CN116518025A - Torsional vibration damper and method for manufacturing the same - Google Patents

Torsional vibration damper and method for manufacturing the same Download PDF

Info

Publication number
CN116518025A
CN116518025A CN202211726420.9A CN202211726420A CN116518025A CN 116518025 A CN116518025 A CN 116518025A CN 202211726420 A CN202211726420 A CN 202211726420A CN 116518025 A CN116518025 A CN 116518025A
Authority
CN
China
Prior art keywords
cover part
disk
torsional vibration
vibration damper
friction ring
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
CN202211726420.9A
Other languages
Chinese (zh)
Inventor
若尔特·伊斯特万·纳吉
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 CN116518025A publication Critical patent/CN116518025A/en
Pending legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F16F15/129—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 characterised by friction-damping means
    • F16F15/1292—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 characterised by friction-damping means characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
    • 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
    • F16F15/13121—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 clutch arrangements, e.g. for activation; integrated with clutch members, e.g. pressure member
    • 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
    • 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
    • F16F15/30—Flywheels
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

The invention relates to a torsional vibration damper and to a method for producing the same, comprising: an input member rotatably provided around a rotation axis; and an output part which can rotate relative to the input part about a rotational axis against the action of the spring device, wherein the input part comprises a radially inwardly open annular chamber which accommodates the spring device and is formed by a disk part which can be connected to a crankshaft of the internal combustion engine and a cover part which is connected to the disk part in a radially outer sealing manner, wherein the annular chamber is sealed when a friction device is formed between a disk spring diaphragm accommodated on the output side and a friction ring which is axially preloaded by the disk spring diaphragm relative to the cover part. In order to simplify handling during the production of a torsional vibration damper, the friction ring is accommodated rotatably relative to the disk spring diaphragm and the cover part and is accommodated in a loss-proof manner on the cover part.

