CN102918297A - Torsional Vibration Damper - Google Patents
Torsional Vibration Damper Download PDFInfo
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- CN102918297A CN102918297A CN2011800268132A CN201180026813A CN102918297A CN 102918297 A CN102918297 A CN 102918297A CN 2011800268132 A CN2011800268132 A CN 2011800268132A CN 201180026813 A CN201180026813 A CN 201180026813A CN 102918297 A CN102918297 A CN 102918297A
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- 230000000694 effects Effects 0.000 claims description 8
- 230000015572 biosynthetic process Effects 0.000 claims description 2
- 238000013016 damping Methods 0.000 description 7
- 238000002485 combustion reaction Methods 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 5
- 239000011324 bead Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000002955 isolation Methods 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 239000007858 starting material Substances 0.000 description 3
- 230000008093 supporting effect Effects 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 2
- 230000003042 antagnostic effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 235000012489 doughnuts Nutrition 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 238000012432 intermediate storage Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
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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
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/1464—Masses connected to driveline by a kinematic mechanism or gear system
- F16F15/1478—Masses connected to driveline by a kinematic mechanism or gear system with a planetary gear system
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a torsional vibration damper (1) comprising two flywheel masses (3, 4) which can be mounted on one another about a rotational axis (2) of the torsional vibration damper and can be rotated to a limited extent relative to one another about the rotational axis against the action of a spring device. In order to improve the vibration decoupling performance of a torsional vibration damper, in particular arranged in the drive train of a motor vehicle, an annular pendulum mass (11) is provided, which is mounted centrally with respect to the axis of rotation and which is driven in rotation by one of the two flywheel masses over a limited angle of rotation when the two flywheel masses are twisted with respect to one another.
Description
Technical field
The present invention relates to a kind of torque-vibration damper, particularly be in the drivetrain of Motor Vehicle, comprise that two can be bearing in around the spin axis of this torque-vibration damper and go up each other and can center on the each other flywheel mass of Finite Twist of effect that described spin axis resists a spring assembly.
Background technique
This torque-vibration damper for example with the form of double mass flywheel by fully open and all be that series connection is used for a long time.At this, the effect of the spring assembly that two flywheel masses are preferably formed by arc spring around spin axis opposing is bearing in each other goes up.If torsional vibration enters into this torque-vibration damper, then carry out time lag and output damping in the intermediate storage of in this spring assembly, carrying out torque peak in the situation of the corresponding compression of spring assembly and to drivetrain.At this, the quality of vibration isolation particularly depends on for example energizing frequency and the moment that needs to transmit by this torque-vibration damper of the internal-combustion engine of diesel engine form.At this, in the situation of predetermined structure space condition, owing to must be configured with the spring assembly of high stiffness, the increase of the moment of transmitting along with need, damping capacity is variation also.
Therefore for example disclosedly by DE 10 2,004 011 380 A1 be, advise torque-vibration damper a kind of and the centrifugal force pendulum combination, in this torque-vibration damper, except the spring assembly that works in a circumferential direction between two diskwares, also arrange one circumference distribute that ground arranges and with respect to one around the pendulum mass of the limited pivot of load-bearing member of the spin axis rotation of torque-vibration damper and form a vibration canceller that matches with rotating speed.Described pendulum mass centers on respectively the axis of oscillation pivot of described spin axis radially outer and has high number of components and have a plurality of supportings position with load-bearing member, and described supporting position suffers high centrifugal force load.By described pendulum mass necessary spacing (contacting with each other in order to avoid) to each other, the operational maximum moment of inertia of described pendulum mass is relatively little in the situation of operational structure space.
Summary of the invention
Therefore task of the present invention is that a kind of torque-vibration damper of improvement is provided, and it is with low cost and damping element is firmly integrated, has reduced simultaneously number of components and has realized simple supporting.
This task will solve by a kind of torque-vibration damper, it particularly is in the drivetrain of Motor Vehicle, comprise that two can be bearing in around the spin axis of this torque-vibration damper and go up each other and can center on the each other flywheel mass of Finite Twist of effect that described spin axis resists a spring assembly, wherein, arrange one and be bearing in the annular quality pendulum of central authorities with respect to described spin axis, described quality pendulum when two flywheel masses are reversed by one of described two flywheel masses rotary actuation on limited windup-degree.
Can reduce number of components and construct bearing device in simpler mode by the quality part of unique quality pendulum form (it can arrange around the limited displacement of described spin axis ground) only.The driving when sense of rotation, rotational speed or Spin-up change of quality pendulum is by means of carrying out with respect to rotarily driving of a flywheel mass, and described flywheel mass is only born little load and can be supported in simpler mode.By the quality pendulum of a unique annular, the moment of inertia of shock-absorption quality can be with respect to a plurality of pendulum masses that distribute at circumference for example with 3 to 5 times of risings.The driving of quality pendulum when windup-degree changes particularly causes vibration elimination effect at this by rotational impact excitation flywheel mass the time.
