CN115750681A - Torsional vibration damper with sliding clutch - Google Patents
Torsional vibration damper with sliding clutch Download PDFInfo
- Publication number
- CN115750681A CN115750681A CN202211026507.5A CN202211026507A CN115750681A CN 115750681 A CN115750681 A CN 115750681A CN 202211026507 A CN202211026507 A CN 202211026507A CN 115750681 A CN115750681 A CN 115750681A
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- China
- Prior art keywords
- friction
- vibration damper
- torsional vibration
- flange part
- disk
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Classifications
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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
- F16F15/129—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
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- 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 (1) having an input part (2) which is arranged so as to be rotatable about a rotational axis (d) and having an output part (3) which is rotatable relative to the input part (2) about the rotational axis (d) in a limited manner against the action of a spring device (4) and which comprises a slip clutch (5), wherein the slip clutch (5) comprises a substantially radially extending, disk-shaped flange part (21) which is clamped at a radial distance between two support disks (26, 27) which are connected to one another, wherein a frictional connection (29, 30) of the slip clutch (5) between each support disk (26, 27) and the flange part (21) is formed by a friction surface (31, 32) and a metallic counter-friction surface (33, 34). In order to be able to operate the sliding clutch (5) in a thermally balanced manner, the mating friction surfaces (33, 34) are arranged on different components.
Description
Technical Field
The invention relates to a torsional vibration damper having an input part which is arranged so as to be rotatable about an axis of rotation and an output part which is rotatable relative to the input part about the axis of rotation in a limited manner against the action of a spring device and which comprises a slip clutch, wherein the slip clutch comprises a substantially radially extending, disk-shaped flange part which is clamped at a radial distance between two support disks which are connected to one another, wherein the frictional connection of the slip clutch between the support disks and the flange part is formed by a friction surface and a metallic counter-friction surface, respectively.
Background
Torsional vibration dampers of this type are used to damp torsional vibrations in drive trains, in particular hybrid drive trains, of motor vehicles and are usually received on the input side by the crankshaft of an internal combustion engine having torsional vibrations. In order to limit torque peaks, so-called jerks, a slip clutch is integrated into the output of the torsional vibration damper, said slip clutch having a frictional engagement between a preloaded friction surface and a counter-friction surface, and upon the occurrence of a jerk the slip clutch slips and separates the jerk from the downstream part of the drive train.
A torsional vibration damper, referred to as a dual-mass flywheel, is known from DE 10 2018 696 A1, in which a flange part for applying a spring device arranged between an input part and an output part on the output side is clamped between two support disks connected to one another in order to form a slip clutch. In this case, a frictional engagement is produced between two friction surfaces of the support disk, which are designed as friction disks, and a metallic counter-friction surface of the flange part, so that the entire amount of friction produced can be introduced into the flange part.
Disclosure of Invention
The object of the invention is to improve a torsional vibration damper of this type. The invention is based on the object, inter alia, of providing a torsional vibration damper whose thermal load can be compensated.
This object is achieved by the solution of claim 1. The dependent claims of claim 1 reproduce advantageous embodiments of the object of claim 1.
The proposed torsional vibration damper serves to isolate torsional vibrations, in particular of an internal combustion engine with torsional vibrations in a drive train, in particular a hybrid drive train. The torsional vibration damper comprises an input part arranged in a manner capable of rotating around a rotation axis and an output part which is capable of rotating around the rotation axis relative to the input part in a limited manner against the action of a spring device and comprises a sliding clutch.
The torsional vibration damper can be configured as a dual mass flywheel, wherein a primary flywheel can be assigned to the input and a secondary flywheel can be assigned to the output. The input element can be made of a sheet metal, for example. The disk piece and the cover piece, which can be connected to the crankshaft, for example, by means of fastening screws, can also be made of sheet metal, for example, and can be formed in a modified manner, the disk piece and the cover piece being connected to one another in a radially outer, abutting manner or overlapping manner in the axial direction, for example by welding. Further mass elements, encoder markings for controlling the internal combustion engine, starter ring gear and/or the like can be accommodated on the output part depending on the application. The plate piece and the cover piece preferably form an annular chamber in which the spring device is mounted.
The spring device is formed on helical compression springs arranged distributed over the circumference, for example, from arc-shaped springs which are pre-bent over their installation diameter. The spring means act in the circumferential direction. For this purpose, input-side and output-side loading means are provided on the end sides of the helical compression springs. The input-side loading means, which is engaged between the end sides of the helical compression springs adjacent in the circumferential direction and loads the helical compression springs in the circumferential direction upon relative rotation between the input and output members about the axis of rotation, is configured, for example, as an embossing, a material application or the like provided in the disk member and/or in the cover member. The output-side charging means is formed by a flange part which is arranged substantially in the radial direction and has a radially widened flange limb on the radial outside, which flange limb engages between circumferentially adjacent end sides of the helical compression spring and charges the helical compression spring in the circumferential direction. The flange wings are arranged axially between the embossings of the loading means on the input side when the loading means are arranged on both sides on the disk part and the cover part.