Description

Torsional vibration damper and method for manufacturing the same
Technical Field
The invention relates to a torsional vibration damper and to a method for producing the same, comprising: an input member rotatably provided around a rotation axis; and an output part which can be rotated relative to the input part about a rotational axis against the action of the spring device, wherein the input part comprises a radially inwardly open annular chamber which accommodates the spring device and is formed by a disk part which can be connected to a crankshaft of the internal combustion engine and a cover part which is connected to the disk part in a radially outer sealing manner, wherein the annular chamber is sealed off in the case of a friction device formed between a disk spring diaphragm accommodated on the output side and a friction ring which is preloaded by the disk spring diaphragm axially against the cover part.
Background
For example, publications DE 10 2020 116 058 A1 and WO14/037001A1 show torsional vibration dampers having an input part with a radially inwardly open annular chamber formed by a disk part connectable to a crankshaft of an internal combustion engine and a cover part sealingly connected to the disk part radially outside, in which annular chamber a spring device is arranged. The output member is arranged in a limited rotatable manner relative to the input member against the action of the spring means. In order to seal the annular chamber outwards and to form a friction device for setting a basic friction in the case of rotation between the input part and the output part, a friction ring is provided, which is preloaded against the cover part by a belleville diaphragm fixedly connected to the output part. During the production and installation of torsional vibration dampers, in which the spring device and the output element are inserted into a flat disk element and then the cover element is centered on the disk element with the interposition of a friction ring under pretensioning of the disk spring diaphragm and then sealingly connected, the cover element must be fastened to the cover element by means of corresponding handling means in order to ensure precise positioning during the abutment of the cover element against the disk element. Furthermore, it is difficult in some applications to accommodate the friction ring in a rotationally fixed manner, for example by means of locking hooks or the like which engage through openings, and the friction ring must remain rotatable relative to the cover part when the torsional vibration damper is in use.
Disclosure of Invention
It is an object of the present invention to improve such a torsional vibration damper and a method for producing such a torsional vibration damper. In particular, the object of the invention is to provide a torsional vibration damper and a method for producing a torsional vibration damper which can be produced in a simple manner despite the friction ring being rotatably arranged relative to the cover part.
The object is achieved by the subject matter of embodiments of the present invention. Advantageous embodiments of the invention are described hereinafter.
The proposed torsional vibration damper is used for torsional vibration isolation in a powertrain, for example in a hybrid powertrain of an internal combustion engine with torsional vibration, in particular of an internal combustion engine with three cylinders. The torsional vibration damper may be provided as a dual mass flywheel having a primary flywheel mass and a secondary flywheel mass, for example with a clutch plate accommodated or receivable at the secondary flywheel mass for forming a friction clutch, or as a torsional vibration damper having a dual mass flywheel effect, wherein at least a part of the secondary flywheel mass is provided in a subsequent drive train arrangement, for example in a rotor of an electric machine, a double clutch or the like.
The torsional vibration damper includes: an input element which is arranged rotatably about a rotational axis, for example a crankshaft axis of an internal combustion engine; and an output member which is relatively rotatable with respect to the input member about an axis of rotation against the action of the spring means.
The input element forms an annular chamber which is open at the radial inner side and accommodates the spring device by means of a disk element which can be connected to a crankshaft of the internal combustion engine and a cover element which is connected to the disk element in a sealing manner at the radial outer side. Between the input and output parts, friction means are provided which are effective when the input and output parts are rotated relative to each other, said friction means additionally acting in said region as an effective seal of the annular chamber outwards between the input and output parts. In order to form the friction device, a disk spring diaphragm fastened to the output part and closing the face between the output part and the cover part is axially preloaded against the cover part, wherein a friction ring is arranged axially between the disk spring diaphragm and the cover part.
The spring arrangement may comprise helical compression springs or spring packs with mutually nested helical compression springs distributed over the circumference and arranged in the circumferential direction. The helical compression springs or spring groups can be arranged in a preferred manner on a single diameter or on a plurality of diameters. The spring device can have a multi-stage characteristic curve by means of helical compression springs which are actuated differently by the angle of rotation. The helical compression spring may be embodied as a short, linear helical compression spring or, in a preferred manner, as a curved spring which is pre-curved in its use diameter. The end faces of the helical compression springs are acted upon on the input side and on the output side, respectively. For this purpose, axially paired or pressed contact means can be provided on the disk part and the cover part, which contact means are axially connected between circumferentially adjacent end sides of the helical compression spring and which contact the input part and the output part in the circumferential direction during a relative rotation. Preferably, a flange limb which engages from the radially inner side between the circumferentially adjacent end sides of the helical compression spring is provided on the output side, said flange limb expanding radially, for example, at the flange part on the output side.
