CN113137451A - Torsional vibration damper with coil spring for sealing - Google Patents

Torsional vibration damper with coil spring for sealing Download PDF

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Publication number
CN113137451A
CN113137451A CN202110007672.5A CN202110007672A CN113137451A CN 113137451 A CN113137451 A CN 113137451A CN 202110007672 A CN202110007672 A CN 202110007672A CN 113137451 A CN113137451 A CN 113137451A
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CN
China
Prior art keywords
damper
torsional vibration
spring
output
vibration damper
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202110007672.5A
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Chinese (zh)
Inventor
丹尼斯·克内布尔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN113137451A publication Critical patent/CN113137451A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13114—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by modifications for auxiliary purposes, e.g. provision of a timing mark
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/1343—Wound springs characterised by the spring mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F16F15/1343—Wound springs characterised by the spring mounting
    • F16F15/13461—Set of springs, e.g. springs within springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/30—Sealing arrangements

Abstract

The invention relates to a torsional vibration damper (10) having a sealing coil spring for transmitting torque between a drive element and a driven element and for reducing torsional vibrations occurring in a drive train of a vehicle, having a damper input (12) which is rotatable about a rotational axis (D); a damper output (20) which is rotatable about an axis of rotation and is rotatable in a limited manner against the action of a spring element (18) arranged in an interior space (24), the damper input having a damper input element (12.1) which is arranged on the drive side with respect to a reference axial direction (R), the damper output having a damper output element (20.1) which is arranged on the driven side with respect to the damper input element in the axial direction, wherein, in an axial gap (48) formed between the damper output element and the damper input element, at least one first disc spring (46) which seals the interior space and causes an axial force is arranged on the drive side with respect to the damper output element in the axial direction.