Described quality pendulum with respect to one of two flywheel masses rotarily drive or rotate be coupling in this can by means of at least one, preferred a plurality of that distribute at circumference equably, can be bearing between described quality pendulum and the described flywheel mass with reversing in other flywheel masses, form respectively the small gear formation of force transfering device such as toothing with described flywheel mass and described quality pendulum.Other force transfering device for example can be that other moment of torsion transmits rolling geometrical construction, crank hinge and the analog that coupling element for example rubs sealed.
This or these be configured to peg graft axle and have for quality pendulum and the small gear that drives with the corresponding outer toothing of flywheel and for example be bearing in another flywheel by means of plastic bushing in simpler mode.At this, secondary flywheel can drive described quality pendulum, and wherein, described small gear such as grafting axle can be received in the elementary flywheel with reversing.Alternatively, elementary flywheel can drive described quality pendulum.In this case, the grafting axle can be installed in secondary flywheel mass or the member that is connected with this secondary flywheel mass for example loads in the flange part of energy storage device of described spring assembly with reversing.In without the mode of execution of flywheel mass or when separately described flywheel mass being set, described quality pendulum can be arranged in the member of other input sides or outlet side such as drive and peg graft accordingly axle or small gear by member such as the diskware control of input side or outlet side with reversing.
At this, between the flywheel mass of quality pendulum and this quality pendulum of driving, velocity ratio can be set, thereby when the rotational acceleration of quality pendulum changed, described quality pendulum and sense of rotation were driven with a velocity ratio acceleration or deceleration relatively.At this, be configured in small gear and flywheel mass and be a side and and the quality pendulum realize different gear ratio for the toothing between the opposing party, wherein, the number of teeth and/or functional diameter (FD) can differently consist of.Reversing of quality pendulum can be identical with the sense of rotation that drives with flywheel mass, wherein, the corresponding outer toothing of small gear utilization is engaged in quality counterpart profile pendulum or flywheel at radially outer or inner radial rotation in locking manner with respect to the spin axis of torsional vibration damping respectively.If should realize the turn-back of quality pendulum, then for example small gear is engaged in the toothing spare or is engaged in described quality other toothing spares that put or described flywheel mass by means of toothing other outside at radially outer by means of an outer toothing.Have been found that by experiment at this, the characteristic that depends on internal-combustion engine, thereby for example depend on the cylinder number and depend on the torsional vibration that is incorporated in the drivetrain that the effect of torsional vibration damping is depended on velocity ratio with respect to described torsional vibration and depended on that the sense of rotation of quality pendulum for example is 2 rank with respect to driving with flywheel mass.For example have in four cylinders and the Maximum Torque situation for the diesel engine that surpasses 300Nm 1.0 to 1.8, preferred 1.2 to 1.6 drive up than being proved to be particularly advantageous with 0.8 to-0.1, preferred-0.6 to-0.2 step-down ratio.Be understandable that for example have at internal-combustion engine in the situation of individual features of Otto (Otto) motor of different cylinder numbers (for example between three cylinder to eight cylinders) or diesel engine, different preferred velocity ratios can be favourable.
The quality pendulum can consist of on single type ground.For example the quality pendulum can be formed by sheet material, and wherein, at radially outer, in order to improve moment of inertia, a plurality of flaggies can fold up and down.In inner radial, the quality pendulum can be bearing on the bearing flange.The bearing flange of a flywheel mass can be formed at identical or other diameter the bearing device of other flywheel mass.Being used for forming the toothing spare of toothing with small gear can be directly stretch out or can be formed by the corresponding sheet material parts that stretch out from described sheet material.Described bearing device can be to slide-or rolling bearing device.In addition, be proved to be particularly advantageous and be, described quality pendulum by a load-bearing member and that forms a toothing and a bearing support fix as on the load-bearing member as described in being riveted on for example form casting-or the quality loop of forging piece form.
At this, described quality pendulum can be arranged on an elementary flywheel mass with the opposed side of described secondary flywheel mass on.In this configuration, quality pendulum is approximate to be arranged on the outside of torque-vibration damper and towards the wall of internal-combustion engine.Elementary flywheel mass can be pressed in the radially outer zone at least at this, thereby so that the quality pendulum can be arranged on the inner radial of an axial bead, described axial bead for example can receive described starter gear ring.