The torsional vibration damper can be constructed essentially in two embodiments. In a first embodiment, the input member forms a primary flywheel mass and the output member forms a secondary flywheel mass. The input and output components are rotatably supported on each other, for example by means of ball bearings, for example deep groove ball bearings or radial thrust ball bearings or plain bearings. For this purpose, the disk element can be formed in one piece as an axial extension for accommodating the secondary flywheel mass, or the bearing dome connected to the disk element can be formed as an axial extension for accommodating the secondary flywheel mass. Furthermore, the secondary flywheel mass is supported axially relative to the input part such that the axial force of the belleville spring diaphragm, which is generated by the pretensioning relative to the cover part, is supported on the bearing between the input part and the output part. The housing of the belleville spring diaphragm at the output part is realized, for example, at a rivet connection between the secondary flywheel mass and a flange part of the output-side spring-loaded device. The secondary flywheel mass serves as a counter plate for the friction clutch, wherein the clutch plate is arranged on the secondary flywheel mass in a mounted or mountable manner, and the friction linings of the clutch disk are arranged in an axially preloaded or preloaded manner between the friction surfaces of the counter plate and the pressure plate of the clutch pressure plate.
In an alternative embodiment, the output component has an output hub, by means of which the torque to be derived is transmitted directly to the transmission input shaft of the transmission, to the shaft section of the rotor, to the rotor of the electric machine or to a drive train arrangement arranged therebetween, for example a double clutch, a hydrodynamic torque converter or the like. The input member may have a primary flywheel mass and the secondary flywheel mass of the torsional vibration damper may be at least partially disposed on the powertrain member downstream of the output hub. The axial force of the disk spring diaphragm is supported by means of a support ring arranged between the disk element and the output element. Furthermore, the support ring can seal the annular chamber on the side opposite the friction means. The disk spring diaphragm can be arranged, for example, at a rivet connection between the output hub and a flange part for loading the spring device on the output side. The support ring may be arranged between the flange part and the disk part of the input part, for example directly radially outside a fastening opening for accommodating the torsional vibration damper on the crankshaft.
The at least one centrifugal force pendulum can be integrated in particular on the output side into a torsional vibration damper. For example, the centrifugal force pendulum may be accommodated radially in the spring device into the annular chamber. Alternatively or additionally, the centrifugal pendulum may be provided outside the annular chamber, for example with pendulum masses which are axially adjacent and arranged at the radial level of the spring device or which are arranged axially intersecting one another and which are arranged in the spring device or radially intersecting the spring device. Furthermore, a torque limiting device can be provided radially in the spring device, for example, between the spring device and the torque-conducting component in the annular space or outside the annular space, said torque limiting device forming a frictional engagement up to a predetermined limit torque and sliding when the limit torque is exceeded.
In order to make it possible to adapt the friction ring to the operation in a drive train, for example a drive train with a specifically required internal combustion engine with three cylinders, and still be able to be installed simply, the friction ring is accommodated rotatably relative to the disk spring diaphragm and the cover part and is accommodated in a loss-proof manner at the cover part. This means in particular that, at least during the installation of the torsional vibration damper, the friction ring is accommodated in a loss-proof manner at the cover part before the friction ring is preloaded against the cover part, and the subassembly is thereby installed between the cover part and the friction ring without additional access to the friction ring, i.e. the subassembly is placed onto the disk part with the spring device and the output part inserted, the disk spring diaphragm is preloaded and the cover part can be connected, for example welded, in a sealing manner with the disk part. After the torsional vibration damper has been completed and in particular during operation of the torsional vibration damper, the friction ring can be rotated relative to the disk spring diaphragm and the cover part under the pretension of the disk spring diaphragm.
In order to accommodate the friction ring in a loss-proof and rotatable manner on the cover part, the friction ring can be hooked in an axially active manner with the cover part. The friction ring can, for example, have hooks at its inner circumference, which are oriented axially toward the cover part and open radially outwards, in a circumferentially distributed manner. The hooks surround and engage the inner circumference of the cover member from behind. In the case of a sufficiently elastic hook, which is preferably produced from plastic and is injected by means of a mold, the hook can be locked, i.e. clamped, for example, with the inner circumference of the cover part under elastic deformation. In the case of friction rings, in particular made of reinforced plastics, the cover part can have recesses for the hooks at its inner circumference, at least in number and in the orientation distributed in the circumferential direction. In this case, the hooks coincide in the circumferential direction with the recesses of the cover part, the hooks are inserted through the recesses, and the friction ring and the cover part are rotated relative to one another about the axis of rotation, so that the recesses and the hooks rotate relative to one another. Thereby, the hooks bite into the cover part and the friction ring is accommodated at the cover part in a loss-proof manner.
