CN114382834A - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN114382834A CN114382834A CN202111062079.7A CN202111062079A CN114382834A CN 114382834 A CN114382834 A CN 114382834A CN 202111062079 A CN202111062079 A CN 202111062079A CN 114382834 A CN114382834 A CN 114382834A
- Authority
- CN
- China
- Prior art keywords
- output
- vibration damper
- torsional vibration
- axial
- sheet metal
- 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
Links
Images
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
- F16F15/121—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
- F16F15/129—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
-
- 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
- F16F2230/0052—Physically guiding or influencing
- F16F2230/007—Physically guiding or influencing with, or used as an end stop or buffer; Limiting excessive axial separation
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 (1) having an input part (2) which is arranged so as to be rotatable about a rotational axis (d) and an output part (13) which is rotatable relative to the input part about the rotational axis (d) against the action of a spring device (10), the output part having an output hub (15) which is produced from sheet metal and a flange part (14) which is connected to the output hub and which is acted upon by the spring device (10) on the output side. In order to securely fasten the input part (2) and the output part (13) to one another, for example during transport after installation, an axial recess (27) is provided in the output part (13), into which the sheet metal part (25) of the input part engages with an axial play (26).
Description
Technical Field
The invention relates to a torsional vibration damper having an input part which is arranged so as to be rotatable about a rotational axis and an output part which is rotatable relative to the input part about the rotational axis against the action of a spring device, the output part having an output hub which is produced from a sheet metal and a flange part which is connected to the output hub and which is acted upon by the spring device on the output side.
Background
Torsional vibration dampers are used to isolate torsional vibrations of an internal combustion engine with torsional vibrations of a drive train of a motor vehicle. For this purpose, the input part of the torsional vibration damper is connected to the crankshaft and the output part is connected to the remaining drive train. The torque with torsional vibrations entering the input part is damped by means of spring devices arranged in an active manner between the input part and the output part and friction hysteresis devices connected in parallel with the spring devices and is transmitted via the output hub, for example, to a subsequent friction clutch or to a dual clutch of a dual clutch transmission.
A torsional vibration damper of this type is known, for example, from DE 102018125615 a1, the output hub of which is produced from sheet metal by means of a stamping method. The input part and the output part are axially displaced relative to each other over a large area at the spring device, for example after assembly, for example during transport.
Disclosure of Invention
The object of the invention is to improve a torsional vibration damper of this type. The object of the invention is in particular to stabilize a torsional vibration damper during transport and operation thereof.
This object is achieved by the subject matter of claim 1. The dependent claims of claim 1 present advantageous embodiments of the subject matter of claim 1.
The proposed torsional vibration damper serves to isolate torsional vibrations of an internal combustion engine with torsional vibrations in a conventional or hybrid drive train of a motor vehicle. For this purpose, the torsional vibration damper is connected to the crankshaft of the internal combustion engine in a rotationally fixed manner indirectly or directly, for example, by means of a fastening bolt of its input part. The input part is arranged so as to be rotatable about a rotational axis and, if it is directly fastened to the crankshaft, is arranged so as to be rotatable about the crankshaft axis. The output part of the torsional vibration damper can be arranged in a rotationally fixed manner relative to the input part against the action of the spring device about the axis of rotation or rather about an axis of rotation (described in the following description as the axis of rotation of the input part) which is axially offset to a lesser extent relative to the axis of rotation of the input part by means of the output hub.
The torsional vibration damper can be configured as or provide the function of a dual mass flywheel. For this purpose, the input part has a primary flywheel mass. The output member itself may have a secondary flywheel mass. Alternatively or additionally, a downstream drive train device, for example a secondary flywheel mass of a double clutch, a hydrodynamic torque converter, a rotor of an electric machine or the like, can be coupled downstream of the output part via the output hub and thus produce the effect of a dual mass flywheel of the torsional vibration damper.
