DE102020110947A1 - Torsional vibration damper - Google Patents

Abstract

The invention relates to a torsional vibration damper 1, comprising a damper input part 5, which can be coupled to the drive train 2 on the drive side, and a damper output part 6, which can be coupled to the drive train 2 on the output side, the damper input part 5 and the damper output part 6 to each other about a common axis of rotation against the effect at least one spring device 7 are rotatable, the damper input part 5 and / or the damper output part 6 having means by which the spring device 7 acting in the circumferential direction can be compressed, the means for compressing the spring device 7 comprising a spring coupling flange 8, which on the one hand rotates with the Damper output part 6 is connected and arranged coaxially to this, and on the other hand is coupled to the spring device 7, wherein the spring device 7 is designed as a bow spring 9, which is positioned in a channel-shaped and annular bow spring retainer 10, which is integra l is formed with a damper input disk 11 of the damper input part 5, the arc spring retainer 10 having a radially outer first cross-sectional contour 12 with a radially circumferential, inwardly open V-shape, which is interrupted in the circumferential direction at at least two points by a second cross-sectional contour 13 each, which has a section 14 running axially towards the front edge.

Description

The invention relates to a torsional vibration damper, in particular for a drive train of a motor vehicle, comprising a damper input part which can be coupled to the drive train on the drive side and a damper output part which can be coupled to the drive train on the output side, the damper input part and the damper output part to each other about a common axis of rotation counter to the action at least one spring device are twistable, the damper input part and / or the damper output part having means by which the spring device acting in the circumferential direction of the dual-mass flywheel can be compressed, the means for compressing the spring device comprising a spring coupling flange, which on the one hand is non-rotatably connected to the damper output part and is coaxial is arranged to this, and on the other hand is coupled to the spring device, wherein the spring device is designed as a bow spring, which in a channel-shaped and annular arc enfederretainer is positioned, which is formed integrally with a damper input disk of the damper input part.

Torsional vibration dampers are known in principle for damping torsional vibrations of a drive shaft of a motor vehicle engine. For example, from the DE 10 2008 004 150 A1 a two-mass flywheel is known in which a damper input part is coupled via an arc spring to a damper output part rotatable relative to the damper input part for damping torsional vibrations of a crankshaft of an internal combustion engine. The bow spring is in a bow spring channel
which is also referred to as a bow spring retainer - arranged, wherein a channel wall of the bow spring channel is formed by the damper input part. A flange of the damper output part protrudes into the arc spring duct and is supported on the duct wall via a friction ring.

There is a continuing need to manufacture torsional vibration dampers that are optimized in terms of production technology and at low cost.

This object is achieved by a torsional vibration damper, in particular for a drive train of a motor vehicle, comprising a damper input part which can be coupled to the drive train on the drive side and a damper output part which can be coupled to the drive train on the output side, the damper input part and the damper output part opposing each other about a common axis of rotation the action of at least one spring device, wherein the damper input part and / or the damper output part have means by which the spring device acting in the circumferential direction can be compressed, the means for compressing the spring device comprising a spring coupling flange which, on the one hand, is non-rotatably connected to the damper output part and is coaxial is arranged to this, and on the other hand is coupled to the spring device, wherein the spring device is designed as a bow spring, which in a channel-shaped and annular bow spring retainer p ositioniert is, which is formed integrally with a damper input disk of the damper input part, wherein the arc spring retainer has a radially outer first cross-sectional contour with a radially circumferential, inwardly open V-shape, which is interrupted in the circumferential direction at at least two points by a second cross-sectional contour in each case has a section extending axially towards the front edge.

Due to the construction of a torsional vibration damper according to the invention, this is optimized in terms of production technology, which is explained in more detail below with reference to the exemplary embodiments.

First, the individual elements of the claimed subject matter of the invention are explained in the order in which they are named in the set of claims and particularly preferred embodiments of the subject matter of the invention are described below.

The basic mode of operation of a torsional vibration damper is as follows: A damper input disc and a secondary flywheel connected to the clutch hub in a rotationally fixed manner are resiliently connected via one or more energy stores, in particular spring elements, so that a more or less large angular deflection is achieved under load. The suspension can usually be dampened by a friction device.

For the purposes of this application, the drive train of a motor vehicle is understood to mean all components that generate the power for driving the motor vehicle in the motor vehicle and transmit it to the road via the vehicle wheels.

For the purposes of this application, motor vehicles are land vehicles that are moved by machine power without being tied to railroad tracks. A motor vehicle can, for example, be selected from the group of passenger cars (cars), trucks (trucks), small motorcycles, light motor vehicles, motorcycles, motor buses (KOM) or tractors. A hybrid electric vehicle, also referred to as a Hybrid Electric Vehicle (HEV), is an electric vehicle that is driven by at least one electric motor and another energy converter and generates energy from both its electrical storage (battery) as well as an additional fuel.