The proposed method involves the production or installation of a proposed torsional vibration damper having an input part and an output part which can be rotated relative to the input part against the action of a spring device, wherein a radially inwardly open annular chamber formed by a disk part and a cover part is formed for receiving the spring device. The disk part and the cover part are sealingly connected, in particular welded, to each other. In order to simplify handling of the cover part during the joining process on the disk part, a subassembly is formed from the cover part and a friction ring which is accommodated in a loss-proof and rotatable manner at the cover part. After the insertion of the spring device and the flange part of the output part, which is acted upon on the output side by the spring device, the cover part is placed under axial pretension of the friction ring by means of the disk spring diaphragm fastened to the output part and is connected, for example welded, to the disk part. The secondary flywheel mass or the output hub is then riveted to one another by means of a rivet connection, such as a primary rivet connection and possibly other components, for example a pendulum mass carrier of a centrifugal pendulum, at least one additional mass ring and/or the like, and a belleville disk diaphragm, according to an embodiment of the torsional vibration damper.
For example, it is advantageous if at the friction ring, which is preferably produced from plastic by means of an injection molding method, hooks are provided at its inner circumference, which are oriented axially toward the cover part and open radially outwards, preferably produced with a mold, in a distributed manner over the circumference.
In order to simplify the fastening of the friction ring by means of hooks, in particular in the case of torsionally stiff friction rings, recesses for the hooks can be provided at the cover part at least in number and in the orientation in the circumferential direction at its inner circumference. To form the subassembly, the hooks are guided through the recesses and then the friction ring is rotated relative to the cover part in the circumferential direction between two adjacent recesses in the circumferential direction.
Drawings
The invention is explained in detail with reference to the embodiments shown in fig. 1 to 3. The figures show:
figure 1 shows a cross section of an upper part of a torsional vibration damper arranged in a rotatable manner about an axis of rotation,
FIG. 2 shows a subassembly formed from the cover member and friction ring of FIG. 1 prior to installation of the subassembly, an
Fig. 3 shows a detail of the friction ring of fig. 1 and 2 in the region of the hook in a 3D view.
Detailed Description
[21] Fig. 1 shows a section through an upper part of a torsional vibration damper 1, which is arranged about a rotational axis d and is embodied as a dual mass flywheel, having: an input member 2 forming a primary flywheel mass; and an output member 3 which is arranged in a limited rotatable manner relative to the input member 2 about an axis of rotation d against the action of the spring means 4, said output member having a secondary flywheel mass 5.
[22] The inlet part 2 comprises a disk part 6 forming a radially inwardly open annular chamber 8 and a cover part 7 which is sealingly connected to the disk part at the radially outer part, in this case welded. Furthermore, a starter ring gear 9 is accommodated on the shoulder of the disk element.
[23] In the exemplary embodiment shown, the secondary flywheel mass 5 forms a counter plate for the friction clutch and is rotatably supported on the bearing dome 10 of the disk element by means of a bearing device, such as a sliding bearing 11. The flange part 13 and the belleville spring diaphragm 14 are fixedly connected to the secondary flywheel mass 5 by means of the rivet connection 12.
[24] The spring device 4 comprises circumferentially distributed and circumferentially arranged helical compression springs 15, 16, which here form a spring stack in a nested manner and are designed as arcuate springs that are pre-bent in their use diameter. The end sides of the helical compression springs 15, 16 are effectively loaded in the circumferential direction on the input side and the output side, respectively. For this purpose, as is not visible in the illustrated sectional view, presses are provided at the input side at the disk part 6 and the cover part 7, which presses engage between the end sides of the helical compression springs 15, 16, respectively, which are adjacent in the circumferential direction. Also not visible, the flange part 13 has radially expanded flange limbs on the output side, which are each engaged radially inwardly between adjacent end sides of the helical compression springs in the circumferential direction and which, in the event of a relative rotation between the input part 2 and the output part 3, project axially between the presses of the disk part 6 and the cover part 7. The helical compression springs are guided and centered axially and radially by means of further presses 17 arranged in the cover part 7 in a circumferentially distributed manner.
[25] Between the input member 2 and the output member 3 friction means 18 are provided for providing a basic friction against the spring action of the spring means 4 upon relative rotation of said input member and said output member. For this purpose, the friction ring 19 is accommodated in a loss-proof and rotatable manner on the cover part 7 and is axially preloaded relative to the cover part 7 by means of the belleville spring diaphragm 14. The axial force of the belleville spring diaphragm 14 is supported on the disk member 6 by means of a support ring 20.
