CN103375531A - Centering element for torsional vibration damper and torsional vibration damper provided with centering element - Google Patents
Centering element for torsional vibration damper and torsional vibration damper provided with centering element Download PDFInfo
- Publication number
- CN103375531A CN103375531A CN2013102218872A CN201310221887A CN103375531A CN 103375531 A CN103375531 A CN 103375531A CN 2013102218872 A CN2013102218872 A CN 2013102218872A CN 201310221887 A CN201310221887 A CN 201310221887A CN 103375531 A CN103375531 A CN 103375531A
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- Prior art keywords
- centring element
- dead slot
- vibration damper
- torsional vibration
- section
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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
- F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
Abstract
The invention relates to a centering element for a torsional vibration damper, particularly a centering element for a dual-mass flywheel, wherein the torsional vibration damper comprises an input part, an output part and a rotational axis. The input part is centrally provided with a first recess relative to the rotational axis. The output part is centrally provided with a second recess relative to the rotational axis. The input part and the output part are rotatable together around the rotational axis and are rotatable relative to each other in a limited manner. The centering element comprises a first centering section assigned to the first recess, and a second centering portion assigned to the second recess. The invention also discloses the above torsional vibration damper provided with the centering element. In this way, the centering properties of both the input part and the output part of the torsional vibration damper, particularly at mounting positions, are improved. The torsional vibration damper is improved structurally and / or functionally.
Description
Technical field
The present invention relates to for torsional vibration damper, centring element in particular for double mass flywheel, described torsional vibration damper has: input block and output block, spin axis, the first dead slot that on described input block, arranges about heart in the described spin axis and the second dead slot that on described output block, arranges about heart in the described spin axis, described input block and described output block can jointly rotate and can limitedly reverse toward each other around described spin axis, and relate to a kind of torsional vibration damper with this centring element.
Background technique
Disclose the double clutch that is used for Motor Vehicle, has following characteristics by DE102009024217A1, described double clutch has oil-resisting housing; This housing can not be connected with the bent axle of internal-combustion engine with relatively rotating; At least one torsional vibration damper, two wet clutches and a centrifugal force pendulum are set in this housing; These wet clutches have each input block and each output block; The input block of these wet clutches interconnects; The output block of these wet clutches can not be connected with transmission input shaft with relatively rotating; In the power stream of the input block from the housing to the wet clutch vibration damper is set, wherein, the input block of this torsional vibration damper is connected with housing, and the output block of this vibration damper is connected with the input block of this wet clutch; Input block at wet clutch arranges centrifugal force pendulum.According to DE102009024217A1, described torsional vibration damper can not be received in with relatively rotating on the bent axle of spin axis rotation and be constructed to have the primary components that is fixedly connected with described bent axle and the double mass flywheel of secondary parts.This output block is connected with the input block rotation of wet clutch in locking manner by the tooth section of packing at the wheel hub of input block as the secondary parts of double mass flywheel.
Summary of the invention
Task of the present invention is, realizes or improve input block and the especially centering in the mounting point of output block of the described torsional vibration damper of beginning, and structurally and/or improve the described torsional vibration damper of beginning on the function.
Described task is to be used for torsional vibration damper, centring element in particular for double mass flywheel solves, described torsional vibration damper has: input block and output block, spin axis, the first dead slot that on described input block, arranges about heart in the described spin axis and the second dead slot that on described output block, arranges about heart in the described spin axis, described input block and described output block can jointly rotate and can limitedly reverse toward each other around described spin axis, wherein, described centring element has and attaches troops to a unit in the first centering section of described the first dead slot and attach troops to a unit in the second centering section of the second dead slot.
This centring element can have spin axis.This centring element can have rotational symmetric shape.The first centering section and the second centering section can sequentially arrange on the bearing of trend of spin axis mutually.
