DE112018007303T5 - TORSION DAMPER - Google Patents

Abstract

The invention provides a torsion damper, wherein the primary mass part and the channel cover part are attached to one another at the outer circumference and at least part of the support ring is arranged between the primary mass part and the flange in the axial direction of the torsion damper and the flange, the diaphragm spring and the secondary mass part are attached to one another and the diaphragm spring is located between the flange and the secondary mass part and is pressed elastically against the channel cover part. The support ring comprises an adjustment support ring and a fixed support ring which supports the flange, wherein the axial section of the adjustment support ring is wedge-shaped and when the pressure drops between the flange and the primary mass part due to the wear and / or the plastic deformation of the diaphragm spring, the adjustment support ring moves in the direction of the radial outer side of the torsional damper moved relative to the fixed support ring under the action of centrifugal force, so that the axial distance between the primary mass part and the flange is maintained or increased and the spring force of the diaphragm spring remains approximately constant.

Description

Technical area

The present invention relates to components of a transmission system, in particular a torsion damper.

Background of the invention

Various shock absorbers are currently used to improve the NVH performance of automobiles. For example, torsional dampers are known in the art, such as. B. CN107429789A and CN107076260A . In particular, this torsional damper can be a two-mass flywheel which is used to reduce torsional vibrations of the drive shaft of a motor vehicle engine.

In order to reduce the resonance of the torsional damper, the basic damping must be kept at an appropriate value.

1 shows a sectional view of a known torsional damper 100 . The torsional damper 100 has a spacer 10 that is used to connect to the crankshaft, a primary mass part (primary flywheel) 20th and a locking ring 30th on. The spacer 10 , the primary mass part 20th and the locking ring 30th are through the rivets 110 connected with each other.

The torsional damper 100 also includes a flange 40 , a secondary mass part (hub) 50 and a diaphragm spring 60 that between the flange 40 and the secondary mass part 50 is arranged. The flange 40 , the secondary mass part 50 and the diaphragm spring 60 are through the rivets 120 connected with each other. The inner peripheral portion of the secondary mass part 50 forms a wedge socket 51 which transmits the rotation, for example, to an input shaft of a transmission.

The torsional damper 100 also includes a channel cover member 70 that on the outer circumference with the primary mass part 20th is welded, and a channel for receiving an arc spring as an energy storage element is on the radial outer section of the torsional damper 100 between the primary mass part 20th and the channel cover part 70 arranged.

The torsional damper 100 also includes a friction ring 80 and the friction ring 80 is by a diaphragm spring 60 against the duct cover part 70 pressed. Because the contact area between the friction ring 80 and the duct cover part 70 is relatively large, the frictional force is also relatively large. Therefore it can be assumed that during the rotation of the primary mass part 20th and the channel cover part 70 opposite the flange 40 and the secondary mass part 50 only between the diaphragm spring 60 and the friction ring 80 relative rotation takes place and between the friction ring 80 and the duct cover part 70 static friction is maintained, with no relative movement taking place.

The torsional damper 100 also includes a backup ring 90 holding the flange 40 supports. In the axial direction A. of the torsion damper 100 is a radial extension part of the support ring 90 between the primary mass part 20th and the flange 40 clamped. Because of this, there is rotational friction between the support ring 90 and the primary mass part 20th and / or the flange 40 .

The test bench test and the road test determined that the basic damping of the tested (used) torsional damper 100 is obviously lower than that of the new (unused) torsional damper 100 . This is mainly because the spring force of the diaphragm spring 60 decreases. The reasons for the decrease in the spring force: (1) Wear of the support ring 90 ; and (2) plastic deformation of the diaphragm spring 60 . At the in 1 The design shown cannot compensate for this wear and tear.

Object of the invention

The object of the present invention is to overcome or at least reduce the deficiencies according to the current state of the art and to provide a torsion damper which can automatically adjust the spring force of the diaphragm spring in the event of wear and / or plastic deformation of the diaphragm spring.

