CN101305207B - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
- Publication number
- CN101305207B CN101305207B CN200680041522XA CN200680041522A CN101305207B CN 101305207 B CN101305207 B CN 101305207B CN 200680041522X A CN200680041522X A CN 200680041522XA CN 200680041522 A CN200680041522 A CN 200680041522A CN 101305207 B CN101305207 B CN 101305207B
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- CN
- China
- Prior art keywords
- vibration damper
- torsional vibration
- coupling
- energy
- travelling wave
- 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.)
- Expired - Fee Related
Links
- 230000008878 coupling Effects 0.000 claims abstract description 67
- 238000010168 coupling process Methods 0.000 claims abstract description 67
- 238000005859 coupling reaction Methods 0.000 claims abstract description 67
- 238000004146 energy storage Methods 0.000 claims description 28
- 230000006835 compression Effects 0.000 claims description 18
- 238000007906 compression Methods 0.000 claims description 18
- 239000011159 matrix material Substances 0.000 claims description 15
- 238000007667 floating Methods 0.000 claims description 2
- 239000006096 absorbing agent Substances 0.000 description 2
- 230000003321 amplification Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000036039 immunity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
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
- F16F15/1232—Wound springs characterised by the spring mounting
- F16F15/1234—Additional guiding means for springs, e.g. for support along the body of springs that extend circumferentially over a significant length
-
- 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
- F16F15/10—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
- F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
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)
- Motor Power Transmission Devices (AREA)
- Vibration Prevention Devices (AREA)
- Springs (AREA)
Abstract
The invention relates to a torsional vibration damper, in particular a split flywheel, having at least two centrifugal masses (2,3) which can be rotated counter to the resistance of at least two deformable energy store elements (7,8), in particular coil pressure springs, which are coupled to one another by means of at least one coupling device (24) which, when a first energy store element (7) is deformed, in particular expanded, causes a second energy store element (8) to be driven in a targeted fashion, and which has at least a first and a second driver device (27,28).; In order to prevent undesired rattling during operation of a motor vehicle which is equipped with this torsional vibration damper, the first driver device (27) is coupled to a first coupling slide element (32) which is in turn coupled to the first energy store element (7), and the second driver device (28) is coupled to a second coupling slide element (32) which is in turn coupled to the second energy store element (8).
Description
Technical field
The present invention relates to a kind of torsional vibration damper that has at least two rotating masses, especially split flywheel, described rotating mass can overcome the especially resistance rotation of helical compression spring of at least two deformable energy-storage travelling wave tubes, described energy-storage travelling wave tube is coupled to each other by at least one coupling device, when first energy-storage travelling wave tube deforms when especially unloaded, described coupling device is on purpose taken second energy-storage travelling wave tube and is had at least one and first takes device and one second and take device.
Summary of the invention
The objective of the invention is to prevent to be furnished with jolting that the automobile of torsional vibration damper is in operation and occurs not expecting.
For a kind of torsional vibration damper that has at least two rotating masses, especially split flywheel, described rotating mass can overcome the especially resistance rotation of helical compression spring of at least two deformable energy-storage travelling wave tubes, described energy-storage travelling wave tube is coupled to each other by at least one coupling device, when first energy-storage travelling wave tube deforms when especially unloaded, described coupling device is taken second energy-storage travelling wave tube targetedly and is had at least one and first takes device and one second and take device, described purpose realizes like this, described first takes device connects with one first coupling sliding element, the described first coupling sliding element connects with described first energy-storage travelling wave tube again, and described second takes device connects with one second coupling sliding element, and the described second coupling sliding element connects with described second energy-storage travelling wave tube again.Within the scope of the present invention original torsional vibration damper is tested discovery, when rotating speed is very high, traction travel and inertia traveling between alternately in energy-storage travelling wave tube be subjected to frictional force action and keep static, and the output block of torque vibration vibration damper moves along the inertia traveling direction.In the process that rotating speed descends, energy-storage travelling wave tube is upspring when reaching certain rotating speed.If energy-storage travelling wave tube is upspring, between described rotating speed, just form so-called dynamic unbalance so when different rotating speeds.By connecting of coupling sliding element and coupling device, can prevent do not expect static of energy-storage travelling wave tube and upspring according to of the present invention.