Description

Torsional vibration damper with coil spring for sealing
Technical Field
The present invention relates to a torsional vibration damper.
Background
A torsional vibration damper is known, for example, from DE 102017123791 a 1. A torsional vibration damper embodied as a dual-mass flywheel is described, which has a damper input and a damper output, which can be rotated counter to one another against the action of at least one spring element arranged in an interior space that can be filled with grease, wherein the damper output comprises a damper output, which is operatively coupled to a bow spring and is connected to a driven hub via a torque limiter. A diaphragm spring is arranged on the driven disk hub, which diaphragm spring bears against the primary mass cover and forms a first seal of the interior space with respect to the surroundings. The second sealing of the interior space is realized via a friction ring with a sealing flange fixed on the drive side. The second seal together with the first seal seals the interior space from the surroundings.
It has been found that in particular the second seal is not sufficient under certain conditions and in particular water can enter from the outside into the inner space.
Disclosure of Invention
The aim of the invention is to improve the sealing of a torsional vibration damper. In particular, water should be prevented from entering the interior space.
At least one of these objects is achieved by a torsional vibration damper having the features of the invention. This makes it possible to seal the interior more reliably and to prevent lubricant within the interior from leaking and contaminants, in particular water, from entering the interior.
The torsional vibration damper can be arranged in a drive train of the vehicle. The drive element can be an internal combustion engine. The driven element can be a torque transmission device, such as a wet or dry dual clutch, a torque converter, a hybrid module with an electric motor as a further drive element, and/or a transmission. The torsional vibration damper can be embodied as a dual mass flywheel.
The damper input element can have a primary mass. The damper input element can accommodate a starter ring gear on the outer periphery. The damper input element can be connected to the drive element by means of a screw connection.
The spring element can be a compression spring or an arc spring. At least two spring elements can be arranged in the circumferential direction.
The damper housing can at least partially surround the damper input element. A cover plate which is fixedly connected to the damper input element can be assigned to the damper housing. The cover plate can be arranged in the axial direction on the driven side relative to the spring element.
The damper output element can be an arcuate spring flange. A centrifugal pendulum can be arranged on the damper output. The centrifugal pendulum can have at least one pendulum mass which can be moved in a limited manner along the pendulum path on the pendulum mass carrier. The pendulum mass carrier can be connected to the damper output element in a rotationally fixed manner, in particular in one piece.
The first coil spring can bear directly against the damper input element and/or the damper output element.
The diaphragm spring can be arranged in the axial direction on the driven side relative to the output element of the damper in order to further seal the interior space. The diaphragm spring can be rotationally supported in a force-loaded manner on the damper input, in particular on the cover plate.
In a preferred embodiment of the invention, the first coil spring is arranged axially overlapping the screw connection connecting the damper input element and the drive element. The damper input element can be connected to a crankshaft of the internal combustion engine via a screw connection.
In a special embodiment of the invention, the first coil spring bears against a component assigned to the input of the vibration damper in the first bearing region. The component can be a damper input element, a component fixedly connected to the damper input element, for example a hub, a friction ring connected to the damper input element or to the hub, or a centering disk connected to the damper input element. The component can be fixedly connected to the damper input element via a screw connection.
The first coil spring can be centered radially at the member. The friction ring can be centered radially on the damper input element or on a component fixedly connected thereto, in particular on the centering disk.
In a further special embodiment of the invention, the maximum diameter of the first contact area is smaller than the central diameter located radially midway between the, in particular, largest outer circumference of the damper output element and the, in particular, smallest inner circumference, or the axis of rotation, of the damper output element. This reduces the frictional energy generated by the relative rotation between the damper input and the damper output.
In a special embodiment of the invention, the first cup spring bears in the second bearing region against a component assigned to the output of the vibration damper. The component can be a damper output element, a component fixedly connected to the damper output element, for example a disk hub, or a friction ring connected to the damper output element or to the disk hub.
The first coil spring can be centered radially at the member. The friction ring can be centered radially on the damper output element, in particular on the inner circumference of the damper output element or on a component fixedly connected thereto.
The centering of the friction ring can be located radially inside or outside the first contact area and/or the second contact area.
In a preferred embodiment of the invention, a second disc spring is arranged in the axial gap. The second coil spring can act in series with the first coil spring in terms of axial force between the damper input and the damper output.