Can realize especially mutual location, centering ground in the mounting point of the input block of torsional vibration damper and output block according to centring element of the present invention.Can realize that torsional vibration damper is connected without any problems with internal-combustion engine.The input block that can realize torsional vibration damper is connected without any problems with the bent axle of internal-combustion engine.Can realize that torsional vibration damper is connected without any problems with speed changer.The output block that can realize torsional vibration damper is connected without any problems with the input shaft of speed changer.Can realize feeling relieved with lower cost.Can realize feeling relieved with higher degree of accuracy.Can realize the assembling capacity of the automation of torsional vibration damper.Can be implemented in the short-and-medium cycle of installation process.Reduced the risk of damaging.Can realize the torsional vibration damper that is installed on the internal-combustion engine is tested.Torsional vibration damper with can realize centering by centring element during speed changer is connected.This centring element needn't be removed.This centring element can be felt relieved in the mounting point reliably.This centring element can remain in the mounting point reliably.This centring element can move in running position reliably.This centring element can remain in the running position reliably.This centring element can be displaced in the running position by the mounting point.Stoped the direction of centring element from running position towards the mounting point unexpectedly to be shifted.
This centring element can have ring segment, and the first centering section and the second centering section can form with ring segment.This centring element can have the surface of pointing to radially outer.The surface of this centring element sensing radially outer can have the shape of cylindricality.The surface that this centring element points to radially outer can be columniform shape.The surface that this centring element points to radially outer can have the first paragraph that consists of the first centering section.The surface that this centring element points to radially outer can have the second segment that consists of the second centering section.This first centering section and the second centering section can have roughly the same at least outer diameter.This first centering section can have identical outer diameter with the second centering section.This first centering section can have than the large outer diameter of the second centering section.
This centring element can have towards the second centering section direction section of reclining that point to, middle heart setting.This section of reclining can have towards the abutment face of the direction of the second centering section of the bearing of trend sensing of spin axis.By this section of reclining this centring element is displaced to the running position from the mounting point.This section of reclining can be attached troops to a unit in the input shaft of speed changer.This abutment face can so be located with respect to the first centering section and/or with respect to the second centering section on the bearing of trend of spin axis, so that centring element can be displaced to the running position from the mounting point when speed changer is installed.This abutment face can vertically arrange about spin axis.This abutment face can have circular shape.This abutment face can be flat.
Centring element can have at least one and surpass the outstanding locking section of the second centering section radial outer surface towards radially outer.This centring element can have a plurality of locking sections.These locking sections can arrange with distributing at the circumferencial direction of centring element.These locking sections can arrange on the circumferencial direction of centring element evenly distributedly.Centring element can have three locking sections.At least one locking section can be used for centring element is remained on the mounting point.At least one locking section can be used for centring element is remained on running position.At least one locking section can arrange on elastic displacement ground on centring element.At least one locking section can arrange towards inner radial elastic movement ground.Therefore at least one locking section is unclamped.At least one locking section can have stop boss.This stop boss can have slope section.This slope section can point to the first centering section.This stop boss can have the locking section.This locking section can be pointed to the second centering section.
The solution of the above-mentioned task of the present invention realizes with torsional vibration damper, especially double mass flywheel, described torsional vibration damper has: input block and output block, spin axis, the first dead slot that on described input block, arranges about heart in the described spin axis and the second dead slot that on described output block, arranges about heart in the described spin axis, described input block and described output block can jointly rotate and can limitedly reverse toward each other around described spin axis, wherein, arrange according to centring element of the present invention in the inside of the first dead slot and/or the second dead slot.