A torsion damper is developed which has a primary mass part, a support ring, a flange, a diaphragm spring, a secondary mass part and a duct cover part, the primary mass part and the duct cover part being fastened to one another at the outer circumference and at least a part of the support ring between the primary mass part in the axial direction of the torsion damper and the flange is arranged and the flange, the diaphragm spring and the secondary mass part are fixed to each other and the diaphragm spring is located between the flange and the secondary mass part and is elastically pressed against the channel cover part.

The support ring comprises an adjustment support ring and a fixed support ring which supports the flange, the axial portion of the adjustment support ring being wedge-shaped and when the pressure decreases between the Flange and the primary mass part due to the wear and / or the plastic deformation of the diaphragm spring, the adjustment support ring moves under the action of centrifugal force against the fixed support ring to the radial outside of the torsional damper in order to keep the spring force of the diaphragm spring approximately constant.

In at least one embodiment, the fixed support ring is a ring element with an approximately L-shaped axial section, the adjustment support ring having a plurality of arcuate ring segments.

In at least one embodiment, in the axial section of the support ring, the contact surface between the fixed support ring and the adjustment support ring forms a straight line with a radial inclination relative to the torsion damper.

In at least one embodiment, the axial thickness of the adjustment support ring is designed such that it becomes smaller the closer it is to the radial outer side of the torsional damper.

In at least one embodiment, the fixed support ring comprises an axial extension part that extends along the axial and circumferential directions of the torsional damper, and a radial extension part that extends along the axial and peripheral directions of the torsional damper. The axial thickness of the radial extension part is greater at the position closer to the radially outer side.

In at least one embodiment, the adjustment support ring is arranged between the fixed support ring and the primary mass part. The torsional damper also includes a retaining ring that is attached to the primary mass portion. The retaining ring is configured so that it can prevent the ring segments of the adjustment support ring from falling to the radially inner side of the torsional damper.

In at least one embodiment, the adjustment support ring is arranged between the fixed support ring and the flange, wherein the fixed support ring can prevent the ring segments of the adjustment support ring from falling down towards the radial inside of the torsion damper.

In at least one embodiment, the adjustment support ring is made of plastic.

In at least one embodiment, the torsional damper also has a friction ring, the outer circumference of the diaphragm spring being pressed against the channel cover part by the friction ring.

In at least one embodiment, the torsional damper is a dual-mass flywheel or a dual clutch damper.

In the event of component wear and / or plastic deformation of the diaphragm spring, the adjustment support ring can move outward in the radial direction under the action of centrifugal force, so that the axial distance between the primary mass part and the flange is maintained or increased in order to ensure that the spring force of the Diaphragm spring remains almost constant.

Figure list

• 1 shows an axial partial sectional view of a known torsional damper.
• 2A Fig. 13 is a partial sectional view in the first embodiment according to the present invention.
• 2 B FIG. 13 shows a partially enlarged view of the FIG 2A illustrated torsional damper.
• 3 FIG. 11 shows an axial view of the torsion damper in FIG 2A .
• 4th shows a partial sectional view of the im 2A shown torsional damper in used condition.
• 5 shows an axial view of the in 2A shown torsional damper in used condition.
• 6A and 6B Fig. 13 shows a partial sectional view of a torsion damper in the second embodiment according to the present invention.

Detailed embodiments

An exemplary embodiment according to the present invention is explained below with reference to the figures.

The first embodiment

In 2A to 5 becomes the torsional damper 200 shown in the first embodiment according to the present invention. The structure of the torsion damper 200 agrees with the in 1 illustrated torsion damper 200 match. Therefore, the same or similar reference numerals are used for the same or similar parts as in FIG 1 used. The main focus below is on optimizing the in 1 illustrated structure according to the present invention.

In this embodiment, the existing single support ring is 90 divided into two components, namely the fixed support ring 91 and the adjustment support ring 92 . The solid support ring 91 and the adjustment support ring 92 can move relative to each other.

The solid support ring 91 remains in contact with the flange 40 to the flange 40 to support.