In addition, in order further to improve isolation effect, can effectively give one or two flywheel mass configuration a centrifugal force pendulum.For this reason, except described quality pendulum, also arrange a plurality of that distribute at circumference, can be with respect to the quality pendulum of the limited pivot of a load-bearing member.For example, can be used as load-bearing member and pendulum mass is received in the inner radial of this spring assembly at the flange part of outlet side such as primary side loading spring device.
Description of drawings
Elaborate the present invention by means of the embodiment among Fig. 1 to 12.This illustrate:
Fig. 1: the phantom from the transmission side observation that is torque-vibration damper of the present invention;
Fig. 2: the phantom from starting pusher side to observe that is the torque-vibration damper of Fig. 1;
Fig. 3: be that torque-vibration damper among Fig. 1 is along the sectional view of the line Y-Y that dissects;
Fig. 4: be that torque-vibration damper among Fig. 1 is along the sectional view of the line X-X that dissects;
Fig. 5: the disintegration figure that is the torque-vibration damper among Fig. 1;
Fig. 6: be the phantom with respect to the torque-vibration damper of the change of the torque-vibration damper among Fig. 1, having subtend ground has the quality of gear ratio ground rotation to put with respect to the flywheel mass that drives;
Fig. 7: be the phantom of the torque-vibration damper that changes with respect to the torque-vibration damper of Fig. 6, have the quality pendulum that the rotation of gear ratio ground is arranged with respect to the flywheel mass that drives in the same way;
Fig. 8: be the phantom of the torque-vibration damper that changes with respect to the torque-vibration damper of Fig. 6, have subtend ground with respect to the quality pendulum of the flywheel mass that drives without the rotation of gear ratio ground;
Fig. 9: be a kind of phantom of torque-vibration damper, have the quality pendulum that is driven by elementary flywheel mass;
Figure 10: the phantom that is the torque-vibration damper among Fig. 9;
Figure 11: be a kind of phantom of torque-vibration damper, the small gear bearing device that has the quality pendulum that driven by elementary flywheel mass and change with respect to the torque-vibration damper of Fig. 9; With
Figure 12: the phantom that is the torque-vibration damper among Figure 11.
Embodiment
Fig. 1 and 2 is from transmission side (Fig. 1) and from starting pusher side (Fig. 2) to illustrate around spin axis 2 rotation and be received in internal-combustion engine, the torque-vibration damper 1 on the bent axle of four cylinder diesel engine for example, and it is the form of double mass flywheel.These two flywheel masses 3,4 can be in the limitedly mutually displacement of effect of going up each other by means of bearing device 6 antagonistic spring devices 7, wherein, flywheel mass 3 input side be fixed on the bent axle as elementary flywheel mass by means of permanent opening 5 and flywheel mass 4 as the back-pressure plate that needs friction clutch fixed thereon, described spring assembly is made of two arc springs 8 at this.For this reason, in elementary flywheel mass 3 some invisible arms 10 that are recessed into shaped part and radially widen the flange part that is connected with this secondary flywheel mass setting are set on secondary flywheel mass 4.
But except the flywheel mass 3 of antagonistic spring device 7 Finite Twists, 4 torsional vibration damping function, described torque-vibration damper also is provided with the quality pendulum 11 of eliminating vibration, and described quality pendulum is driven in rotation when described two flywheel masses 3,4 are reversed.For this reason, small gear 12 can reverse ground and be received in the described elementary flywheel mass 3 at circumference with distributing, the both sides of the acceptance division of described small gear in described elementary flywheel mass 3 have outer toothing 13,14, in described outer toothing and the flange part 9 and the toothing spare 15 in the quality pendulum 11,16 form the toothing 17 that rests on the planetary type gear transmission unit, 18, in described planetary type gear transmission unit, elementary flywheel mass 3 can be considered the bridge member that is connected between secondary flywheel mass 4 and the quality pendulum 11, namely the described quality pendulum 11 of described secondary flywheel mass 4 rotary actuations.Toothing 17 is arranged on the flange part 9 and toothing 18 is arranged on the quality pendulum 11 at radially outer at this in inner radial, thereby so that the driving of quality pendulum carry out in reverse sense of rotation.In addition, thus the outer toothing 14 by the toothing 18 on the quality pendulum 11 is realized quality pendulum 11 ratios that drive up with respect to secondary flywheel mass 4 with respect to the larger diameter of the toothing 17 on the flange part 9 and on the secondary flywheel mass 4.
Fig. 3 and Fig. 4 illustrate the sectional view along dissect line X-X or Y-Y of the torque-vibration damper 1 among Fig. 1.Described elementary flywheel mass 3 is received on the bearing member 19 regularly, and described secondary flywheel mass 4 by means of the bearing device 6 that is arranged on permanent opening 5 inner radial, can receive such as rolling bearing with reversing.Quality pendulum 11 radially outers at described permanent opening 5 are the sliding bearing device by means of bearing device 20(at this) can be received on the described bearing member 19 with reversing.Be arranged on described bearing member 19 for the guide bearing 27 that receives unshowned transmission input shaft in inner radial.