This torsional vibration damper can be arranged in the power train of oil-engine driven Motor Vehicle.This power train can have internal-combustion engine.This internal-combustion engine can have bent axle.This power train has friction clutch device.This friction clutch device can have single clutch.This friction clutch device can have double clutch.This power train can have speed changer.This speed changer can have at least one input shaft.Torsional vibration damper can be arranged in power train between internal-combustion engine and the friction clutch device.Torsional vibration damper can be arranged in power train between internal-combustion engine and the speed changer.Torsional vibration damper can be used for damps torsional vibrations.Torsional vibration especially can be by internal-combustion engine the process in cycle cause.Spring-vibration damper-device can act between input block and output block.Spring-vibration damper-device can have spring assembly.This spring assembly can have at least one accumulator.This spring assembly can have at least one arc spring.This spring-vibration damper-device can have rubbing device.Torsional vibration damper can have the centrifugal force pendulum device.
The input block of torsional vibration damper also can be called primary components.The output block of torsional vibration damper also can be called secondary parts.Input block can have the flange section.The flange section of this input block can be used for torsional vibration damper is connected with the bent axle of internal-combustion engine.The first dead slot can be arranged on the flange section of input block.The first dead slot can have circular shape.The first dead slot can have the surface of pointing to inner radial.The surface of this first dead slot can have the shape of cylindricality.The surface of this first dead slot can have columniform shape.The surface of this first dead slot can have the first inner diameter.This output block can have the flange section.The flange section of this output block can be used for torsional vibration damper is connected with the input shaft of speed changer.This second dead slot can be arranged on the flange section of output block.This second dead slot can have the shape of type exterior feature.This second dead slot can have the hub type exterior feature.This second dead slot can have the surface section of pointing to inner radial.The surface section of this second dead slot sensing inner radial can define the reception shape of cylindricality.The surface section that this second dead slot points to inner radial can define columniform reception shape.This second dead slot can have the second inner diameter.This second inner diameter can point to the second dead slot the surface section formation of inner radial.This first inner diameter and the second inner diameter can equate.This first inner diameter can be larger than the second inner diameter.On the bearing of trend of spin axis, can between the first dead slot and the second dead slot, form the gap.On the bearing of trend of spin axis, can between the first dead slot and the second dead slot, be formed for the gap of at least one locking section of centring element.
The outer diameter of the first centering section can be at least generally corresponding with the first inner diameter of torsional vibration damper.Between the first inner diameter of the outer diameter of the first centering section and torsional vibration damper, can form cooperation.The outer diameter of the second centering section can be at least generally corresponding with the second inner diameter of torsional vibration damper.Between the second inner diameter of the outer diameter of the second centering section and torsional vibration damper, form and cooperate.
In the mounting point, centring element can be arranged on the first dead slot inside and be arranged on the second dead slot with the second centering section inner with the first centering section.In this mounting point, described at least one locking section is between the input block and output block that can be arranged on torsional vibration damper on the bearing of trend of spin axis.
In running position, centring element can be arranged on the first dead slot inside and the second dead slot can be released.In this running position, described at least one locking section can be arranged on input block dorsad on the side of the output block of torsional vibration damper on the bearing of trend of spin axis.In this running position, described at least one locking section can stop centring element to be moved back in the mounting point.
Generally speaking and in other words, by the present invention, drawn thus the other centring element that is used for vibration damper.This centring element can be by plastics or similar material manufacturing.This centring element can be installed between the primary components and wheel hub of vibration damper.This centring element can be felt relieved by resilient key on primary components.Utilization less gap between centring element and wheel hub can be guaranteed by the desired fit up gap of the tolerance chain of speed changer.This vibration damper can be exported in this state.This centring element can at first reduce the dislocation between primary components and the secondary parts, so vibration damper can be screwed on the motor automatically.In this state, vibration damper can carry out self-alignment for the axle to different engine test stands and secondary parts are led.Secondary parts can slide and rotation at the centering part at duration of test.Then, when speed changer was installed, transmission shaft can mesh at once by dislocation and the wheel hub that reduces between primary components and the secondary parts.Then, speed changer can be pushed into the face of being spirally connected at cluster engine.Thus, transmission shaft can be between bent axle and primary components mobile centring element.By the locking wedge spare on pin, centring element can snap on the described position when operation.Permissible error and axial motion by speed changer can realize that transmission shaft also touches centring element sometimes when operation.But centring element can so dispose, so that above-mentioned contact only occurs over just on the very little diameter, consequent friction is harmless.