[26] The friction ring 19 has, at its inner circumference, hooks 21 which are radially expanded toward the cover part 7 and open radially outward, which surround and grip the inner circumference of the cover part 7. The hooks 21 penetrate the cover part 7 at a recess at the inner circumference of the cover part 7, which recess is not visible in the sectional view, and rotate relative to the recess, so that the friction ring 19 is rotatably arranged between the cover part 7 and the disk spring diaphragm 14 under axial pretensioning of the disk spring diaphragm 14 when the torsional vibration damper 1 is in use. The anti-lost accommodation of the friction ring 19 at the cover part 7 by means of the hooks 21 is only important during the assembly of the torsional vibration damper 1.
[27] The method of how the torsional vibration damper 1 is assembled is here realized as follows:
[28] the helical compression springs 15, 16, the wear protection shell 22, the flange part 13 and the disk spring diaphragm 14 are inserted into the disk part 6 lying on the rear side with the upwardly open shell, and if necessary a grease for lubrication is fed to the annular chamber 8 with the spring device 4.
[29] The cover part 7 is accommodated by means of the hooks 21 at the cover part 7 in a loss-proof manner in such a way that: the hooks 21 are inserted through the recesses at the inner circumference 23 of the cover part 7 and then the friction ring 19, as shown, is rotated into a position between two adjacent recesses of the hooks 21 in the circumferential direction. Thereby, in the use of the torsional vibration damper 1, the assembly formed by the cover part 7 and the friction ring 19 can be handled and joined to the disk part 6 in a loss-proof manner and without further auxiliary means, despite the subsequent rotatability of the friction ring 19 relative to the cover part 7.
[30] The secondary flywheel mass 5 is centered axially on the bearing dome 10 relative to the support ring 20 and the activation ring 24 and is riveted to the flange part 13 and the belleville spring diaphragm 14 via the through-openings 26 by means of rivets 25 of the riveting device 12. The through opening 26 is closed by means of a sealing cap 27.
[31] The disk part 6 and the cover part 7 are connected to one another in a sealing manner by means of a circumferential weld 36.
[32] Fig. 2 shows, in a 3D view, an unengaged subassembly 28 of the cover part 7 and the friction ring 19, which subassembly is arranged about the axis of rotation D, with reference to fig. 1. The cover part 7 has a pressing 29 for the input side of the two-part helical compression springs 15, 16 and a pressing 17 for axial and radial support and centering. At the inner circumference 23, an axially tapering friction surface region 30 is provided. In the friction surface region 30, a plurality of recesses 31, here six recesses, are provided on the inner circumference 23, which recesses are distributed over the circumference.
[33] The friction ring 19 has a circumferential friction surface 32 facing and frictionally engaging the friction surface area 30. On the side facing away from the friction surface, a circumferential engagement region 33 is provided, which serves to axially act on the friction surface 32 of the friction ring 19 with respect to the friction surface region 30 of the cover part 7 by means of the disk spring diaphragm 14. Here, two hooks 21 are provided diametrically opposite one another on the inner circumference 34 of the friction ring 19. For engaging the friction ring 19 on the cover part 7 for forming the sub-assembly 28, the hooks 21 are inserted through two diametrically arranged recesses 31. Subsequently, the friction ring 19 and the cover part 7 are rotated relative to one another, so that the hooks 21 are each arranged between two circumferentially adjacent recesses 31 in the circumferential direction, so that the friction ring 19 and the cover part 7 are connected to one another in a loss-proof manner and in a rotatable manner during a subsequent operation of the torsional vibration damper 1. In order to avoid random relative rotation, a small friction can be provided between the hooks 21 and the friction surface area 30.
[34] Fig. 3 shows detail a of fig. 2 in a 3D view with reference to fig. 2. The hooks 21 of the friction ring 19 are shown extending axially towards the cover part 7 at the inner circumference 34 of the friction ring and open radially outwards. The hooks 21 are arranged in one piece and produced with a mold at the friction ring 19 produced from plastic by means of an injection molding method or in 3D printing. The radially outwardly directed fingers 35 of the hooks 21 are formed on the side facing away from the friction surface 32 with rounded corners, chamfers or the like for better insertion into the selected recess 31. The distance a between the inner side of the fingers 35 and the friction surface 32 corresponds substantially to the thickness of the friction surface region 30 of the cover part 7, so that the fingers 35 are not subjected to high axial tensioning forces on the one hand and on the other hand the rotatability of the friction ring 19 on the cover part 7 is inhibited by means of corresponding friction.
List of reference numerals
1. Torsional vibration damper
2. Input member
3. Output part
4. Spring device
5. Secondary flywheel mass
6. Disk member
7. Cover member
8. Annular chamber
9. Starting gear ring
10. Bearing dome
11. Sliding bearing
12. Riveting device
13. Flange part
14. Belleville spring diaphragm
15. Spiral pressure spring
16. Spiral pressure spring
17. Press section
18. Friction device
19. Friction ring
20. Support ring
21. Hook
22. Wear protective housing
23. Inner circumference
24. Start ring
25. Rivet
26. Through openings
27. Sealing cover
28. Sub-assembly
29. Press section
30. Friction surface area
31. Blank part
32. Friction surface
33. Junction region
34. Inner circumference
35. Finger element
36. Weld joint
Details A
a spacing
d axis of rotation