More precisely, the fixed support ring 91 the following components: an axial extension part 91A for contact with the inner circumference of the flange 40 which is roughly along the axial direction A. and the circumferential direction C. of the torsion damper 200 extends; a radial extension part 91B that with the axial extension part 91A forms a unit and extends approximately along the radial direction R. and the circumferential direction C. of the torsion damper 200 extends. The radial extension part 91B is located between the adjustment support ring 92 and the flange 40 , wherein an axial side of the radial extension part 91B (right side of the 2A and 2 B) with the flange 40 is in contact and the other axial side 911 (please refer 2 B) of the radial extension part 91B the adjustment support ring 92 touched. The axial portion of the radial extension part 91B is roughly wedge-shaped. The axial thickness of the radial extension part 91B is shaped to be larger at the position closer to the radially outside. More precisely, it forms in the axial section of the torsional damper 200 the other side 911 an oblique line opposite to the radial direction R. is inclined.

The adjustment support ring 92 is located between the primary mass part 20th and the fixed support ring 91 . Corresponding to the radial extension part 91B of the fixed support ring 91 is also the axial portion of the adjustment support ring 92 roughly wedge-shaped. The axial thickness of the adjustment support ring 92 is designed so that the closer the thickness is to the radial outside, the smaller. More precisely, it forms in the axial section of the torsional damper 200 an axial side surface 921 of the adjustment support ring 92 an oblique line relative to the radial direction R. is inclined.

It is assumed that the spacer 10 , the primary mass part 20th etc. in 3 and 5 are omitted, so that the fixed support ring 91 and the adjustment support ring 92 are axially visible. Referring to 3 and 5 forms the fixed support ring 91 in the circumferential direction C. of the torsion damper 200 preferably a single piece and the adjustment support ring 92 into several ring segments 92A , 92B , 92C and 92D which are all arcuate. The adjustment support ring 92 is in several ring segments 92A , 92B , 92C and 92D split to make sure the adjustment support ring 92 relative to the fixed support ring 91 can move to the radial outside, especially in the event of wear of the support ring 90 .

Referring to 2A , 2 B and 4th can the locking ring 30th several ring segments 92A , 92B , 92C , 92D Support from the radial inside to avoid one or more ring segments 92A , 92B , 92C , 92D of the adjustment support ring 92 during the assembly of the torsion damper 200 fall or deviate from the desired position.

Referring to the 2A to 3 can the adjustment support ring 92 when new (in the condition in which the torsional damper 200 used for the first time) due to the adjustment of the centrifugal force of the adjustment support ring 92 be held in its installation position to avoid the action of centrifugal force and the spring force of the diaphragm spring 60 balance. Referring to the 4th and 5 the pressure decreases after use due to wear of the support ring 90 and / or the plastic deformation of the diaphragm spring 60 from which the diaphragm spring 60 through the flange 40 on the support ring 90 exercises. At this point the adjustment support ring will move 92 under the action of centrifugal force in the direction of the radial outside, so that the spring force of the diaphragm spring 60 remains roughly constant.

In this embodiment there is the adjustment support ring 92 preferably made of flexible materials such as plastic. This allows the ring segments 92A , 92B , 92C , 92D easily bent to conform to the shape of the solid support ring 91 better adjust when the adjustment support ring 92 moved to the radial outside.

It is assumed that the size of the radial extension part 91B of the adjustment support ring 92 and the fixed support ring 91 is designed so that the adjustment support ring 92 does not move to the radial outside due to centrifugal force until it is removed from the fixed support ring 91 solves. When the support ring 90 Is worn out, the distance between the primary mass part may be 20th and the flange 40 by the movement of the adjustment support ring 92 relative to the fixed support ring 91 can be kept almost constant. When the plastic deformation of the diaphragm spring 60 leads to a decrease in the spring force, the axial distance between the primary mass part 20th and the flange 40 by the movement of the adjustment support ring 92 relative to the fixed support ring 91 be increased to the spring force of the diaphragm spring 60 to keep approximately constant. Therefore, the torsional damper 200 In the present embodiment, keep the basic damping constant, so that the service life of the torsional damper 200 is extended.

It goes without saying that the torsional damper 200 in the present embodiment as Dual mass flywheel or dual clutch damper can be used.