At least one component of the component rotatable about the axis of rotation is produced from a sheet metal by means of a stamping forming method. The input part can be produced by a plate part made of sheet metal having a fastening opening, wherein a cover part made of sheet metal can be connected in a sealing manner to the plate part radially on the outside to form an annular space in which the spring device is accommodated. A starter ring gear, a sensor ring for detecting a characteristic value of the rotation of the crankshaft of the internal combustion engine and/or a mass ring, for example, produced from sheet metal, can be arranged on the disk and/or the cover.
The output member includes an output hub made of sheet material, the internal teeth of which may be broached or otherwise fabricated during the stamping process without the need for rework (werkzeugfallend) or subsequent machining. Furthermore, the output part comprises a flange part for loading the spring device in the circumferential direction on the output side by means of a flange wing widening radially outward. The output part can be equipped with an additional mass and/or a centrifugal pendulum made of solid or sheet metal, the pendulum mass support of which can be a flange part, for example. In order to limit the maximum torque that can be transmitted via the torsional vibration damper, a torque limiting device can be provided between the spring device and the internal toothing of the output hub.
The spring device may be formed by helical compression springs arranged distributed over the circumference, the end sides of which are loaded in the circumferential direction on the input side and the output side, respectively. For this purpose, axially widened loading devices can be provided on the disk and the cover on the input side, which loading devices are mounted or formed as a press, for example by welding. The output side is loaded by means of a flange part. The helical compression spring may be provided as an arc-shaped spring divided into two, three or four portions that are pre-bent in its use diameter. A plurality of helical compression springs may be nested within one another to form a spring stack distributed over the circumference. Multiple sets of helical compression springs or spring sets may be stacked radially one above the other. If necessary, the helical compression spring can be supported radially on the outside on the annular chamber by an interposed hardened wear protection cover. To avoid friction, the annular chamber may be at least partially filled with a lubricant, such as grease.
The annular cavity may be sealed between the input member and the output member. For example, a diaphragm spring can be arranged axially preloaded on the output side between the flange part and/or the output hub and on the input side at the cover part. The diaphragm spring can be fixedly received between the flange part and the output hub at the rivet and can be prestressed relative to the cover part. Alternatively, the diaphragm spring can be fixed on the input side and be prestressed relative to the output part. Preferably, the dynamic frictional contact of the diaphragm spring with the friction ring arranged in between is used as a friction device, which provides a frictional hysteresis device in parallel with the spring device. The diaphragm spring axially pretensions the output part relative to the input part. For this purpose, an axial sealing ring is preferably clamped axially in the radial direction in the fastening opening between the input part, for example a disk part, and the output part, for example a flange part, the axial sealing ring supporting the base friction and sealing the annular chamber radially on the inside.
In order to stabilize the torsional vibration damper in relation to axial loads between the input part and the output part, in particular during transport after assembly thereof, an axial recess is provided between the input part and the output part, into which the sheet metal part of the input part engages with axial play. The engagement of the sheet metal part in the axial recess ensures a friction-free operation of the torsional vibration damper during operation. After assembly, for example during transport, excessive axial displacement of the output part relative to the input part is avoided by the sheet metal part, after the axial play has been eliminated, being stopped on the output part and being supported on the input part. In particular in the case of diaphragm springs, the axial recess is dimensioned such that an axially elastic spring path of the diaphragm spring is set in the axial gap between the input part and the output part. Thus, if, for example, during the lifting of the torsional vibration damper at the output part, the output part is supported on the sheet metal part of the input part after the axial play has been eliminated, the diaphragm spring is protected against plastic deformation.
According to an advantageous embodiment of the torsional vibration damper, the flange part and the output hub bear radially on one another and are riveted to one another by means of a central rivet. In this case, it is advantageous to form an axial recess between the flange part and the output hub, i.e. to set the axial recess on the flange part and/or on the output hub by means of a deformation process which does not require reworking.
In this case, the output hub can have a pot-shaped portion in the radial region of the axial recess, i.e. radially on the inside of the central rivet and radially on the outside of the internal toothing, which widens the axial recess between the flange part and the output hub.
Alternatively, for example, in the case of a narrow axial installation space, the output hub can have a press-on in the radial region of the axial recess, which widens the axial recess.