Utilize " can " especially represent the optional feature of the present invention.Therefore specific embodiments of the invention comprise respectively corresponding feature or corresponding some features.
Description of drawings
Illustrate in greater detail embodiments of the invention below with reference to accompanying drawing.Draw further feature and advantage by specification.Embodiment's specific features can illustrate general features of the present invention.Utilize embodiment's feature relevant with further feature that the single feature of the present invention also can be shown.
It schematically and exemplarily illustrates:
Fig. 1: with sectional drawing the double mass flywheel with centring element has been shown and has been arranged in the mounting point;
Fig. 2: show double mass flywheel on I. C. engine crankshaft, that have centring element and be arranged in the mounting point;
Fig. 3: show test during internal-combustion engine double mass flywheel on I. C. engine crankshaft, that have centring element be arranged in the mounting point;
Fig. 4: show double mass flywheel between I. C. engine crankshaft and transmission input shaft, that have centring element and be arranged in running position; And
Fig. 5: show centring element for double mass flywheel with perspective view.
Embodiment
Fig. 1 has illustrated the double mass flywheel 100 with centring element 102 with sectional drawing and has been arranged in the mounting point.The double mass flywheel 100 that Fig. 2 shows on I. C. engine crankshaft 104 is arranged in the mounting point.Fig. 3 show test during internal-combustion engine the double mass flywheel 100 on bent axle 104 be arranged in the mounting point.The double mass flywheel 100 that Fig. 4 shows between I. C. engine crankshaft 104 and transmission input shaft 106 is arranged in running position.
Output block 110 has flange components 128.Flange components 128 has the shape of dish type.Flange components 128 has with porose orifice ring, such as 130.These holes 130 are used for packing into bolt 124.The orifice ring of the flange components 128 of output block 110 is corresponding with the orifice ring of the flange section 120 of input block 108.Output block 110 has the dead slot 132 that arranges about heart in the spin axis 112.Dead slot 132 has the hub type exterior feature.Dead slot 132 has the surface section of pointing to inner radial.The surface section that dead slot 132 points to inner radial defines columniform reception shape.Dead slot 132 has inner diameter.The inner diameter of dead slot 132 forms by the surface section that dead slot 132 points to inner radial.
The dead slot 126 of input block 108 has identical inner diameter with the dead slot 132 of output block 110.On the bearing of trend of spin axis 112, the dead slot 126 of input block 108 and the dead slot of output block 110 132 are by space like this, to such an extent as to form a gap 134.
Fig. 5 shows centring element 200 for double mass flywheel with perspective view, and described centring element is as according to the centring element 102 of Fig. 1, Fig. 2, Fig. 3 and Fig. 4, and described double mass flywheel is as according to the double mass flywheel 100 of Fig. 1, Fig. 2, Fig. 3 and Fig. 4.
Centring element 200 has ring segment 202 at radially outer.Ring segment 202 has the surface 204 of pointing to radially outer.Centring element 200 has attaches troops to a unit in the side 206 of internal-combustion engine and attaches troops to a unit in the side 208 of speed changer.Be formed for the centering section 210 of the input block of double mass flywheel in internal combustion engine side with the surface 204 of pointing to radially outer.Be formed for the centering section 212 of the output block of double mass flywheel in transmission side with the surface 204 of pointing to radially outer.Ring segment 202 has outer diameter.Ring segment 202 be used on the centering section 210 of input block outer diameter with identical for the outer diameter on the centering section 212 of output block.The outer diameter of ring segment 202 is so measured, and cooperates so that form respectively with the inner diameter of the dead slot of input block and with the inner diameter of the dead slot of output block.Described cooperation is so measured, so that guaranteed on the one hand the mutually fully centering and guaranteed on the other hand assembling capacity of input block and output block.