The sliding clutch comprises a substantially radially extending, disk-shaped flange part which is clamped at a radial distance between two interconnected support disks. Due to the disk-shaped design, two radially spaced friction joints are produced which are axially preloaded by means of a support disk arranged at an axially fixed distance and which accommodates the disk spring region of the flange part, wherein the friction joints of the slip clutch are formed between the support disk and the flange part by a friction surface and a metallic counter-friction surface, respectively.
In order to introduce the frictional energy occurring in the active sliding clutch not only into the metallic mating friction surfaces of the flange part, but also to distribute the frictional energy introduced into the sliding clutch to the flange part and the support part, the metallic mating friction surfaces of each frictional joint and the friction surfaces forming the respective functional joint with respect thereto are arranged on different components, i.e. on the flange part and the at least one support disk. The friction surfaces are formed in this case from an essentially non-metallic friction material which has a poorer heat-conducting property than the metallic counter-friction surfaces, so that a large part of the friction energy generated during the slip clutch slip is introduced into the respective component via the metallic counter-friction surfaces in the form of thermal energy.
The friction surface can be formed, for example, by a friction lining arranged on the associated component. The friction pad can be used for wet or dry operation. Accordingly, so-called paper mats made of fibrous material are compacted or wound for wet operation or so-called paper mats made of friction material are compacted or wound for dry operation. The friction linings can be directly connected to the respective component, for example adhesively or positively connected. Alternatively, the friction linings can be connected to the carrier plate, for example, pressed, melted and/or the like, in particular for dry operation of the slip clutch. The carrier plate can in this case be connected to the respective component in a form-fitting manner, for example riveted. For example, at least one friction lining can be fixed in one piece on an axial projection on the associated component. The axial projection can be constructed or molded, for example, directly, die-cut or tool-shaped during the production of the respective component, i.e. the support disk or the flange part.
For example, a first friction lining arranged on the first support disk forms a first frictional engagement with a first mating friction surface arranged on the flange part, and a second friction lining arranged on the flange part forms a second frictional engagement with a second mating friction surface arranged on the second support disk.
The first support disk is radially widened relative to the second support disk. The first support disk comprises a friction surface on the radially outer side, which forms a frictional engagement with a metallic mating friction surface of the flange part. For example, the friction joint can transmit a large part of the torque which is required to be transmitted via the slip clutch by means of the friction lining and the corresponding mating friction surface on the flange part. Radially inwardly of the friction joint, a metallic counter-friction surface of the second support disk and a friction lining fixed to the flange part radially inwardly of the metallic counter-friction surface form a second friction joint.
For example, one of the support disks can be connected to the output sleeve of the torsional vibration damper in one piece in order to save manufacturing costs. Friction linings can be arranged in a preferred manner on the support disk. The friction lining is preferably arranged radially outside a further friction lining provided on the flange part.
In a preferred manner, the slip clutch is designed for dry operation, wherein the slip clutch is arranged outside the annular space. In this case, the sliding clutch is preferably arranged radially inside the annular space. In this case, the annular chamber is sealed by means of a sealing ring between the disk part and the flange part on the one hand and between the flange part and the cover part on the other hand. In this case, the sealing can be prestressed axially between the disk part and the flange part or between the cover part and the flange part, respectively. This additionally enables the output part to be positioned elastically in the axial direction relative to the input part.
In order to produce the friction which is possibly set by the sealing ring during the relative rotation of the input part and the output part about the axis of rotation, a further friction device can be provided. For example, the friction ring can be accommodated with axial pretension between the disk element and a support disk adjacent to the disk element. For example, an axial pretension can be provided by pretensioning the sealing ring, so that the friction ring additionally forms an axial stop position of the output part relative to the input part.
Drawings
The invention is explained in more detail on the basis of an embodiment shown in the sole figure. The figures show an upper sectional view of a torsional vibration damper arranged torsionally about a rotational axis.
Detailed Description
The figure shows an upper sectional view of a torsional vibration damper 1 arranged torsionally about a rotational axis d, which has an input part 2 and an output part 3 which can be torsionally pivoted to a limited extent about the rotational axis d against the action of a spring device 4. A slip clutch 5 is operatively arranged in the output 3.