The second embodiment

6A and 6B show a torsional damper 300 in the second embodiment according to the present invention, in which, for the sake of simplicity, only the structure around the support ring 90 is shown. The same or like reference numerals are assigned to the same or like parts as in the first embodiment, and the detailed description of these components is omitted.

In this embodiment, the fixed support ring is used 91 supporting the flange 40 in contact with the primary mass part 20th . More precisely, the fixed support ring 91 the following components: an axial extension part 91A that makes contact with the inner circumference of the flange 40 which is roughly along the axial direction A. and the circumferential direction C. of the torsion damper 300 extends; an extension part 91B in the radial direction that with the axial extension part 91A forms a unit and extends approximately along the radial direction R. and the circumferential direction C. extends. The radial extension part 91B is located between the primary mass part 20th and the adjustment support ring 92 . The axial portion of the radial extension part 91B is roughly wedge-shaped. The axial thickness of the radial extension part 91B is shaped to be larger at the position closer to the radially outside. In the axial section of the torsion damper 300 forms an axial side 912 of the radial extension part 91B an oblique line relative to the radial direction R. is inclined.

The adjustment support ring 92 is located between the fixed support ring 91 and the flange 40 . Corresponding to the radial extension part 91B of the fixed support ring 91 is also the axial portion of the adjustment support ring 92 roughly wedge-shaped. The axial thickness of the adjustment support ring 92 is designed so that the closer the thickness is to the radial outside, the smaller. More precisely, it forms the other axial side surface 922 of the adjustment support ring 92 in the axial section of the torsion damper 300 an oblique line relative to the radial direction R. is inclined.

The present embodiment can operate in a similar manner to the first embodiment. Referring to 6B the adjustment support ring may become 92 in the second embodiment move under the action of centrifugal force in the direction of the radial outer side when the component is worn and / or the diaphragm spring 60 is plastically deformed, so that the axial distance between the primary mass part 20th and the flange 40 is maintained or increased to ensure that the spring force of the diaphragm spring 60 remains roughly constant.

In the second embodiment, the axial extension part 91A of the fixed support ring 91 prevent the ring portion of the adjustment support ring 92 (please refer 3 and 5 ) during the assembly of the torsion damper 300 falls down towards the radially inner side. In this embodiment the locking ring is 30th not required to use the adjustment support ring 92 to support and adapt.

• (1) In der ersten Ausführungsform ist der Einstellstützring 92 in vier Ringsegmente 92A, 92B, 92C und 92D aufgeteilt. Die vorliegende Erfindung ist jedoch nicht darauf beschränkt. Beispielsweise kann der Einstellstützring 92 in zwei, drei oder eine andere Anzahl an Ringssegmenten aufgeteilt werden.
• (2) In der ersten Ausführungsform wird das Umfangsteil der Membranfeder 60 durch den Reibungsring 80 elastisch gegen das Kanalabdeckungsteil 70 gedrückt. Die vorliegende Erfindung ist jedoch nicht darauf beschränkt. Beispielsweise kann der Reibungsring 80 weggelassen werden, sodass die Membranfeder 60 direkt und elastisch gegen das Kanalabdeckungsteil 70 gedrückt wird.
• (3) Es ist anzunehmen, dass die axialen Abschnitte des Einstellstützrings 92 und des festen Stützrings 91 nicht auf die in der Figur gezeigte Form beschränkt sind, solange der Einstellstützring 92 sich unter Einwirkung der Zentrifugalkraft unter der Bedingung des Bauteilverschleißes und / oder plastischer Verformung der Membranfeder 60 relativ zum festen Stützring 91 in Richtung der radialen Außenseite bewegen kann und somit die Federkraft der Membranfeder 60 ungefähr konstant bleibt.

The present invention is of course not restricted to the above-mentioned embodiments and those skilled in this field can develop further variants or modifications based on the above-mentioned embodiments according to the present invention, which do not exceed the scope of protection of the present invention.

• (1) In the first embodiment, the adjustment support ring is 92 into four ring segments 92A , 92B , 92C and 92D divided up. However, the present invention is not limited to this. For example, the adjustment support ring 92 be divided into two, three or some other number of ring segments.
• (2) In the first embodiment, the peripheral part becomes the diaphragm spring 60 through the friction ring 80 elastic against the channel cover part 70 pressed. However, the present invention is not limited to this. For example, the friction ring 80 be omitted so that the diaphragm spring 60 directly and elastically against the duct cover part 70 is pressed.
• (3) It is assumed that the axial portions of the adjustment support ring 92 and the fixed support ring 91 are not limited to the shape shown in the figure as long as the adjustment support ring 92 under the action of centrifugal force under the condition of component wear and / or plastic deformation of the diaphragm spring 60 relative to the fixed support ring 91 can move in the direction of the radial outside and thus the spring force of the diaphragm spring 60 remains roughly constant.

List of reference symbols

100, 200, 300

Torsional damper;

10

Spacer;

20th

Primary mass part;

30th

Locking ring;

40

Flange;

50

Secondary mass part;

51

Wedge sleeve;

60

Diaphragm spring;

70

Channel cover part;

80

Friction ring;

90

Support ring;

91

fixed support ring;

91A

axial extension part;

91B

radial extension part;

911

another axial side of the radial extension part;

912

an axial side of the radial extension part;

92

Adjustment support ring;

92A, 92B, 92C, 92D

Ring segments;

921

an axial side of the adjustment support ring;

922

another axial side of the adjustment support ring;

110, 120

Rivets;

A.

axial direction;

R.

radial direction;

C.

Circumferential direction.

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

• CN 107429789 A [0002]
• CN 107076260 A [0002]

Claims (10)

Torsion damper which has a primary mass part, a support ring, a flange, a diaphragm spring, a secondary mass part and a duct cover part, the primary mass part and the duct cover part being fastened to one another on the outer circumference and at least part of the support ring between the primary mass part and the flange in the axial direction of the torsion damper is arranged and the flange, the diaphragm spring and the secondary mass part are attached to each other and the diaphragm spring is located between the flange and the secondary mass part and is elastically pressed against the channel cover part. The support ring comprises an adjustment support ring and a fixed support ring which supports the flange, wherein the axial section of the adjustment support ring is wedge-shaped and when the pressure decreases between the flange and the primary mass part due to the wear and / or the plastic deformation of the diaphragm spring, the adjustment support ring under the action of Centrifugal force relative to the fixed support ring is moved to the radial outside of the torsional damper in order to keep the spring force of the diaphragm spring approximately constant. Torsional damper after Claim 1 , characterized in that the fixed support ring is a ring member having an axial portion in an approximately L-shaped shape, the adjustment support ring having a plurality of arcuate ring segments. Torsional damper after Claim 1 , characterized in that in the axial section of the support ring the contact surface between the fixed support ring and the adjustment support ring forms a straight line with a radial inclination relative to the torsion damper. Torsional damper after Claim 1 , characterized in that the axial thickness of the adjustment support ring is designed so that it is smaller, the closer it is to the radial outer side of the torsional damper. Torsional damper after Claim 1 , characterized in that the fixed support ring has the following components: an axial extension part which extends along the axial and circumferential directions of the torsional damper, and a radial extension part which extends along the axial direction and the peripheral direction of the torsional damper, the axial thickness of the radial extension part, the greater the closer to the radial outside. Torsional damper after Claim 2 , characterized in that the adjustment support ring is arranged between the fixed support ring and the primary mass part, the torsion damper also having a locking ring which is attached to the primary mass part, the locking ring being designed so that it can prevent the ring segments of the adjustment support ring to fall down on the radial inside of the torsional damper. Torsional damper after Claim 2 , characterized in that the adjustment support ring is arranged between the fixed support ring and the flange, the fixed support ring being able to prevent the ring segments of the adjustment support ring from falling down to the radial inside of the torsional damper. Torsional damper according to one of the Claims 1 to 7th , characterized in that the adjustment support ring is made of plastic. Torsional damper according to one of the Claims 1 to 7th , characterized in that the torsional damper also comprises a friction ring, the peripheral part of the diaphragm spring being pressed against the channel cover part by the friction ring. Torsional damper according to one of the Claims 1 to 7th , characterized in that the torsional damper is a dual mass flywheel or a dual clutch damper.

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