Claims (10)

1. A torsional vibration damper (1), the torsional vibration damper having: an input member (2) rotatably provided around a rotation axis (d); and an output part (3) which can be rotated relative to the input part (2) about the rotational axis (d) against the action of the spring device (4), wherein the input part (2) comprises a radially inner annular chamber (8) which is open and accommodates the spring device (4) and is formed by a disk part (6) which can be connected to a crankshaft of the internal combustion engine and a cover part (7) which is connected to the disk part in a radially outer sealing manner, wherein the annular chamber is sealed when friction means (18) are formed between a disk spring diaphragm (14) accommodated on the output side and a friction ring (19) which is preloaded by the disk spring diaphragm axially against the cover part (7), characterized in that the friction ring (19) is accommodated rotatably relative to the disk spring diaphragm (14) and the cover part (7) and is accommodated in a loss-proof manner at the cover part (7).
2. Torsional vibration damper (1) according to claim 1, characterized in that the friction ring (19) is hooked with the cover part (7) in an axially active manner.
3. Torsional vibration damper (1) according to claim 2, characterized in that the friction ring (19) has, at its inner circumference (34), in a circumferentially distributed manner, hooks (21) which are oriented axially towards the cover part (7) and open radially outwards, which hooks surround the inner circumference (23) of the cover part (7).
4. A torsional vibration damper (1) as claimed in claim 3, characterized in that the cover part (7) has at its inner circumference (34) a recess (31) for the hooks (21) at least in number and in circumferential orientation.
5. Torsional vibration damper (1) according to one of claims 1 to 4, characterized in that the input part (2) and the output part (3) are rotatably supported on each other and the axial force of the belleville spring diaphragm (14) is supported on a bearing.
6. A torsional vibration damper according to any of claims 1 to 4, characterized in that the output part has an output hub and the axial force of the belleville spring diaphragm is supported by means of a support ring arranged between the disk part and the output part.
7. Method for producing a torsional vibration damper (1) according to one of claims 1 to 6, having an input part (2) and an output part (3) which can be rotated relative to the input part against the action of a spring device (4), wherein an annular chamber (8) which is open radially inwards is formed by the disk part (6) and the cover part (7) by means of a sealing connection, in particular welding, of the disk part (6) and the cover part (7) for accommodating the spring device (4), characterized in that a subassembly (28) is formed by the cover part (7) and a friction ring (19) which is accommodated in a loss-proof and rotatable manner at the cover part (7), and that after insertion of the spring device (4) and a flange part (13) of the output part (3) of the spring device (4) on the output side, the cover part (7) is axially preloaded by means of a disk-shaped diaphragm (14) which is fastened to the output part (3), and the cover part (7) is connected to the disk part (6) is placed.
8. Method according to claim 7, characterized in that at the friction ring (19) at its inner circumference (34) hooks (21) are provided which are oriented axially towards the cover part (7) and open radially outwards in a circumferentially distributed manner.
9. Method according to claim 8, characterized in that at the cover part (7) at its inner circumference (23) a recess (31) is provided for the hooks (21) at least in number and in circumferential orientation.
10. Method according to claims 7 and 8, characterized in that the hooks (21) are guided through the recesses (31) and subsequently the friction ring (19) is turned in the circumferential direction relative to the cover part (7) between the two recesses (31) to form the sub-assembly (28).
CN202211726420.9A 2022-01-31 2022-12-30 Torsional vibration damper and method for manufacturing the same Pending CN116518025A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022102138.6 2022-01-31
DE102022102138.6A DE102022102138A1 (en) 2022-01-31 2022-01-31 Torsional vibration damper and method for its manufacture