The input member 2 is made of a plate material in this embodiment. For this purpose, the disk element 6 and the cover element 7 are stamped and formed from sheet metal. The disk element 6 can be connected to a crankshaft 10 of an internal combustion engine by means of fastening openings 8 and screws 9 distributed over the circumference. The disc element 6 and the cover element 7 are connected tightly to each other radially on the outside. For this purpose, an axially molded projection 12 of the cover part 7 bridges the axially molded projection 11 of the disk part 6 radially on the outside and is centered thereon or pressed against it. The cover element 7 is welded tightly to the disk 6 on the end face 13 of the projection 11 by means of a preferably circumferential weld 14, forming an annular space 15.
The spring device 4 is accommodated in the annular chamber 15 in a sealed manner with respect to the outside. For lubricating the spring device 4, the annular chamber 15 can be at least partially filled with a lubricant, for example grease. The spring device 4 is formed here by arc-shaped springs 16 distributed over the circumference. Two to six arcuate springs 16 can be arranged distributed over the circumference. The input-side and output-side loading means engage between the end sides of the bow springs 16 adjacent in the circumferential direction, the loading means loading the bow springs 16 in the circumferential direction in a relative rotation of the input part 2 relative to the output part 3. The input-side loading means 17 are in this case embodied as molded parts 18, 19 in the disk piece 6 and the cover piece 7. In order to support the curved spring 16 against centrifugal forces, a solidified sliding cover 20 is arranged between the curved spring 16 and the projection 11.
The output part 3 comprises a flange part 21 and an output sleeve 22 which is connected to the shaft 46 in a rotationally fixed manner by means of an internal toothing 47, between which the slip clutch 5 is arranged. The flange part 21 has an output-side loading means 23 radially on the outside. The flange limb 24, which is radially widened in this case, engages in the annular space 15 between the end sides of the arcuate spring 16 adjacent in the circumferential direction and passes axially between the molded parts 18, 19.
The flange part 21 has a radially inner coil spring region 25 which is clamped axially between support disks 26, 27 connected to one another by means of rivets 28. The support discs 26, 27 form respective frictional engagement portions 29, 30 with the flange member 21. The frictional engagement 29, 30 is formed by a friction pair of a friction surface 31, 32 and a metallic counter-friction surface 33, 34, respectively. The friction surfaces 31, 32 are arranged on friction pads 35, 36. Friction pad 35 is fixed to support disc 26. For this purpose, the support disk 26 is provided with an axial projection 37 into which the friction lining 35 is inserted. The rivet head is then molded onto the axial projection 37, so that the friction lining 35 is fixedly connected to the support disk 26. The friction pad 36 is fixed to the flange member 21. For this purpose, an axial projection 38 is molded onto the flange part 21, by means of which the friction lining 36 is connected to the flange part 21 by being inserted into the axial projection 38 and then by molding a rivet head onto the axial projection 38. Corresponding recesses are provided in the friction linings 35, 36 for receiving the rivet heads.
In order to introduce the frictional energy generated during the slip clutch 5 when it is slipping in a thermally balanced manner, the frictional engagement 29, 30 is formed opposite the flange part 21. This means that a first metallic counter-friction surface 33 is arranged on the flange part 21 and a second metallic counter-friction surface 34 is arranged on the support disk 27. The friction surface 31 associated with the mating friction surface 33 is therefore arranged on a friction lining 35 of the support disk 26 and the friction surface 32 associated with the mating friction surface 34 is arranged on a friction lining 36 of the flange part 21.
The diameters of the support disks 26, 27 are configured differently as a function of the manner of configuration of the axial loading of the disk spring region 25. The support disk 26 with the radially outer friction lining 35 is connected in one piece with the output sleeve 22. The support disk 27 facing the disk element 6 forms a counter-friction surface 34 on the radially outer side of the rivet 28, with a smaller diameter than the counter-friction surface 33.
A friction ring 39 is arranged between the side of the support disk 27 opposite the counter-friction surface 34 and the radially inner part of the rivet 28 and the disk part 6. The friction ring 39 is centered on a reinforcement ring 40 for the screw 9.
The sliding clutch 5 operates in dry mode. In order to avoid contamination of the frictional connections 29, 30 with lubricant from the annular chamber 15, sealing rings 41, 42 are arranged between the disk part 6 and the flange part 21 and the cover part 7. The sealing rings 41, 42 engage in a form-locking manner in circumferentially distributed openings 45 of the flange part 21 and are prestressed in the axial direction by means of disk springs 43, 44. The disk spring 44 pretensions the friction ring 39 in this case, so that the output part 3 is axially positioned relative to the input part 2.