Centring element 200 has the section of reclining 214 in inner radial.The section of reclining 214 has the abutment face 216 of pointing to transmission side 208 directions.Abutment face 216 vertically arranges about the spin axis of centring element 200.The spin axis of centring element 200 is corresponding with the spin axis of double mass flywheel.The section of reclining 214 has the shape of truncated cone shape.Centring element 200 has dish type section 218.Dish type section 218 is connected ring segment 202 with the section of reclining 214 of centring element 200.Dish type section 218 is arranged on the transmission side 208 of centring element 200.
The locking section that centring element 200 has a plurality of (being three here) arranges in a circumferential direction evenly distributedly, such as 220.These locking sections 220 have respectively the stop boss of the surface 204 that exceeds ring segment 202 stretching out towards radially outer, such as 222.These stop boss 222 have slope section and have the locking section in transmission side in internal combustion engine side respectively.These locking sections 220 have respectively the L shaped shape with two legs.A leg is arranged in the plane with dish type section 218 and with dish type section 218 and is connected.Another leg is arranged in the plane with ring segment 202 and has freely end, and stop boss 222 is arranged on the free end of this leg.These locking sections 220 can so flexibly be sprung into respectively, so that stop boss 222 is shifted towards inner radial.Centring element 200 is by the plastics manufacturing.
In Fig. 1, centring element 102 is arranged in the dead slot 126 of input block 108 with the centering section of firing pusher side within it in the mounting point and is arranged on the centering section in its transmission side in the dead slot 132 of output block 110.The stop boss of centring element 102 stretches in the gap 134 towards radially outer.Therefore, input block 108 and output block 110 mutual centering and centring element 102 are held.In Fig. 2, double mass flywheel 100 is installed on the bent axle 104 of internal-combustion engine by bolt 124.Centring element 102 is arranged in the mounting point unchangeably.In Fig. 3, the internal-combustion engine with the double mass flywheel 100 that is installed on the bent axle 104 is positioned on the test stand.The dead slot 132 that the live axle 136 of test stand is arranged on output block 110 does not have in the section of centring element 102.The live axle 136 of test stand drives with output block 110 and is connected.Centring element 102 is arranged in the mounting point unchangeably.Cooperating between centring element 102 and input block 108 and output block 110 so measured, so that input block 108 and output block 110 are reversed toward each other.In Fig. 4, speed changer is installed on internal-combustion engine and the double mass flywheel 100.The input shaft 106 of speed changer is pushed in the dead slot 132 of output block 110.At this, input shaft 106 makes centring element 102 move into the running position from the mounting point towards the internal-combustion engine direction.Stop boss at first flexibly springs into and then again ejects in running position.In running position, centring element 102 with the locking section of stop boss be supported on input block 108 on the side of internal-combustion engine.Therefore, centring element 102 is maintained in the running position.Centring element 102 is measured by like this towards speed changer and the surface that contacts with input shaft 106 littlely, so that be in operation input block 108 and output block 110 is reversed toward each other.
Reference numerals list
100 double mass flywheels
102 centring elements
104 bent axles
106 input shafts
108 input blocks
110 output blocks
112 spin axiss
114 arc springs
116 rubbing devices
118 centrifugal force pendulum devices
120 flange sections
122 holes
124 bolts
126 input block dead slots
128 flange components
130 holes
132 output block dead slots
134 gaps
136 test stand live axles
200 centring elements
202 ring segments
204 radial outer surface
206 internal combustion engine side
208 transmission side
The centering section of 210 internal combustion engine side
The centering section of 212 transmission side
214 sections of reclining
216 abutment face
218 dish type sections
220 locking sections
222 stop boss
Claims (10)
1. centring element (102,200), be used for torsional vibration damper, in particular for double mass flywheel (100), described torsional vibration damper has: input block (106) and output block (110), spin axis (112), described input block (106) upper about described spin axis (112) in the first dead slot (126) of arranging of heart and described output block (110) upper about described spin axis (112) in second dead slot (132) of heart setting, described input block (106) and described output block (110) can jointly rotate and can limitedly reverse toward each other around described spin axis, wherein, described centring element (102,200) has attaches troops to a unit in the first centering section (210) of described the first dead slot (126) and attaches troops to a unit in the second centering section (212) of described the second dead slot (132).
2. centring element (102 according to claim 1,200), it is characterized in that, described centring element (102,200) have ring segment (202), and described the first centering section (210) and described the second centering section (212) form by described ring segment (202).
3. according to each described centring element (102,200) in the claims, it is characterized in that described the first centering section (210) and described the second centering section (212) have roughly the same at least outer diameter.
4. according to each described centring element (102 in the claims, 200), it is characterized in that described centring element (102,200) has towards the direction of described the second centering section (212) section of reclining (214) that point to, middle heart setting.
5. according to each described centring element (102 in the claims, 200), it is characterized in that, described centring element (102,200) has at least one outstanding locking section (220) of radial outer surface (204) that surpasses described the second centering section (212) towards radially outer.
6. centring element according to claim 5 (102,200) is characterized in that, at least one described locking section (220) can be arranged on the described centring element (102,200) elastic displacement.
7. each described centring element (102,200) in 6 according to claim 5 is characterized in that at least one described locking section (220) has stop boss (222).
8. torsional vibration damper, especially double mass flywheel (100), it has: input block (106) and output block (110), spin axis (112), described input block (106) upper about described spin axis (112) in the first dead slot (126) of arranging of heart and described output block (110) upper about described spin axis (112) in second dead slot (132) of heart setting, described input block (106) and described output block (110) can jointly rotate and can limitedly reverse toward each other around described spin axis (112), it is characterized in that, each described centring element (102,200) in described the first dead slot (126) and/or described the second dead slot (132) inside arrange according to the claims.
9. torsional vibration damper according to claim 8, it is characterized in that, in the mounting point, described centring element (102,200) utilizes described the first centering section (210) to be arranged on described the first dead slot (126) inside and utilizes described the second centering section (212) to be arranged on described the second dead slot (132) inside.
10. each described torsional vibration damper in 9 according to claim 8, it is characterized in that, in running position, described centring element (102,200) is arranged on described the first dead slot (126) inside and described the second dead slot (132) is released.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012206136.3 | 2012-04-16 | ||
| DE102012206136 | 2012-04-16 | ||
| DE1020122061363 | 2012-04-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103375531A true CN103375531A (en) | 2013-10-30 |
| CN103375531B CN103375531B (en) | 2017-03-01 |
Family
ID=49232347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310221887.2A Expired - Fee Related CN103375531B (en) | 2012-04-16 | 2013-04-12 | Centring element for torsional vibration damper and the torsional vibration damper with centring element |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103375531B (en) |
| DE (1) | DE102013205181A1 (en) |
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| CN105683615A (en) * | 2013-10-31 | 2016-06-15 | Valeo离合器公司 | Mechanism for filtering torque fluctuations of a secondary member |
| CN105697569A (en) * | 2014-12-15 | 2016-06-22 | 舍弗勒技术股份两合公司 | Torque transmission device for drivetrain of motor vehicle and drivetrain of motor vehicle |
| CN108953488A (en) * | 2017-05-17 | 2018-12-07 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN110067820A (en) * | 2018-01-23 | 2019-07-30 | 舍弗勒技术股份两合公司 | Clutch system and driving unit with the supporting arrangement in commanding apparatus |