Alternatively or additionally, the flange part may have a lead-through on its inner circumference in the radial region of the axial recess, which widens the axial recess. In this case, the pot and/or the press is/are configured axially away from the flange part and/or the feedthrough is configured axially away from the output hub.
As sheet metal parts which engage in the preferably circumferentially formed axial recesses, it is possible to use, for example, webs which are fixedly connected to the disk parts with the fastening openings or ring parts or webs formed from the disk parts. It has proven to be particularly advantageous to connect at least one sheet metal part, which is produced in a forming process, for example flat-stamped, pre-bent and subsequently connected, for example welded, to the input part, surrounds the flange part radially on the inside thereof and extends radially into the axial recess. In this case, an annular edge which engages radially from the inside into the axial recess can be provided on the sheet metal part. Alternatively, a plurality of flanges distributed over the circumference, turned out radially outward and engaging into the axial recess can be provided.
For example, sheet metal parts which are configured as reinforcing rings for the disks can be arranged in the region of the fastening openings. The reinforcing ring has a radial region with an opening aligned with the fastening opening of the disk, to which radial region an axial projection is connected, which axial projection has a radially outwardly turned flange engaging in an axial recess on the end side.
Drawings
The invention is described in detail with reference to an embodiment shown in the sole drawing. The figures show a sectional view of the upper part of a torsional vibration damper arranged rotatably about a rotational axis.
Detailed Description
The sole figure shows a simplified sectional view of the upper part of the torsional vibration damper 1 arranged rotatably about the axis of rotation d, and the figure does not show the components that are present if appropriate, such as the starter ring gear, the sensor ring, the additional masses on the input and/or output side, the centrifugal pendulum, the torque limiting device, etc.
The input part 2 comprises a disk 3 having a fastening opening 4 and a fastening screw 5 for fastening the torsional vibration damper 1 to a crankshaft of an internal combustion engine or to a component operatively connected thereto. A reinforcing ring 6 is accommodated on the disc 3. The cover 8 is connected in a sealing manner, for example welded, to the axially molded projection 7 of the disk 3 radially on the outside. The disc 3 and the cover 8 form an annular chamber 9 in which the spring means 10 are accommodated.
The spring device 10 has helical compression springs 11 distributed over the circumference, the helical compression springs 11 being configured as arc-shaped springs which are pre-bent over their use diameter. The arcuate springs are supported against centrifugal force on the annular chamber 9 with a preferably hardened wear protection cover 12 placed radially on the outside in the middle.
The output part 13 comprises a flange part 14 and an output hub 15 with internal toothing 16, the flange part 14 and the output hub 15 being connected to each other by means of rivets 18 of a main rivet 17.
During the relative rotation of the input part 2 and the output part 13, the spring device 10 acts in the circumferential direction. For this purpose, the end sides of the helical compression springs 11 are acted upon in the circumferential direction on the input side by the pressed sections 19, 20 and on the output side by the radially widened flange limb 21 of the flange part 14.
The annular chamber 9 can be at least partially filled with lubricant to lubricate the spring device 10 and sealed off outwards by the diaphragm spring 22 and inwards by the axial sealing ring 23. The diaphragm spring 22 is accommodated on the main rivet 17 and is axially preloaded against the cover 8 at the radial outside. This pretension force axially displaces the output part 13 relative to the input part 2 and pretensions the axial sealing ring 23. The axial sealing ring 23 is centered on the reinforcement ring 6.
A friction ring 24 is arranged between the diaphragm spring 22 and the cover 8, so that on the one hand a friction hysteresis, which is superimposed on the spring device 10, is coupled between the diaphragm spring 22 and the cover 8, and on the other hand a friction hysteresis, which is superimposed on the spring device 10, is coupled between the flange part 14 and the disk part 3 by means of an axial sealing ring 23.
In order to limit the axial travel of the output part 13 relative to the input part 2 at least to the elastic spring travel of the diaphragm spring 22 and to prevent elastic deformation of the diaphragm spring, for example when the torsional vibration damper 1 located on the output part 13 is lifted, a sheet metal part 25 in the form of a reinforcing ring 6 is engaged with an axial gap 26 in an axial recess 27 of the output part 13.
The axial recess 27 is preferably formed without further machining by corresponding machining of the components made of sheet metal (flange part 14 and output hub 15). For this purpose, the output hub 15 has a pot 28 in the radial region of the axial recess 27. The pot 28 displaces the internal toothing 16 of the output hub 15 and the portion radially inside the pot 28 relative to the contact surface 29 of the output hub 15 that bears against the flange part 14 at the main rivet 17 and axially away from the disk 3. Thereby increasing the axial clearance 27 between the flange member 14 and the output hub 15. Furthermore, a lead-through 30, which is directed axially in the direction of the disk 3 and which further enlarges the axial recess 27, is molded onto the inner circumference of the flange part 14.
The reinforcing ring 6, which is made of sheet metal, has an axially widened projection 31 on the radial outside, on which the axial sealing ring 23 is centered, and on the end side, a collar 32 which widens radially into the axial recess 27. By making the axial stiffness of the flange 32 greater than the stiffness of the diaphragm spring 22, the output part 13 is supported on the input part 2 without exceeding the axial elastic spring travel of the diaphragm spring 22 after the axial play 26 of the flange 32 has been eliminated and the flange has stopped on the flange part 14 or on the output hub 15.
The torsional vibration damper 1 is assembled, for example, by placing a helical compression spring 11 and a flange 14 in the flat-lying disk 3. The reinforcing ring 6 with the axial sealing ring 23 centered thereon is then installed and the fastening bolt 5 is introduced into the fastening opening 4. The diaphragm spring 22 and the output hub 15 are riveted to the flange part 14 by means of rivets 18 through rivet openings 33. The rivet opening 33 is then closed by means of a sealing cap 34. Finally, the cover 8 with the friction ring 24 installed is placed and the cover 8 is welded to the disc 3. The torsional vibration damper 1 can be lifted for transport and for mounting on the crankshaft on the output part 13, for example at the centering openings of the internal toothing 16. The torsional vibration damper 1 is screwed to the crankshaft by means of a screw tool which engages via the engagement opening 35 of the output hub 15 by means of the fastening screw 5.
List of reference numerals
1 torsional vibration damper
2 input part
3 disc
4 fixed port
5 fastening bolt
6 reinforcing ring
7 projection
8 cover part
9 Ring Cavity
10 spring device
11 helical compression spring
12 wear prevention cover
13 output member
14 Flange part
15 output hub
16 internal tooth part
17 main riveting part
18 rivet
19 pressing part
20 pressing part
21 flange wing
22 diaphragm spring
23 axial sealing ring
24 friction ring
25 sheet metal part
26 axial gap
27 axial hollow part
28 pot shaped part
29 contact surface
30 threading part
31 projection
32 Flange
33 rivet port
34 sealing cover
35 joint mouth
d axis of rotation
Claims (10)
1. A torsional vibration damper (1) having an input part (2) which is arranged rotatably about a rotational axis (d) and an output part (13) which is rotatable relative to the input part about the rotational axis (d) against the action of a spring device (10) and which has an output hub (15) which is manufactured from sheet metal and a flange part (14) which is connected to the output hub and which acts on the spring device (10) on the output side, characterized in that an axial recess (27) is provided in the output part (13) into which a sheet metal part (25) of the input part (2) engages with an axial play (26).
2. The torsional vibration damper (1) as claimed in claim 1, characterized in that the axial recess (27) is set on the flange part (14) and/or on the output hub (15) by means of a deformation process which does not require reworking.
3. The torsional vibration damper (1) as claimed in claim 2, characterized in that the output hub (15) has a pot (28) in the radial region of the axial recess (27) which widens it.
4. Torsional vibration damper (1) as claimed in claim 2, characterized in that the output hub has a press-on widening of the axial recess in the radial region of the axial recess.
5. The torsional vibration damper (1) as claimed in any of claims 2 to 4, characterized in that the flange part (14) has a lead-through (30) at its inner periphery in the radial region of the axial recess (27) which widens the axial recess.