A kind of preferred embodiment of described torsional vibration damper is characterised in that, described coupling sliding element is made of a sliding element in a plurality of sliding elements respectively, when torsional vibration damper was subjected to tension load, a described sliding element at first moved together with corresponding energy-storage travelling wave tube.Energy-storage travelling wave tube is preferably arc helical compression spring.Described coupling sliding element is preferably along the energy-storage travelling wave tube of the described correspondence that radially is arranged on torsional vibration damper and the piston shoes between elementary rotating mass or the input block.
The another kind of preferred embodiment of described torsional vibration damper is characterised in that described coupling sliding element relatively is provided with on diameter on the circumference.It is especially favourable that this set is proved to be within the scope of the present invention.
The another kind of preferred embodiment of described torsional vibration damper is characterised in that, described coupling sliding element is arranged between two driving dactylitic pieces that stretch out from coupling device.In addition, described coupling sliding element also can set the hole, and the driving dactylitic piece that stretches out from coupling device is coupled to the described hole.
The another kind of preferred embodiment of described torsional vibration damper is characterised in that described driving dactylitic piece radially extends inwards or along axial direction from coupling device.Realize the installation of auxiliary interior vibration damper thus.
The another kind of preferred embodiment of described torsional vibration damper is characterised in that described coupling device comprises annular matrix, and described driving dactylitic piece stretches out from this annular matrix.Preferably described coupling device one is designed to thin-plate member.
The another kind of preferred embodiment of described torsional vibration damper is characterised in that described annular matrix has bent angle shape cross section.Realize the stable support of coupling device thus.
The another kind of preferred embodiment of described torsional vibration damper is characterised in that described annular matrix floating ground (schwimmend) is supported between the elementary rotating mass and described sliding element of this torsional vibration damper.
Other advantage of the present invention, feature and details are learnt from explanation following, that describe different embodiments with reference to the accompanying drawings.
Description of drawings
Fig. 1 shows torsional vibration damper according to first embodiment in the mode of semi-section;
Fig. 2 shows as shown in Figure 1 torsional vibration damper in the mode in cross section;
Fig. 3 is the view that is similar to Fig. 1 according to second embodiment;
Fig. 4 is the view that is similar to Fig. 2 according to second embodiment;
Fig. 5 has illustrated coupling ring according to first embodiment with stereogram;
Fig. 6 shows coupling ring among Fig. 5 in the mode of plan view;
Fig. 7 is along the sectional view of line VII-VII among Fig. 6;
Fig. 8 shows coupling ring in the mode of front view;
Fig. 9 is the amplification detail drawing of IX part among Fig. 8;
Figure 10 has illustrated coupling ring according to second embodiment with stereogram;
Figure 11 shows coupling ring among Figure 10 in the mode of plan view;
Figure 12 is the sectional view of the line XII-XII in Figure 11; With
Figure 13 is the amplification detail drawing of the XIII part of Figure 11.
Embodiment
Constitute the flywheel 1 of split in Fig. 1 and 2 with the torsional vibration damper shown in the different views, described flywheel has first or elementary rotating mass 2 and one second or the secondary rotating mass 3 that can be fixed on the unshowned internal combustion engine drive axle.Friction clutch is fixed on described second rotating mass 3, is provided with clutch driven plate between this friction clutch and second rotating mass, can engage and throw off same unshowned transmission input shaft by described friction clutch.Described elementary rotating mass 2 is also referred to as the input block of torsional vibration damper.Described secondary mass 3 is also referred to as the output block of torsional vibration damper.
Described two rotating masses 2 and 3 can support each other with the relative rotation by support device 4.In described embodiment, support device 4 be arranged on the hole 5 that is used to pass fastening screw trip bolt radially outside, described fastening screw trip bolt is used for described first rotating mass is assembled to the internal combustion engine drive axle.The vibration damping equipment 6 that comprises energy-storage travelling wave tube acts between described two rotating masses 2 and 3, and described energy-storage travelling wave tube is made of helical compression spring 7,8 again.Within helical compression spring 7,8, be provided with an interior vibration damper 11 diametrically with helical compression spring 12.Described helical compression spring 7,8 is the crooked and covering angular ranges of 180 degree nearly that extend respectively along circumferencial direction.Described two helical compression springs 7 and 8 radially relatively are provided with on circumference.