| CN110345171A (en) * | 2018-04-08 | 2019-10-18 | 舍弗勒技术股份两合公司 | Clutch disk and clutch apparatus with centrifugal pendulum |
| WO2020056732A1 (en) * | 2018-09-21 | 2020-03-26 | 舍弗勒技术股份两合公司 | Torque transmission member and centering tool for centering assembly of torque transmission member |
| CN111795114A (en) * | 2019-04-09 | 2020-10-20 | 舍弗勒技术股份两合公司 | Flywheel assembly and drive train |
| CN112283296A (en) * | 2019-07-24 | 2021-01-29 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112014005914A5 (en) * | 2013-12-18 | 2016-09-08 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper with centrifugal pendulum |
| DE102014221005B3 (en) * | 2014-10-16 | 2015-07-23 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper with centrifugal pendulum |
| WO2018149430A1 (en) * | 2017-02-15 | 2018-08-23 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
| DE102017210658A1 (en) * | 2017-06-23 | 2018-12-27 | Zf Friedrichshafen Ag | Friction device for transmitting a torque from a flywheel to a drive device and corresponding method |
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| US6348000B1 (en) * | 1998-02-13 | 2002-02-19 | Ap Time Limited | Torsional vibration dampers |
| CN1539063A (en) * | 2001-08-06 | 2004-10-20 | ¬��Ħ��Ƭ����������Ϲ�˾ | Method for assembling clutch system |
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| DE102009027559A1 (en) * | 2009-07-09 | 2011-01-13 | Zf Friedrichshafen Ag | Torsional vibration damper arrangement, in particular in a clutch disc |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2286105B1 (en) | 2008-06-16 | 2013-02-13 | Schaeffler Technologies AG & Co. KG | Dual clutch with rotary vibration damper |
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- 2013-03-25 DE DE201310205181 patent/DE102013205181A1/en not_active Ceased
- 2013-04-12 CN CN201310221887.2A patent/CN103375531B/en not_active Expired - Fee Related
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| US6348000B1 (en) * | 1998-02-13 | 2002-02-19 | Ap Time Limited | Torsional vibration dampers |
| CN1539063A (en) * | 2001-08-06 | 2004-10-20 | ¬��Ħ��Ƭ����������Ϲ�˾ | Method for assembling clutch system |
| CN101223380A (en) * | 2005-07-14 | 2008-07-16 | 卢克摩擦片和离合器两合公司 | Vibration damping unit, in particular a dual-mass flywheel |
| DE102009027559A1 (en) * | 2009-07-09 | 2011-01-13 | Zf Friedrichshafen Ag | Torsional vibration damper arrangement, in particular in a clutch disc |
| CN201794989U (en) * | 2010-09-08 | 2011-04-13 | 青岛丰宝汽车离合器有限公司 | Dual-mass flywheel assembly |
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| US9683627B2 (en) | 2013-10-31 | 2017-06-20 | Valeo Embrayages | Mechanism for filtering torque fluctuations of secondary member |
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| CN108953488A (en) * | 2017-05-17 | 2018-12-07 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN110067820A (en) * | 2018-01-23 | 2019-07-30 | 舍弗勒技术股份两合公司 | Clutch system and driving unit with the supporting arrangement in commanding apparatus |
| CN110345171A (en) * | 2018-04-08 | 2019-10-18 | 舍弗勒技术股份两合公司 | Clutch disk and clutch apparatus with centrifugal pendulum |
| CN110345171B (en) * | 2018-04-08 | 2022-11-22 | 舍弗勒技术股份两合公司 | Clutch disc with centrifugal pendulum and clutch device |
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| CN112262272A (en) * | 2018-09-21 | 2021-01-22 | 舍弗勒技术股份两合公司 | Torque transmission element and centering tool for centering assembly of torque transmission element |
| CN111795114A (en) * | 2019-04-09 | 2020-10-20 | 舍弗勒技术股份两合公司 | Flywheel assembly and drive train |
| CN112283296A (en) * | 2019-07-24 | 2021-01-29 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| CN112283296B (en) * | 2019-07-24 | 2024-04-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
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| DE102013205181A1 (en) | 2013-10-17 |
| CN103375531B (en) | 2017-03-01 |
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