In one possible embodiment, a torsional vibration damper can be designed as a two-mass flywheel. A dual mass flywheel can in particular comprise a damper input part, a damper output part, a rotary slide bearing, one or more spring devices and, if necessary, one or more damper devices. In the dual mass flywheel (DMF), the flywheel is divided into the primary flywheel (damper input part) and the secondary flywheel (damper output part). In the torque flow between the damper input part and the damper output part, a spring device is arranged which connects the damper input part and the damper output part to one another in a torsionally flexible manner.

The spring device can in particular comprise a bow spring. To dampen the torsion between the damper input part and the damper output part, a damping device, for example in the form of a friction clutch, can preferably be arranged in the torque flow between the damper input part and the damper output part.

The function of the damper input part is to couple the drive side of the dual mass flywheel with the spring device. The damper input part can in particular be designed in several parts and comprise a damper input disk which is connected to the primary wheel hub in particular via a primary connecting disk. The damper input disk and the primary connection disk can preferably be connected to one another in a rotationally fixed manner by means of riveted connections.

The damper input disk can in particular have a receptacle for the spring device. The receptacle, in particular for a bow spring, is preferably arranged in the form of a channel in the damper input disk. It is particularly preferred that the receptacle for the spring device is formed monolithically with the damper input disk. The bow spring channel is also referred to as a bow spring retainer.

According to a preferred embodiment of the invention, it can be advantageous for the second cross-sectional contours to be offset from one another by 180 °.

It can furthermore be advantageous for the second cross-sectional contours to be of essentially identical design.

In a further development of the invention, it can furthermore be preferred that the arc spring sweeps over a circumferential angle of at least 140 °. the spring element is designed as a compression spring.

Furthermore, it can be advantageous that the spring element has an inner spring.

According to a further advantageous embodiment of the invention, it can be preferred that the spring element is formed from a series connection of several compression or arc springs.

The invention will be explained in more detail below with reference to figures without restricting the general inventive concept. The figures are merely of a schematic nature and are used exclusively for understanding the invention. The same elements are provided with the same reference symbols. The different features of the various exemplary embodiments can also be freely combined with one another within what is technically feasible.

• 1 drei Querschnittsdetailansichten des erfindungsgemäßen Drehschwingungsdämpfers,
• 2 Prozessschritte der Bogenfederretainerfertigung in Frontal- und Querschnittsansichten,
• 3 Bogenfeder und Bogenfederretainer in einer schematischen Seitenansicht, und
• 4 Kraftfahrzeug mit Drehschwingungsdämpfer in einer schematischen Blockansicht.

Show it:

• 1 three detailed cross-sectional views of the torsional vibration damper according to the invention,
• 2 Process steps of bow spring retainer production in frontal and cross-sectional views,
• 3 Bow spring and bow spring retainer in a schematic side view, and
• 4th Motor vehicle with torsional vibration damper in a schematic block view.

1 shows a torsional vibration damper 1 for a drive train 2 of a motor vehicle 3 as it is in the 4th is indicated. The figure shows a detail of the torsional vibration damper 1 in a front view (middle figure) and two cross-sectional views along the cutting planes AA and BB.

The torsional vibration damper 1 comprises a damper input part 5 , which is connected to the drive train on the drive side 2 can be coupled and a damper output part 6th that is attached to the drive train on the output side 2 is connectable. The damper input part 5 and the damper output part 6th are to each other about a common axis of rotation against the action of at least one spring device 7th arranged twistable. The damper input part 5 and / or the damper output part 6th have means through which the spring device acting in the circumferential direction 7th is compressible, wherein the means for compressing the spring device 7th in the embodiment shown a spring coupling flange 8th include, on the one hand non-rotatably with the damper output part 6th is connected and arranged coaxially to this, and on the other hand with the spring device 7th is coupled. The spring device 7th is as Bow feather 9 formed, which in a channel and ring-shaped bow spring retainer 10 is positioned which is integral with a damper input disk 11 of the damper input part 5 is trained. The bow feather retainer 10 has a radially outer first cross-sectional contour 12th with a radially circumferential, inwardly open V-shape, which can be seen from the detailed cross-sectional view of the lower right-hand illustration in FIG 1 is recognizable. This first cross-sectional contour is in the circumferential direction 12th in at least two places by a second cross-sectional contour each 13th interrupted, the one to the front edge axially extending section 14th having. This second cross-sectional contour 13th is in the lower left illustration of the 1 pictured. It can be seen clearly that the axially extending section of the second cross-sectional contour 13th starting from the radially outermost point of the first cross-sectional contour 12th extends, wherein extends to the second cross-sectional contour 13th in the axial direction is followed by a radially outwardly extending section which forms a circumferential circular ring with fastening bores, which is also good in the representations of FIG 2 is recognizable.