Publications (1)

Publication Number Publication Date
CN116518025A true CN116518025A (en) 2023-08-01

Family

ID=87160648

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202211726420.9A Pending CN116518025A (en) 2022-01-31 2022-12-30 Torsional vibration damper and method for manufacturing the same

Country Status (2)

Country Link
CN (1) CN116518025A (en)
DE (1) DE102022102138A1 (en)

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014037001A1 (en) 2012-09-06 2014-03-13 Schaeffler Technologies AG & Co. KG Torsional vibration damper
DE102020116058A1 (en) 2020-06-18 2021-12-23 Schaeffler Technologies AG & Co. KG Torsional vibration damper with a friction element

Also Published As

Publication number Publication date
DE102022102138A1 (en) 2023-08-03

Similar Documents

Publication Publication Date Title
CA2539790C (en) Crankshaft torque modulator
US4767380A (en) Damper-type flywheel suitable for automobile transmissions
US9267569B2 (en) Planetary torsional damper system
US8371948B2 (en) Flywheel device
US8453816B2 (en) Flexplate coupling for a wet clutch transmission
US8287390B2 (en) Damper assembly with engine-side cover plate directly connected to engine crankshaft and powertrain having same
US4874350A (en) Torsional damper device comprising two coaxial parts cooperating with circumferentially acting springs
CN106382333B (en) Damper of the twin flywheel type comprising a sealing gasket ensuring the tightness of the primary flywheel
CN107636355B (en) Belt pulley decoupler with slip guide shell
US20050150734A1 (en) Device for coupling a housing arrangement of a coupling device to a rotor arrangement of an electric machine
CN113137451A (en) Torsional vibration damper with coil spring for sealing
CN105927709B (en) Torsional vibration damper and method for producing the same
CN114382834A (en) Torsional vibration damper
CN116518025A (en) Torsional vibration damper and method for manufacturing the same
JP6169450B2 (en) Torsional damper
CN115839389A (en) Torsional vibration damper with torque limiter
CN114761703A (en) Torsional vibration damper with torque limiting device
JP5525435B2 (en) Shaft coupling with torque limiter
CN115038893B (en) Dual mass flywheel with releasable torque limiter
US20210341021A1 (en) Torsional vibration damper
CN115126789A (en) Torque transmission device and torsional vibration damper for the same
US20080149444A1 (en) Torsional vibration damper
CN115929845A (en) Curved spring stop with threading geometry
CN115199701A (en) Torsional vibration damper
US5937987A (en) Motor vehicle clutch

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication