CN101321969A - Rotary oscillation damper - Google Patents
Rotary oscillation damper Download PDFInfo
- Publication number
- CN101321969A CN101321969A CNA2006800454614A CN200680045461A CN101321969A CN 101321969 A CN101321969 A CN 101321969A CN A2006800454614 A CNA2006800454614 A CN A2006800454614A CN 200680045461 A CN200680045461 A CN 200680045461A CN 101321969 A CN101321969 A CN 101321969A
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- CN
- China
- Prior art keywords
- vibration damper
- torsional vibration
- coupling
- energy storage
- matrix
- 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.)
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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
- 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
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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
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
- F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
- F16F15/1343—Wound springs characterised by the spring mounting
- F16F15/13453—Additional guiding means for springs
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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
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)
- Vibration Dampers (AREA)
- Vibration Prevention Devices (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
The invention relates to a tortional vibration damper, in particular a divided flywheel, having at least two flywheel masses which can be rotated counter to the resistance of at least two deformable energy store elements, in particular helical pressure springs which are coupled to one another by at least one coupling device which, when a first energy store elements deforms, is in particular relaxed, brings about selective driving of a second energy store element, and has at least a first and a second driver device. In order to prevent undesired shaking during operation of a motor vehicle which is equipped with the tortional vibration damper, the first driver device is coupled to a first coupling element, which is in turn coupled to the first energy store element, and the second driver device is coupled to a second coupling element which is in turn coupled to the second energy store element.
Description
The present invention relates to a kind of torsional vibration damper, especially divided flywheel, have at least two flywheel masses, the resistance that these flywheel masses can be resisted at least two deformable energy storage element, especially helical compression springs reverses, these energy storage elements are coupled each other by at least one coupling device, and described coupling device makes the second energy storage element on purpose be taken and has one first at least and takes device and one second and take device at the first energy storage deformed element, when especially lax.
Task of the present invention is, avoids producing the vibration of not expecting in the work that is equipped with according to the Motor Vehicle of the torsional vibration damper of claim 1 preamble.
A kind of torsional vibration damper, especially divided flywheel, have at least two flywheel masses, these flywheel masses can be resisted at least two deformable energy storage elements, especially the resistance of helical compression spring reverses, these energy storage elements are coupled each other by at least one coupling device, described coupling device is at the first energy storage deformed element, make the second energy storage element on purpose be taken when especially lax and have one first at least and take device and one second and take device, in this torsional vibration damper, this task solves like this: first takes device and first coupling element is coupled, second takes device and second coupling element is coupled, described first coupling element also is coupled with the first energy storage element, and described second coupling element also is coupled with the second energy storage element.In the research that traditional torsional vibration damper is implemented within the scope of the present invention, determine, when rotating speed is high traction travel and inertia traveling between alternately the time energy storage element under friction, stop, and the output member of torsional vibration damper moves on the inertia direction.Contingently when rotating speed reduces be energy storage element spring when reaching definite rotating speed.If the energy storage element bounces, then between these rotating speeds, produce so-called dynamic unbalance under different rotating speeds.Can avoid the energy storage element to stop undesirably or bounce by coupling element and coupling device according to coupling of the present invention.Coupling element relates to stop element or buffer element.
A preferred embodiment of this torsional vibration damper is characterised in that: coupling element respectively be placed in the energy storage element, when this torsional vibration damper bears traction load, at first be loaded on the end with power.The energy storage element preferably relates to arc helical compression spring.Coupling element preferably relates to for example stop element of cup-shaped, and these stop elements are arranged between the loaded member and affiliated energy storage element of the output member of this torsional vibration damper or outlet side in a circumferential direction.
Another preferred embodiment of this torsional vibration damper is characterised in that: coupling element respectively has a matrix, and described matrix has fixedly a section and a coupling section.Matrix preferably has basically to the configuration of the hollow cylinder of small part.Fixedly section is used for coupling element is fixed on affiliated energy storage element.The coupling section is used for being coupled with coupling device.
Another preferred embodiment of this torsional vibration damper is characterised in that: fixedly section have at least one around groove.Groove can be realized sealed connection of shape between coupling element and the affiliated energy storage element.Coupling element is remained on the energy storage element in the axial direction.
Another preferred embodiment of this torsional vibration damper is characterised in that: the coupling section has two beads that are spaced apart from each other in the axial direction.Intermediate space between the bead is formed for taking the embedding possibility of element.
Another preferred embodiment of this torsional vibration damper is characterised in that: coupling device comprises the matrix of a ring-type.The preferred coupled device is configured to plate integratedly.
Another preferred embodiment of this torsional vibration damper is characterised in that: stretch out two from the matrix of ring-type and take finger.Take in the intermediate space between the bead that refers in the mounted state of this torsional vibration damper, respectively be embedded on the coupling section.
Another preferred embodiment of this torsional vibration damper is characterised in that: take finger and extend in the axial direction.Can realize that thus an additional inside vibration damper is installed in the inner radial of energy storage element.
Another preferred embodiment of this torsional vibration damper is characterised in that: the matrix of ring-type has angular cross section.Can realize the stable support of coupling device thus.
Another preferred embodiment of this torsional vibration damper is characterised in that: be bearing between the elementary flywheel mass or input component and at least one slip shell of this torsional vibration damper, described slip shell is arranged between the energy storage element and elementary flywheel mass or input component of this torsional vibration damper the matrix floating of ring-type.Preferably give slip shell of each energy storage arrangements of components.
Another preferred embodiment of this torsional vibration damper is characterised in that: elementary flywheel mass or input component are provided with a plurality of projections, and the slip shell is located in the axial direction by these projections.The matrix that guarantees the ring-type of coupling device thus has enough gaps.
Another preferred embodiment of this torsional vibration damper is characterised in that: the slip shell respectively is provided with the portion of leaving a blank near projection.Can save structure space thus, and the function of torsional vibration damper is unaffected.
Another preferred embodiment of this torsional vibration damper is characterised in that: the matrix of ring-type respectively has the portion of leaving a blank near projection.Projection under the portion of leaving a blank can realize extends through in the axial direction.
From the explanation that with reference to the accompanying drawings different embodiments is described in detail, obtain other advantage of the present invention, feature and details.Accompanying drawing is represented:
Fig. 1 is according to the plan view of first embodiment's torsional vibration damper;
The cross section view of the line II-II of Fig. 2 in Fig. 1;
The part of an amplification among Fig. 3 Fig. 2;
The three-dimensional view of a coupling ring of Fig. 4;
Plan view that has the helical compression spring of coupling element of Fig. 5;
The three-dimensional view of this coupling element of Fig. 6;
Fig. 7 is according to the plan view of second embodiment's torsional vibration damper;
The cross section view of the line VIII-VIII of Fig. 8 in Fig. 7;
The local I X of an amplification among Fig. 9 Fig. 8;
The plan view of the output member of the torsional vibration damper among Figure 10 Fig. 7;
The plan view of the slip shell of the torsional vibration damper among Figure 11 Fig. 7 to Fig. 9;
The cross section view of the line XII-XII of Figure 12 in Figure 11; And
The cross section view of the line XIII-XIII of Figure 13 in Figure 11.
Constitute a divided flywheel 1 with the torsional vibration damper shown in the different views in Fig. 1 and Fig. 2, this divided flywheel has first or elementary flywheel mass 2 and second or a secondary flywheel mass 3 on the unshowned output shaft that can be fixed on internal-combustion engine.Under intermediate arrangement has the situation of a clutch disk, be fixed with a friction clutch on second flywheel mass 3, an also unshowned transmission input shaft is engaged and separating by this friction clutch.Elementary flywheel mass 2 is also referred to as the input component of torsional vibration damper.Secondary mass 3 is also referred to as the output member of torsional vibration damper.
These two flywheel masses 2 and 3 can support by bearing 4 with reversing toward each other.Bearing 4 is arranged on the radially outer in the hole 5 that is used to pass set screw in the embodiment shown, and these set screws are used for first flywheel mass is assemblied in the output shaft of internal-combustion engine.A vibration damping equipment 6 works between these two flywheel masses 2 and 3, and this vibration damping equipment comprises the energy storage element that some also are made of helical compression spring 7,8.See in the plan view in Fig. 1 that respectively be provided with an other helical compression spring 9,10 in the inside of helical compression spring 7,8, described other helical compression spring has less outer diameter.Inner radial at helical compression spring 7 to 10 is provided with an inner vibration damper 11, and this inside vibration damper comprises some helical compression springs 12.Helical compression spring 7,8 is crooked in a circumferential direction and each is stretching on the angular ranges of 180 degree almost.These two helical compression springs 7 and 8 are in the opposed layout in diameter two ends.
These two flywheel masses 2 and 3 have the loading zone 14,15,16 and 17 that is used for energy storage device 7,8. Loading zone 14,15 is configured on the elementary flywheel mass 2 at input side.Loading zone 16 and 17 respectively is arranged between the loading zone 14 and 15 at outlet side.In addition, loading regional 16 loaded member 20 by flange-like is connected with secondary flywheel mass 3 by means of riveted joint connecting element 21.The loaded member 20 of flange-like is used as torque transfering element between energy storage device 7,8 and secondary flywheel mass 3.The loaded member 20 of flange-like is also referred to as output member.
These two helical compression springs 7 and 8 are coupled each other by coupling device 24.Fig. 4 neutral body show coupling device 24.See that in Fig. 4 coupling device 24 comprises a matrix 25 with ring-type of angular cross section.Therefore, coupling device 24 is also referred to as coupling ring.Extending two in the axial direction from the matrix 25 of ring-type is arranged on taking of diameter two ends and refers to 27,28.
See that in Fig. 3 taking of being shown in broken lines refers to that 27 legs with respect to the angular cross section of the matrix 25 of ring-type are provided with abreast.See that in Fig. 1 the finger 27,28 of taking that stretches out from coupling ring respectively is embedded into the coupling element 31,32. Coupling element 31,32 respectively is fixed on the end of affiliated helical compression spring 7,8.
See that in Fig. 5 coupling element 31 has a matrix 34 of sleeve shape basically, the matrix of this sleeve shape has fixedly a section 35 and a coupling section 36.Fixedly section 35 be equipped with one around groove 37, the spring ring on the end of helical compression spring 7 be embedded into this around groove in.Coupling section 36 has two beads that are spaced apart from each other 38,39.Intermediate space between the bead 38 and 39 can realize taking the embedding that refers to.
The independent coupling element 31 that shows among Fig. 6 three-dimensionally.See that in this three- dimensional view bead 38 and 39 has identical inner diameter and outer diameter.
In the zoomed-in view of Fig. 3, see, between the input component 2 of helical compression spring 7,8 and torsional vibration damper 1, be provided with a slip shell 41 in the radial direction.Slip shell 41 is located by projection 43 in the axial direction, and this projection extrudes from the lid 40 of input component 2.See that in Fig. 1 three projections 43 to 45 extrude from covering 40 altogether.This three projections 43 to 45 are responsible for: the motion that slip shell 41 is not expected in the axial direction or tumble in intermediate space.
Illustrated among Fig. 7 to Fig. 9 one with Fig. 1 to Fig. 6 in similar embodiment.For the identical part of mark, use identical reference number.For fear of repetition, with reference to above stated specification to Fig. 1 to Fig. 6.Only inquire into the difference between these two embodiments below.
See that in Fig. 8 torsional vibration damper 1 comprises two slip shells 41 and 42.See that in the zoomed-in view of Fig. 9 the matrix 25 of coupling ring 24 has the portion 60 of leaving a blank, projection 53 extends through this portion of leaving a blank.Projection 53 extrudes and the axial stop of the shell 42 that is configured for sliding from the lid 40 of elementary flywheel mass 2.
See that in Figure 10 each three projection 53 to 55 and 56 to 58 that is used for these two slip shells are arranged on the loaded member 20 of flange-like.Projection is provided with distributing on the circumference of affiliated slip shell.
The different views of slip shell 42 has been shown among Figure 11 to Figure 13.See that in the cross section view of Figure 13 slip shell 42 has the portion 61 of leaving a blank, this portion of leaving a blank is arranged in the state that slip shell 42 is packed in the zone of taking finger 28 of coupling ring 24.
The reference number inventory
1 flywheel, 20 loaded member
2 flywheel masses, 21 riveting elements
3 flywheel masses, 24 coupling devices
4 bearings, 25 matrixes
Finger is taken in 5 holes 27
6 vibration absorbers 28 are taken finger
7 helical compression springs, 31 coupling elements
8 helical compression springs, 32 coupling elements
9 helical compression springs, 34 matrixes
10 helical compression springs 35 are section fixedly
11 inner shock absorber 36 coupling sections
12 helical compression springs, 37 grooves
14 load regional 38 beads
15 load regional 39 beads
16 load zone 40 lids
17 load regional 41 slip shells
42 slip shells, 55 projections
43 projections, 56 projections
44 projections, 57 projections
45 projections, 58 projections
53 projections 60 portion of leaving a blank
54 projections 61 portion of leaving a blank
Claims (13)
1. torsional vibration damper, especially divided flywheel, have at least two flywheel masses (2,3), these flywheel masses can be resisted at least two deformable energy storage elements (7,8), especially the resistance of helical compression spring reverses, these energy storage elements are coupled each other by at least one coupling device (24), described coupling device is out of shape at the first energy storage element (7), make the second energy storage element (8) on purpose be taken when especially lax and have one first at least and take device (27) and one second and take device (28), it is characterized in that: described first takes device (27) is coupled with first coupling element (31), described second takes device (28) is coupled with second coupling element (32), described first coupling element also is coupled with the described first energy storage element (7), and described second coupling element also is coupled with the described second energy storage element (8).
2. one torsional vibration damper in requiring according to aforesaid right, it is characterized in that: these coupling elements (31,32) respectively be placed in these energy storage elements (7,8), when this torsional vibration damper bears traction load, at first be loaded on the end with power.
3. one torsional vibration damper in requiring according to aforesaid right, it is characterized in that: these coupling elements (31,32) respectively have a matrix (34), and described matrix has fixedly a section (35) and a coupling section (36).
4. according to the torsional vibration damper of claim 3, it is characterized in that: described fixedly section (35) have at least one around groove (37).
5. according to the torsional vibration damper of claim 3 or 4, it is characterized in that: described coupling section (36) has two beads that are spaced apart from each other in the axial direction (38,39).
6. one torsional vibration damper in requiring according to aforesaid right, it is characterized in that: described coupling device (24) comprises the matrix (25) of a ring-type.
7. according to the torsional vibration damper of claim 6, it is characterized in that: stretch out two from the matrix (25) of described ring-type and take finger (27,28).
8. according to the torsional vibration damper of claim 7, it is characterized in that: these are taken finger (27,28) and extend in the axial direction.
9. according to one torsional vibration damper in the claim 6 to 8, it is characterized in that: the matrix of described ring-type (25) has angular cross section.
10. according to one torsional vibration damper in the claim 6 to 9, it is characterized in that: the matrix of described ring-type (25) floating ground is bearing in the elementary flywheel mass (2) and at least one slip shell (41 of this torsional vibration damper, 42) between, described slip shell is arranged between the energy storage element (7,8) of this torsional vibration damper and elementary flywheel mass (2) or the input component.
11. the torsional vibration damper according to claim 10 is characterized in that: this elementary flywheel mass (2) or this input component are provided with a plurality of projections (43～45; 53～58), described slip shell (41,42) is located in the axial direction by these projections.
12. the torsional vibration damper according to claim 11 is characterized in that: described slip shell (42) respectively is provided with the portion of leaving a blank (61) near these projections.
13. the torsional vibration damper according to claim 11 or 12 is characterized in that: the matrix of described ring-type (25) respectively has the portion of leaving a blank (60) near these projections.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102005057841.1 | 2005-12-03 | ||
| DE102005057841 | 2005-12-03 | ||
| PCT/DE2006/001997 WO2007062620A1 (en) | 2005-12-03 | 2006-11-15 | Rotary oscillation damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101321969A true CN101321969A (en) | 2008-12-10 |
| CN101321969B CN101321969B (en) | 2011-01-12 |
Family
ID=37650648
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006800454614A Active CN101321969B (en) | 2005-12-03 | 2006-11-15 | Rotary oscillation damper |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP1957825A1 (en) |
| KR (1) | KR20080071978A (en) |
| CN (1) | CN101321969B (en) |
| BR (1) | BRPI0619162B1 (en) |
| DE (1) | DE112006002997B4 (en) |
| WO (1) | WO2007062620A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105452710A (en) * | 2013-08-09 | 2016-03-30 | Zf腓特烈斯哈芬股份公司 | Torsional vibration damping arrangement for the powertrain of a vehicle |
| CN111989507A (en) * | 2018-04-10 | 2020-11-24 | 舍弗勒技术股份两合公司 | Torsional vibration damper, clutch disc and clutch |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008011725A1 (en) | 2007-03-22 | 2008-09-25 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torsional vibration dampers e.g. for torque converter and drive disks, has drive element and drive element transfer element, with cushioning part arranged opposite between each element |
| DE112008002505A5 (en) * | 2007-10-04 | 2010-06-17 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | torsional vibration dampers |
| KR101417453B1 (en) * | 2012-12-06 | 2014-07-08 | 현대자동차주식회사 | Apparatus for damping of flywheel |
| DE102015210164B3 (en) * | 2015-06-02 | 2016-11-03 | Schaeffler Technologies AG & Co. KG | Pulley decoupler with sliding shells |
| DE102017127063A1 (en) | 2016-12-12 | 2018-06-14 | Schaeffler Technologies AG & Co. KG | torsional vibration dampers |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE464931B (en) * | 1989-09-20 | 1991-07-01 | Volvo Ab | FLY WHEELS FOR COMBUSTION ENGINES |
| US6131487A (en) * | 1995-02-03 | 2000-10-17 | Luk Lamellen Und Kupplungsbau Gmbh | Torsional vibration damper |
| DE19758655C2 (en) * | 1996-11-26 | 2002-11-07 | Exedy Corp | Torque converter bridging mechanism damper |
| DE19903033A1 (en) | 1998-01-29 | 1999-08-05 | Unisia Jecs Corp | Torque transmission device for combustion engines |
| JP2000213598A (en) * | 1999-01-25 | 2000-08-02 | Unisia Jecs Corp | Torque transmitting device |
| FR2794832B1 (en) | 1999-06-10 | 2001-09-14 | Valeo | DOUBLE SHOCK ABSORBER FOR MOTOR VEHICLE |
| DE10209409A1 (en) * | 2001-03-08 | 2002-09-12 | Luk Lamellen & Kupplungsbau | Torsional vibration damper esp. divided flywheel has helical pressure spring with windings in one section having smaller outer diameter than windings outside this section |
| JP2004278792A (en) * | 2003-03-13 | 2004-10-07 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | Torsional vibration damper |
-
2006
- 2006-11-15 KR KR1020087010431A patent/KR20080071978A/en not_active Application Discontinuation
- 2006-11-15 WO PCT/DE2006/001997 patent/WO2007062620A1/en active Application Filing
- 2006-11-15 BR BRPI0619162A patent/BRPI0619162B1/en active IP Right Grant
- 2006-11-15 CN CN2006800454614A patent/CN101321969B/en active Active
- 2006-11-15 EP EP06805524A patent/EP1957825A1/en not_active Withdrawn
- 2006-11-15 DE DE112006002997.5T patent/DE112006002997B4/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105452710A (en) * | 2013-08-09 | 2016-03-30 | Zf腓特烈斯哈芬股份公司 | Torsional vibration damping arrangement for the powertrain of a vehicle |
| CN111989507A (en) * | 2018-04-10 | 2020-11-24 | 舍弗勒技术股份两合公司 | Torsional vibration damper, clutch disc and clutch |
| CN111989507B (en) * | 2018-04-10 | 2023-07-14 | 舍弗勒技术股份两合公司 | Torsional vibration damper, clutch plate and clutch |
| US12000453B2 (en) | 2018-04-10 | 2024-06-04 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper, clutch disc, and clutch |
Also Published As
| Publication number | Publication date |
|---|---|
| BRPI0619162A8 (en) | 2016-12-06 |
| WO2007062620A1 (en) | 2007-06-07 |
| EP1957825A1 (en) | 2008-08-20 |
| DE112006002997B4 (en) | 2018-09-27 |
| BRPI0619162B1 (en) | 2019-01-29 |
| KR20080071978A (en) | 2008-08-05 |
| DE112006002997A5 (en) | 2008-09-04 |
| BRPI0619162A2 (en) | 2011-09-20 |
| CN101321969B (en) | 2011-01-12 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
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Owner name: LUKE ASSET MANAGEMENT CO., LTD. Free format text: FORMER OWNER: LUK LAMELLEN UND KUPPLUNGSBAU GMBH Effective date: 20101210 Owner name: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG Free format text: FORMER OWNER: LUKE ASSET MANAGEMENT CO., LTD. Effective date: 20101210 |
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Free format text: CORRECT: ADDRESS; FROM: BULL, GERMAN TO: HERZOGENAURACH, GERMANY |
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