6. The torsional vibration damper (1) as claimed in any of claims 1 to 5, characterized in that at least one sheet metal part (25) is connected to the input part (2), which sheet metal part surrounds the flange part (14) radially on the inside thereof and extends radially into the axial recess (27).
7. The torsional vibration damper (1) as claimed in any of claims 1 to 6, characterized in that the disk (3) of the input part (2) has a fixing opening (4) for receiving at a crankshaft of an internal combustion engine and is connected radially outside with a cover part (8) so as to form an annular chamber (9) for receiving the spring device (10).
8. Torsional vibration damper (1) according to claim 7, characterized in that the sheet metal part (25) is configured as a stiffening ring (6) of the disc (3) at the fixing opening (4).
9. The torsional vibration damper (1) as claimed in claim 7 or 8, characterized in that a diaphragm spring (22) is arranged between the cover (8) and the output part (13) with an axial pretension.
10. A torsional vibration damper (1) as claimed in claim 9, characterized in that the axially elastic spring travel of the diaphragm spring (22) is set in an axial gap (26) between the input part (2) and the output part (13).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102020127664 | 2020-10-21 | ||
| DE102020127664.8 | 2020-10-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114382834A true CN114382834A (en) | 2022-04-22 |
Family
ID=80929658
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111062079.7A Pending CN114382834A (en) | 2020-10-21 | 2021-09-10 | Torsional vibration damper |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN114382834A (en) |
| DE (1) | DE102021119593A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024124475A1 (en) * | 2022-12-15 | 2024-06-20 | 舍弗勒技术股份两合公司 | Dual mass flywheel |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102022105910A1 (en) | 2022-03-14 | 2023-09-14 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018125615A1 (en) | 2018-10-16 | 2020-04-16 | Schaeffler Technologies AG & Co. KG | Centrifugal pendulum |
-
2021
- 2021-07-28 DE DE102021119593.4A patent/DE102021119593A1/en active Pending
- 2021-09-10 CN CN202111062079.7A patent/CN114382834A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024124475A1 (en) * | 2022-12-15 | 2024-06-20 | 舍弗勒技术股份两合公司 | Dual mass flywheel |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102021119593A1 (en) | 2022-04-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101756996B1 (en) | Flexible flywheel, particularly for a motor vehicle | |
| US4790419A (en) | Clutch with damper type flywheel | |
| JP4106106B2 (en) | Torsional vibration attenuator | |
| US4844216A (en) | Torque converter provided with vibration damper | |
| US5125872A (en) | Apparatus for damping torsional vibrations with a slip clutch between input and output members | |
| US4767380A (en) | Damper-type flywheel suitable for automobile transmissions | |
| US20070151918A1 (en) | Vibration filter for a transmission with automatic, continuous or discontinuous, gearchange, especially for a motor vehicle | |
| CN110621906B (en) | Uncovered dual mass flywheel with centrifugal pendulum | |
| GB2221281A (en) | Torsion vibration damper | |
| CN114382834A (en) | Torsional vibration damper | |
| US5720475A (en) | Torsion damping device, especially for a motor vehicle | |
| US9255610B2 (en) | Torque transmission device | |
| CN113137451A (en) | Torsional vibration damper with coil spring for sealing | |
| US5476166A (en) | Flywheel and clutch system for a motor vehicle | |
| CN111919047B (en) | Torsional vibration damper | |
| US5772516A (en) | Damping device adapted to be integrated into a motor vehicle power unit | |
| CN112833109B (en) | Torque limiter and torsional vibration damper | |
| US5119692A (en) | Damped double flywheel, in particular for automotive vehicles | |
| CN113446354A (en) | Dual mass flywheel | |
| US5761970A (en) | Damping flywheel, particularly for motor vehicles | |
| US11703104B2 (en) | Clutch device comprising a fastening unit, which has a clamping element between a torsional vibration damper and a disconnect clutch | |
| CN112283296B (en) | Torsional vibration damper | |
| CN110848325B (en) | Torsional vibration damper | |
| CN113494563A (en) | Torsional vibration damper and method for assembling a torsional vibration damper | |
| CN114761703A (en) | Torsional vibration damper with torque limiting device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |