active. The output flange 18 can be configured in two parts, in that: the output flange 18 has a transmission flange which bears tangentially against the energy storage element 16 and a connection flange which is connected to the hub 22 and is connected to the transmission flange via a free angle in a torque-transmitting manner. If the second guide shell 32 is fastened to the connecting flange, a free angle for the additional damper 28 can be formed outside the additional damper 28.

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 buffer

26 securing device

28 additional vibration damper

30 first guide housing

32 second guide housing

34 additional energy storage elements.