Described two rotating masses 2 and 3 have the loading zone 14,15,16 that is used for energy-storage travelling wave tube 7,8.Described loading zone 14,15 is configured on the elementary rotating mass 2 at input side.Loading zone 16 is separately positioned between loading zone 14 and 15 at outlet side.In addition, described loading zone 16 links to each other with secondary rotating mass 3 by riveted joint element 21 via flange-type loading component 20.Described flange-type loading component 20 plays the effect of the moment of torsion transmitting element between accumulator 7,8 and secondary rotating mass 3.Described flange-type loading component 20 is also referred to as output block.
Elementary rotating mass 2 links to each other with hub-type parts 10 by so-called disturbing property plate (flex plate) 9 nothings with relatively rotating.Described two helical compression springs 7 and 8 are coupled to each other by coupling device or by coupling ring 24.
Described coupling device 24 illustrates with various views in Figure 10 to 13.Described coupling device 24 comprises annular matrix 25 and therefore is also referred to as coupling ring.As shown in figure 12, described coupling ring 24 has bent angle shape cross section.Two drive dactylitic piece and radially extend inwards from annular matrix 25 27,28 and 29,30.Described two drive dactylitic piece to radially relatively being provided with on circumference.
As shown in Figure 2, helical compression spring 7 links to each other with eight piston shoes 34 to 41 with coupling sliding element 31.Described coupling sliding element 31 and piston shoes 34 to 41 are arranged on outside the helical compression spring 7 diametrically.Coupling sliding element 31 connects with coupling ring 24 by partly enclosing the driving dactylitic piece 27,28 that is acting on this coupling sliding element.Another coupling sliding element 32 connects with coupling ring 24 by driving dactylitic piece 29,30.
Figure 3 illustrates the embodiment who is similar to Fig. 1.Use identical reference character to represent identical parts.For fear of repetition, please refer to the above description of Fig. 1.Below only describe with regard to the difference between described two embodiments.
In the embodiment shown in fig. 3, helical compression spring 7,8 is coupled to each other by coupling ring 64.Described coupling ring 64 has an annular matrix 65, and this annular matrix has the cross section of bent angle shape.
As shown in Figure 4, coupling sliding element 71 in driving dactylitic piece 67, the 68 outer peripheral effects diametrically of stretching out from coupling ring 64.Described coupling sliding element 71 connects with helical compression spring 7.In addition, eight piston shoes 74 to 81 connect with helical compression spring 7.
Fig. 5 to 9 shows coupling device 64 in the mode of various views.As shown in Figure 7, coupling device 64 is made of the annular matrix 65 with bent angle shape cross section.Two pairs drive dactylitic piece 67,68 and 69,70 and extend along axial direction from described annular matrix 65.As shown in Figure 5, described driving dactylitic piece is to radially relatively being provided with on circumference.
List of numerals
1. flywheel 30. drives finger
2. rotating mass 31. coupling sliding members
3. rotating mass 32. coupling sliding members
4. bracing or strutting arrangement 34. piston shoes
5. hole 35. piston shoes
6. vibration absorber 36. piston shoes
7. helical compression spring 37. piston shoes
8. helical compression spring 38. piston shoes
9. immunity plate 39. piston shoes
10. hub-type parts 40. piston shoes
11. interior shock absorber 41. piston shoes
12. helical compression spring 64. coupling rings
14. loading zone 65. matrixes
15. loading zone 67. drives dactylitic piece
16. loading zone 68. drives dactylitic piece
20. loading component 69. drives dactylitic piece
21. riveting set 70. drives dactylitic piece
24. coupling ring 71. coupling sliding elements
25. matrix 74. piston shoes
28. drive dactylitic piece 75. piston shoes
29. drive dactylitic piece 76. piston shoes
77. piston shoes 80. piston shoes
78. piston shoes 81. piston shoes
79. piston shoes
Claims (12)
1. the resistance that torsional vibration damper that has at least two rotating masses (2,3), described rotating mass can overcome at least two deformable energy-storage travelling wave tubes (7,8) rotates, and described rotating mass is by at least one coupling device (24; 64) be coupled to each other, when one first energy-storage travelling wave tube (7) was out of shape, this coupling device was on purpose taken one second energy-storage travelling wave tube (8) and is had at least one and first takes device (27,28; 67,68) and one second take device (28,29; 69,70), it is characterized in that described first takes device (27,28; 67,68) connect with one first coupling sliding element (31), this first coupling sliding element connects with described first energy-storage travelling wave tube (7) again, and described second takes device (28,29; 69,70) connect with one second coupling sliding element (32), this second coupling sliding element connects with described second energy-storage travelling wave tube (8) again.
2. according to the torsional vibration damper of claim 1, it is characterized in that: these coupling sliding elements (31,32) are respectively by a plurality of sliding element (34-41; Such sliding element 74-81) constitutes, and this sliding element at first moves with corresponding energy-storage travelling wave tube (7) when torsional vibration damper is subjected to tension load together.
3. each torsional vibration damper in requiring according to aforesaid right, it is characterized in that: these coupling sliding elements (31,32) radially relatively are provided with on circumference.
4. according to the torsional vibration damper of claim 1 or 2, it is characterized in that: these coupling sliding elements (31,32) are arranged on two from described coupling device (24; 64) between the driving dactylitic piece that stretches out (27-30,67-70).
5. according to the torsional vibration damper of claim 4, it is characterized in that: these drive dactylitic piece (27-30) and extend radially inwardly from described coupling device (24).
6. according to 4 torsional vibration damper in the claim, it is characterized in that: described driving dactylitic piece (67-70) extends along axial direction from described coupling device (64).
7. torsional vibration damper according to claim 5 is characterized in that:
Described coupling device (24; 64) comprise an annular matrix (25; 65), these drive dactylitic piece (27-30; 67-70) stretch out from this annular matrix.
8. torsional vibration damper according to claim 7 is characterized in that: described annular matrix (25; 65) has the cross section of bent angle shape.
9. torsional vibration damper according to claim 7 is characterized in that: described annular matrix floating ground is supported on elementary rotating mass (2) and these sliding elements (31,32 of this torsional vibration damper; 34-41; 74-81).
10. according to the torsional vibration damper of claim 1, it is characterized in that: described torsional vibration damper is the split flywheel.
11. the torsional vibration damper according to claim 1 is characterized in that: described energy-storage travelling wave tube is a helical compression spring.
12. the torsional vibration damper according to claim 1 is characterized in that: described first energy-storage travelling wave tube (7) distortion is to occur when unloaded.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102005058842.5 | 2005-12-09 | ||
| DE102005058842 | 2005-12-09 | ||
| PCT/DE2006/002030 WO2007065393A1 (en) | 2005-12-09 | 2006-11-20 | Torsional vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101305207A CN101305207A (en) | 2008-11-12 |
| CN101305207B true CN101305207B (en) | 2010-07-21 |
Family
ID=37744666
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200680041522XA Expired - Fee Related CN101305207B (en) | 2005-12-09 | 2006-11-20 | Torsional vibration damper |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP1960689A1 (en) |
| KR (1) | KR20080074091A (en) |
| CN (1) | CN101305207B (en) |
| BR (1) | BRPI0619768A8 (en) |
| DE (1) | DE112006002814B4 (en) |
| WO (1) | WO2007065393A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1866538B1 (en) * | 2005-03-26 | 2012-01-18 | Schaeffler Technologies AG & Co. KG | Compound transmission |
| DE102011101129A1 (en) | 2011-05-11 | 2012-11-15 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper for arrangement between internal combustion engine and electric motor in hybrid drive train of motor vehicle, has first damper stages arranged radially within second damper stage and connected in parallel state |
| WO2014114281A1 (en) * | 2013-01-23 | 2014-07-31 | Schaeffler Technologies AG & Co. KG | Helical compression spring and torsional vibration damper |
| US10352396B2 (en) | 2014-02-27 | 2019-07-16 | Exedy Corporation | Damper device |
| DE102018125615A1 (en) * | 2018-10-16 | 2020-04-16 | Schaeffler Technologies AG & Co. KG | Centrifugal pendulum |
| US11703103B2 (en) * | 2021-09-02 | 2023-07-18 | Schaeffler Technologies AG & Co. KG | Torque converter damper assembly |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4722715A (en) * | 1985-01-29 | 1988-02-02 | Valeo | Torsional damper device |
| US6371857B1 (en) * | 1999-01-25 | 2002-04-16 | Unisia Jecs Corporation | Torsional vibration dampers |
| CN1374466A (en) * | 2001-03-08 | 2002-10-16 | 卢克摩擦片和离合器两合公司 | Torsional vibration absorber |
| CN1126882C (en) * | 1998-03-25 | 2003-11-05 | 卢克摩擦片和离合器有限公司 | Torsional vibration damper and helical compression spring for torsional vibration damper |
| JP3500506B2 (en) * | 1991-05-23 | 2004-02-23 | ヴァレオ | Automotive torsion damper |
| CN1187540C (en) * | 2000-06-20 | 2005-02-02 | 哈瑟&弗雷德有限公司 | Method for producing torsional vibration damper housing, especially housing for viscosity torsional vibration damper |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19758942B4 (en) * | 1997-08-01 | 2009-01-29 | Zf Sachs Ag | torsional vibration damper |
| FR2830915B1 (en) * | 2001-10-16 | 2004-03-12 | Valeo | DOUBLE SHOCK ABSORBER IN PARTICULAR FOR MOTOR VEHICLE |
| JP2004278792A (en) * | 2003-03-13 | 2004-10-07 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | Torsional vibration damper |
-
2006
- 2006-11-20 DE DE112006002814.6T patent/DE112006002814B4/en not_active Expired - Fee Related
- 2006-11-20 BR BRPI0619768A patent/BRPI0619768A8/en active Search and Examination
- 2006-11-20 CN CN200680041522XA patent/CN101305207B/en not_active Expired - Fee Related
- 2006-11-20 WO PCT/DE2006/002030 patent/WO2007065393A1/en active Application Filing
- 2006-11-20 EP EP06828535A patent/EP1960689A1/en not_active Withdrawn
- 2006-11-20 KR KR1020087006870A patent/KR20080074091A/en not_active Application Discontinuation
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4722715A (en) * | 1985-01-29 | 1988-02-02 | Valeo | Torsional damper device |
| JP3500506B2 (en) * | 1991-05-23 | 2004-02-23 | ヴァレオ | Automotive torsion damper |
| CN1126882C (en) * | 1998-03-25 | 2003-11-05 | 卢克摩擦片和离合器有限公司 | Torsional vibration damper and helical compression spring for torsional vibration damper |
| US6371857B1 (en) * | 1999-01-25 | 2002-04-16 | Unisia Jecs Corporation | Torsional vibration dampers |
| CN1187540C (en) * | 2000-06-20 | 2005-02-02 | 哈瑟&弗雷德有限公司 | Method for producing torsional vibration damper housing, especially housing for viscosity torsional vibration damper |
| CN1374466A (en) * | 2001-03-08 | 2002-10-16 | 卢克摩擦片和离合器两合公司 | Torsional vibration absorber |
Non-Patent Citations (1)
| Title |
|---|
| 王砚红.汽车动力传动系双质量飞轮式扭振减振器的结构设计与动力学特性研究.中国优秀硕士学位论文全文数据库.2005,2-8. * |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2007065393A1 (en) | 2007-06-14 |
| DE112006002814A5 (en) | 2008-08-28 |
| KR20080074091A (en) | 2008-08-12 |
| BRPI0619768A8 (en) | 2016-12-06 |
| DE112006002814B4 (en) | 2016-07-21 |
| EP1960689A1 (en) | 2008-08-27 |
| CN101305207A (en) | 2008-11-12 |
| BRPI0619768A2 (en) | 2011-10-18 |
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