In a special embodiment of the invention, the first and second spiral springs are arranged axially side by side and radially overlapping. The second coil spring can be arranged mirror-inverted with respect to the first coil spring.
In another special embodiment of the invention, an intermediate element is arranged axially between the first and the second coil spring. The intermediate element can be centered radially on a component associated with the damper input or the damper output. The intermediate element can be supported radially on the inner circumference of the damper output element. The intermediate element can be centered radially at the centering disc. The mid-section can be located radially inward of an inner periphery of the damper output element. The intermediate element can be made of steel and/or plastic.
In a special embodiment of the invention, the first coil spring bears directly against a first side at the intermediate element and the second coil spring bears directly against an opposite second side at the intermediate element. The respective contact areas of the first and second spiral springs on the intermediate element can be located at the same radial level.
In a preferred embodiment of the invention, the first coil spring has an outer and/or inner circumference running continuously in the circumferential direction. Whereby the sealing function of the coil spring can be achieved. The first contact area can contact the inner or outer circumference of the first spiral spring and the second contact area can contact the outer or inner circumference of the first spiral spring.
Further advantages and advantageous embodiments of the invention result from the description of the figures and the drawing.
Drawings
The present invention is described in detail below with reference to the accompanying drawings. In which are shown in detail:
fig. 1 shows a half-sectional view of a torsional vibration damper in a special embodiment of the invention.
Fig. 1a shows an enlarged view of detail a in fig. 1.
Fig. 2 shows a half-sectional view of a torsional vibration damper in a special embodiment of the invention.
Fig. 2a shows an enlarged view of the detail a in fig. 2.
Fig. 3 shows a half-sectional view of a torsional vibration damper in a special embodiment of the invention.
Fig. 3a shows an enlarged view of the detail a in fig. 3.
Fig. 4 shows an enlarged view of an alternative embodiment of detail a in fig. 3.
Fig. 5 shows a half-sectional view of a torsional vibration damper in a special embodiment of the invention.
Fig. 5a shows an enlarged view of the detail a in fig. 5.
Fig. 6 shows an enlarged view of an alternative embodiment of detail a in fig. 5.
Detailed Description
Fig. 1 shows a half-sectional view of a torsional vibration damper 10 according to a special embodiment of the invention. Torsional vibration dampers are used in the drive train of a vehicle for transmitting torque between a driving element, for example an internal combustion engine, and a driven element, for example a transmission, and for reducing torsional vibrations in the drive train.
The torsional vibration damper 10 is preferably embodied as a dual mass flywheel and comprises a damper input 12 which is rotatable about the axis of rotation D and has a damper input element 12.1 arranged on the drive side. The damper input element 12.1 comprises a primary mass and is releasably connected to the crankshaft of the internal combustion engine via a screw connection 14. The damper input element 12.1 is welded radially on the outside to a cover plate 12.2 assigned to the damper input. A starter ring gear 16 is fixed to the outer circumference of the damper input element 12.1.
The damper input element 12.1 is torsionally fixed against the action of the spring element 18 relative to the damper output 20, which is rotatable about the axis of rotation D. The damper input element 12.1 is directly coupled to the spring element 18. The damper output 20 has a damper output element 20.1 which is arranged axially offset from the damper input element 12.1 on the output side. A plurality of spring elements 18 can be arranged spaced apart from one another in the circumferential direction. The individual spring elements 18 are preferably embodied as arcuate springs and are arranged in an interior space 24 which is spanned by the damper housing 22. The interior space 24 can be at least partially filled with a lubricant, for example with grease. The spring element 18 is supported radially on the outside via a sliding cover 26 on an axially extending section of the damper input element 12.1.
The damper output element 20.1 is preferably embodied as a curved spring flange and is coupled directly to the spring element 18. A centrifugal pendulum 28 having a pendulum mass 32, which can be moved along a pendulum path in a limited manner relative to a pendulum mass carrier 30, is arranged on the damper output 20. The pendulum mass carrier 30 is embodied in one piece with the damper output element 20.1.
The damper output element 20.1 is connected in a rotationally fixed manner to a secondary mass 34 arranged outside the interior 24 and to a driven disk hub 36. A diaphragm spring 38 arranged on the output side of the damper output element 20.1 is fastened between the damper output element 20.1 and the driven hub 36, said diaphragm spring bearing rotatably and with force on a friction ring 40 arranged on the cover plate 12.2. The inner space 24 is partially sealed via a diaphragm spring 38.
A further friction ring 44 is accommodated radially centrally on the inner periphery 42 of the damper output element 20.1. The first coil spring 46 is arranged in the axial direction R on the drive side relative to the damper output element 20.1 and in an axial gap 48 formed directly between the damper output element 20.1 and the damper input element 12.1. Thereby preventing water from entering the interior space 24. It is also possible to prevent the lubricant from leaking from the internal space 24.
The first coil spring 46 is arranged radially outside the screw connection 14 and axially overlapping the screw connection 14. In this case, the first coil spring 46 is located radially within the spring element 18 and within the contact region between the diaphragm spring 38 and the cover plate 12.2.
Fig. 1a shows an enlarged illustration of detail a from fig. 1. The first coil spring 46 bears directly against the damper input element 12.1 via the first bearing region 50. The first spiral spring 46 bears directly against the friction ring 44 in the second bearing region 52. The first contact area 50 is located radially inside the second contact area 52. Via the first contact region 50 and the second contact region 52, the first coil spring 46 generates an axial force between the damper input element 12.1 and the damper output element 20.1 via the friction ring 44 and thus effects a reliable sealing of the interior 24.
The first coil spring 46 is centered radially via an axial projection 54 of the friction ring 44. The friction ring 44 is accommodated radially centrally on the inner periphery 42 of the damper output element 20.1.
Fig. 2 shows a half-sectional view of a torsional vibration damper 10 according to a special embodiment of the invention. The torsional vibration damper 10 corresponds to the torsional vibration damper depicted in fig. 1, except for the differences described below. The friction ring 44, which bears directly against the damper input element 12.1 and is centered radially via a centering disk 56 riveted to the damper input element 12.1, has an axial section 58, on which the first coil spring 46 is accommodated centered radially.
In fig. 2a an enlargement of the detail a in fig. 2 is depicted. The first coil spring 46 bears directly against the friction ring 44 via a first bearing region 50 and directly against the damper output element 20.1 via a second bearing region 52. The first contact area 50 is located radially outside the second contact area 52.
Fig. 3 shows a half sectional view of a special embodiment of the torsional vibration damper 10 according to the invention. The damper input element 12.1 is connected to a hub 60 which is arranged on the output side in the axial direction R relative to the damper input element 12.1. Hub 60 accommodates a support bearing 64 on axial section 62, via which damper output 20 is centered at damper input 12.
An enlarged view of detail a in fig. 3 is drawn in fig. 3 a. The first coil spring 46 directly bears against a hub 60 associated with the damper input 12 via the first bearing region 50. The first spiral spring 46 bears directly against the friction ring 44, which is associated with the damper output 20 and is accommodated radially centrally on the inner periphery 42 of the damper output element 20.1, via the second bearing region 52.
An enlarged view of an alternative embodiment of detail a in fig. 3 is depicted in fig. 4. The friction ring 44 is accommodated radially centrally on a hub 60 associated with the damper input 12. A first contact region 50 is formed between the friction ring 44 and the first coil spring 46 and a second contact region 52 is formed between the first coil spring 46 and the damper output element 20.1. The first contact area 50 is located radially inside the second contact area 52.
Fig. 5 shows a half-sectional view of a torsional vibration damper 10 according to a special embodiment of the invention. The torsional vibration damper 10 corresponds to the torsional vibration damper depicted in fig. 1, except for the differences described below. The first coil spring 46 is arranged directly between the damper input element 12.1 and the intermediate element 66. A second disc spring 68 is arranged directly between the intermediate member 66 and the damper output member 20.1. The first coil spring 46 and the second coil spring 68 radially overlap each other. An intermediate member 66 is mounted axially directly between the first and second coil springs 46, 68.
The intermediate element 66 is received radially centrally on the centering disc 56 radially within the first and second coil springs 46, 68. The centering disk 56 is associated with the damper input 12 and is directly fixedly connected to the damper input element 12.1 via the screw connection 14.
An enlarged view of detail a in figure 5 is drawn in figure 5 a. The first coil spring 46 bears directly against the damper input element 12.1 via the first bearing region 50 and directly against the intermediate element 66 via the second bearing region 52. The maximum diameter of the first contact region 50 and the second contact region 52 is smaller than the central diameter located radially midway between the outer circumference and the inner circumference 42 of the damper output element 20.1.
The first coil spring 46 bears directly with a loading force against the intermediate element 66 on a first side and the second coil spring 68 bears directly with a loading force against the intermediate element 66 on a second, opposite side. The first and second coil springs 46, 68 have, in particular, an outer and/or inner periphery running continuously in the circumferential direction.
Fig. 6 shows an enlarged view of a further alternative embodiment of detail a in fig. 5. The intermediate element 66 is radially centered at the inner periphery 42 of the damper output element 20.1.
List of reference numerals
10 torsional vibration damper
12 damper input
12.1 damper input element
12.2 cover plate
14 screw connector
16 starting ring gear
18 spring element
20 damper output
20.1 damper output element
22 shock absorber housing
24 inner space
26 sliding cover
28 centrifugal pendulum
30 pendulum mass support
32 pendulum mass
34 secondary mass
36 driven disk hub
38 diaphragm spring
40 Friction ring
42 inner circumference of
44 friction ring
46 first coil spring
48 axial clearance
50 first contact area
52 second abutment area
54 projection
56 centering disc
Segment 58
60 hub
Section 62
64 support bearing
66 intermediate element
68 second coil spring
D axis of rotation
R axial direction

Claims (10)

1. A torsional vibration damper (10) for transmitting torque between a driving element and a driven element and for reducing torsional vibrations occurring in a drive train of a vehicle, having:
a damper input (12) which can be rotated about an axis of rotation (D) and which has a damper input element (12.1) which is arranged on the drive side with reference to an axial direction (R),
a damper output (20) which is rotatable about the axis of rotation (D) and which is rotatable in a limited manner relative to the damper input (12) against the action of at least one spring element (18) arranged in an interior (24) supported by a damper housing (22), said damper output having a damper output element (20.1) which is arranged on the output side relative to the damper input element (12.1) in the axial direction (R),
it is characterized in that the preparation method is characterized in that,
in an axial gap (48) formed between the damper output element (20.1) and the damper input element (12.1), at least one first disc spring (46) which seals the interior space (24) and causes an axial force is arranged on the drive side relative to the damper output element (20.1) in the axial direction (R).
2. Torsional vibration damper (10) as claimed in claim 1, characterized in that the first disc spring (46) is arranged axially overlapping with a screw connection (14) connecting the damper input element (12.1) and the drive element.
3. The torsional vibration damper (10) as claimed in claim 1 or 2, characterized in that the first cup spring (46) bears in a first bearing region (50) against a component (12.1, 44) assigned to the damper input (12).
4. A torsional vibration damper (10) as set forth in claim 3 wherein said first abutment region (50) has a maximum diameter that is smaller than a central diameter located radially midway between the outer and inner peripheries (42) of said damper output member (20.1).
5. The torsional vibration damper (10) as claimed in claim 3 or 4, characterized in that the first cup spring (46) bears in a second bearing region (52) against a component (20.1, 44) assigned to the damper output (12).
6. Torsional vibration damper (10) as claimed in any of the preceding claims, characterized in that a second disc spring (68) is arranged in the axial gap (48).
7. Torsional vibration damper (10) as claimed in claim 6, characterized in that the first coil spring (46) and the second coil spring (68) are arranged axially side by side and radially overlapping.
8. Torsional vibration damper (10) as claimed in claim 6 or 7, characterized in that an intermediate element (66) is arranged axially between the first and second disc springs (46, 68).
9. Torsional vibration damper (10) as set forth in claim 8, characterized in that the first coil spring (46) directly abuts on a first side at the intermediate element (66) and the second coil spring (68) directly abuts on an opposite second side at the intermediate element (66).
10. Torsional vibration damper (10) as claimed in any of the preceding claims, characterized in that the first disc spring (46) has a continuously extending outer and/or inner circumference in the circumferential direction.
CN202110007672.5A 2020-01-20 2021-01-05 Torsional vibration damper with coil spring for sealing Pending CN113137451A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020101131.8 2020-01-20
DE102020101131 2020-01-20

Publications (1)

Publication Number Publication Date
CN113137451A true CN113137451A (en) 2021-07-20

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Application Number Title Priority Date Filing Date
CN202110007672.5A Pending CN113137451A (en) 2020-01-20 2021-01-05 Torsional vibration damper with coil spring for sealing

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CN (1) CN113137451A (en)
DE (1) DE102020129530A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021122815B3 (en) 2021-09-03 2023-02-09 Schaeffler Technologies AG & Co. KG clutch assembly
DE102022108784A1 (en) 2022-04-11 2023-10-12 Schaeffler Technologies AG & Co. KG Torsional vibration damper with a friction element

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017123791A1 (en) 2017-10-12 2019-04-18 Schaeffler Technologies AG & Co. KG Dual mass flywheel for double clutch

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