List of reference numerals
1. Torsional vibration damper
2. Input member
3. Output member
4. Spring device
5. Sliding clutch
6. Disc piece
7. Cover member
8. Fixed opening
9. Screw nail
10. Crankshaft
11. Raised part
12. Raised part
13. End side
14. Weld part
15. Annular chamber
16. Arc spring
17. Loading device
18. Molding section
19. Molding section
20. Sliding cover
21. Flange part
22. Output sleeve
23. Loading device
24. Flange wing
25. Region of coil spring
26. Supporting disc
27. Supporting disc
28. Riveting part
29. Frictional engagement portion
30. Frictional engagement portion
31. Friction surface
32. Friction surface
33. Pairing friction surface
34. Pairing friction surface
35. Friction lining
36. Friction lining
37. Axial projection
38. Axial projection
39. Friction ring
40. Reinforcing ring
41. Sealing ring
42. Sealing ring
43. Coil spring
44. Coil spring
45. Opening of the container
46. Shaft
47. Internal tooth system
d axis of rotation
Claims (10)
1. A torsional vibration damper (1) having an input part (2) which can be rotated about a rotational axis (d) and an output part (3) which can be rotated about the rotational axis (d) in a limited manner relative to the input part (2) against the action of a spring device (4) and which comprises a slip clutch (5), wherein the slip clutch (5) comprises a substantially radially extending, disk-shaped flange part (21) which is clamped at a radial distance between two mutually connected support disks (26, 27), wherein the radially spaced-apart friction joints (29, 30) of the slip clutch (5) between the support disks (26, 27) and the flange part (21) respectively are formed by friction surfaces (31, 32) and metallic counter-friction surfaces (33, 34), characterized in that the metallic counter friction surfaces (33, 34) are arranged on different components respectively.
2. Torsional vibration damper (1) as claimed in claim 1, characterized in that the friction surfaces (31, 32) are formed by friction linings (35, 36) arranged on the associated component.
3. The torsional vibration damper (1) as claimed in claim 2, characterized in that a first friction lining (35) arranged on a first support disk (26) forms a first friction joint (29) with a first counter-friction surface (33) arranged on the flange part (21) and a second friction lining (36) arranged on the flange part (21) forms a second friction joint (30) with a second counter-friction surface (34) arranged on a second support disk (27).
4. Torsional vibration damper (1) as claimed in claim 2 or 3, characterized in that at least one friction pad (35, 36) is fixed by means of an axial projection (37, 38) arranged integrally on the said component.
5. The torsional vibration damper (1) as claimed in any of claims 1 to 4, characterized in that one of the support disks (26) is connected integrally with the output sleeve (22) of the torsional vibration damper (1).
6. Torsional vibration damper (1) as claimed in claim 5, characterized in that the first support disk (26), in particular the support disk (26) which is connected in one piece with the output sleeve (22), is widened radially with respect to the second support disk (27) and its friction surface (31) is arranged radially outside of the friction surface (32) on the flange part (21).
7. Torsional vibration damper (1) as claimed in any of claims 1 to 6, characterized in that the input (2) forms an annular chamber (15) for the spring device (4) and the slip clutch (5) is arranged outside the annular chamber (15).
8. Torsional vibration damper (1) according to claim 7, characterized in that the annular chamber (15) is formed by a disc piece (6) which can be connected to a crankshaft (10) by means of a fastening opening (8) and a cover piece (7) which is connected to the disc piece, wherein the annular chamber (15) is sealed by means of sealing rings (41, 42) on one side between the disc piece (6) and the flange piece (21) and on the other side between the flange piece (21) and the cover piece (7).
9. Torsional vibration damper (1) according to claim 7 or 8, characterized in that the slip clutch (5) is arranged radially inside and outside the annular chamber (15).
10. Torsional vibration damper (1) as claimed in any of claims 7 to 9, characterized in that a friction ring (39) is accommodated with axial pretension between the disc piece (6) and the support disc (27) adjacent thereto.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102021122671.6 | 2021-09-02 | ||
| DE102021122671.6A DE102021122671A1 (en) | 2021-09-02 | 2021-09-02 | Torsional vibration damper with a slipping clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115750681A true CN115750681A (en) | 2023-03-07 |
Family
ID=85175582
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211026507.5A Pending CN115750681A (en) | 2021-09-02 | 2022-08-25 | Torsional vibration damper with sliding clutch |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN115750681A (en) |
| DE (1) | DE102021122671A1 (en) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018111696A1 (en) | 2018-05-16 | 2019-11-21 | Schaeffler Technologies AG & Co. KG | Dual Mass Flywheel |
-
2021
- 2021-09-02 DE DE102021122671.6A patent/DE102021122671A1/en active Pending
-
2022
- 2022-08-25 CN CN202211026507.5A patent/CN115750681A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE102021122671A1 (en) | 2023-03-02 |
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