The cross-sectional representations of the 1 is also easy to see that the bow spring 9 in the sections of the bow feather retainer 10 in which the first cross-sectional contour 12th is formed (right illustration) at two contact points that of the first cross-sectional contour 12th rests, namely with one contact point each on one of the legs of the V-shaped contour. In the area of the second cross-sectional contour 13th has the bow feather 9 no contact with the bow spring retainer 10 , as you can see from the illustration on the left.

In the embodiment shown, the torsional vibration damper is divided into two, the second cross-sectional contours 13th are then offset by 180 ° opposite, which is good in the 2 you can see. The second cross-sectional contours 13th are designed essentially identically.

The bow feather 9 covers a circumferential angle of at least 140 °. That as a bow feather 9 trained spring element has an inner spring in the embodiment shown, which is particularly good in the 3 can be seen.

The manufacture of the bow feather retainer 10 is based on the 2 explained in more detail. The upper figure of the 2 shows the shape of the bow spring retainer 10 by means of two semicircular slide segments 15th , which are moved in the radial direction outwards to the bow spring retainer 10 into that of the damper input disk 11 to train. As can be seen well from the cross-sectional view, the slide segments have a gable-roof-like, V-shaped contour, which is the corresponding first cross-sectional contour 3 of the bow feather retainer 10 forms. With a 2-way division of the bow spring 9 and an arc spring length greater than 140 ° would be the slide segments 15th no longer in the axial direction from the shaped bow spring retainer 10 can be extended. Through the formation of the second cross-sectional contour 13th however, it is possible to use the slide elements 15th after the formation of the bow spring retainer 10 in their retracted position, which is shown in the figure below 2 is shown axially out of the bow spring retainer 10 to pull. This is also particularly good on the basis of the cross-sectional views along the cutting planes AA and BB of the lower figure in FIG 2 refer to.

the 3 shows the radial contact of the bow spring 9 to the inner surface of the bow spring retainer 10 . It is easy to see that the bow spring 9 on the inner surface of the bow spring retainer 10 in the area of the first cross-sectional contour 13th rests while it is in the area of the second cross-sectional contour 13th no contact with the bow spring retainer 10 Has. In the area between the bow springs 9 the bow spring retainer runs 10 away radially outwards. The transition can be shown flat so that the bow spring 9 can be pushed into the bow spring retainer 19 under moment without great resistance. It is also possible to selectively wind the bow spring 9 from the contact, so to speak, to make it friction-free up to a certain speed.

The invention is not limited to the embodiments shown in the figures. The above description is therefore not to be regarded as restrictive, but rather as explanatory. The following patent claims are to be understood in such a way that a named feature is present in at least one embodiment of the invention. This does not exclude the presence of further features. If the patent claims and the above description define “first” and “second” features, this designation serves to distinguish between two similar features without defining an order of precedence.

List of reference symbols

1

Torsional vibration damper

2

Powertrain

3

Motor vehicle

5

Damper input part

6th

Damper output part

7th

Spring device

8th

Spring coupling flange

9

Bow feather

10

Bow spring retainer

11

Damper input disc

12th

first cross-sectional contour

13th

second cross-sectional contour

14th

axially extending section

15th

Slide segments

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 102008004150 A1 [0002]

Claims (6)

Torsional vibration damper 1, in particular for a drive train 2 of a motor vehicle 3, comprising a damper input part 5, which can be coupled to the drive train 2 on the drive side, and a damper output part 6 which can be coupled to the drive train 2 on the output side, the damper input part 5 and the damper output part 6 to each other around a common axis of rotation are rotatable against the action of at least one spring device 7, the damper input part 5 and / or the damper output part 6 having means by which the spring device 7 acting in the circumferential direction can be compressed, the means for compressing the spring device 7 comprising a spring coupling flange 8 which on the one hand, it is non-rotatably connected to the damper output part 6 and is arranged coaxially therewith, and on the other hand it is coupled to the spring device 7, the spring device 7 being designed as a bow spring 9 which is located in a channel-shaped and annular bow-spring retainer 1 0 is positioned, which is formed integrally with a damper input disk 11 of the damper input part 5, characterized in that the bow spring retainer 10 has a radially outer first cross-sectional contour 12 with a radially inwardly open V-shape which extends in the circumferential direction at at least two points in each case a second cross-sectional contour 13 is interrupted, which has a section 14 running axially towards the end-face edge. Torsional vibration damper 1, after Claim 1 , characterized in that the second cross-sectional contours 13 are offset from one another by 180 °. Torsional vibration damper 1, according to one of the preceding claims, characterized in that the second cross-sectional contours 13 are formed essentially identically. Torsional vibration damper 1 according to one of the preceding claims, characterized in that the bow spring 9 covers a circumferential angle of at least 140 °. the spring element 15 is designed as a compression spring. Torsional vibration damper 1 according to one of the preceding claims, characterized in that the spring element 15 has an inner spring. Torsional vibration damper 1 according to one of the preceding claims, characterized in that the spring element 15 is formed from a series connection of several compression or arc springs.

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