Quality is put 11 two-piece type ground and is made by load-bearing member 21 and quality loop 22, and described load-bearing member is made by sheet material.Load-bearing member and quality loop interconnect by means of rivet 23.Load-bearing member has corresponding dead slot 24 in the situation that forms the toothing spare 16 that axially is shaped, and described toothing spare is spaced from each other in a circumferential direction by corresponding bridge member 25 respectively.In inner radial, being shaped at load-bearing member 21 is used to form the axial bead 26 of bearing device 20.
Fig. 5 illustrates torque-vibration damper 1 with the form of disintegration figure, has the bearing member 19 that receives guide bearing 27, is received in the described bearing member load-bearing member 21 swivel bearings, and described load-bearing member has quality loop 22 and the sliding bearing 31 of fixing by means of rivet 23.In addition, elementary flywheel mass 3 is connected fixing with described bearing member 19 with stopping-off piece and centering ground is connected, and wherein, is fixed connection by permanent opening 5 after on being screwed onto bent axle.Elementary flywheel mass 3 these external radially outers receive starter gear rings 33 and by diskware 34,35 and abrasion protection shell 36 and seal ring 37 in the situation that forms the doughnut that inner radial opens wide, become complete, in described doughnut, put into arc spring 8 and insert flange part 9.Small gear 12 is bearing in the opening 38 of elementary flywheel mass 3.Flange part 9 is by means of rivet 30 and secondary flywheel mass 4 riveted joints.Centring pin 39 is put in the described secondary flywheel mass 4 so that centering ground receives the clutch pressure plate of a friction clutch.
Fig. 6 illustrates the phantom of the torque-vibration damper 101 of the torque-vibration damper 1 that is similar among Fig. 1 to 5, in this torque-vibration damper, on the flange part 109 additionally and circumference form between the dead slot 140 of toothing spare 115 receive one in the both sides of flange part 109 can be with respect to the pendulum mass 141 of flange part 109 limited displacements to form centrifugal force pendulum, just as for example disclosed among DE 10 2,004 011 380 A1.
Fig. 7 illustrates the phantom of the torque-vibration damper 201 of the torque-vibration damper 1 that is similar among Fig. 1 to 6.Be with their difference, the rotating Vortex that quality pendulum 11 is set drives, its mode is that the outer toothing 213,214 of small gear 212 forms toothing 217,218 with toothing spare 215,216 flange part 209 or quality pendulum 211 at radially outer respectively.In an identical manner, in other mode of execution, toothing can be configured in respectively inner radial.
Fig. 8 illustrates corresponding to described torque-vibration damper 1,101,201 torque-vibration damper 301, and it has by the counterrotating of secondary flywheel mass 4 by means of flange part 309 and drives.Outer toothing 313,314 by being configured with same diameter does not exist velocity ratio in other words velocity ratio to be adjusted to 1.0 between flange part 309 and quality pendulum 311 in the situation of the small gear 312 that is configured with the identical number of teeth.
Fig. 9 and 10 illustrates phantom and such partial view of torque-vibration damper 401, and in described partial view, quality pendulum 411 is driven by elementary flywheel mass 403.For this reason, in flange part 409 receptions bolt 441 is arranged, small gear 412 is fixed and can be received on the described bolt with reversing by means of guard ring 442.Elementary flywheel mass 403 comprises some dead slots with toothing spare 415 440, and the outer toothing 413 of described toothing spare and small gear forms toothings 417, and the outer toothing 414 with toothing spare 416 forms the toothing 418 with quality pendulum 411.Shown embodiment shows quality and puts the 41 1 counterrotatings drivings by elementary flywheel mass 403 corresponding to the torque-vibration damper 1,101,301 among Fig. 1 to 5,6 and 8.
Torque-vibration damper 401 with respect to Fig. 9 and 10 changes ground, and Figure 11 and 12 illustrates phantom and partial view of torque-vibration damper 501, has equally the quality pendulum 511 by elementary flywheel mass 503 rotary actuations.Different from torque-vibration damper 401 is that the velocity ratio of quality pendulum 511 oppositely slows down, for example between-0.8 and-0.1, preferably between-0.5 and-0.3.For this reason, have than towards the large diameter of the outer toothing 514 of the toothing 518 of quality pendulum 511 or the large number of teeth towards the outer toothing 513 of the toothing 517 of elementary flywheel mass 503.Be understandable that, the rotary actuation of identical sense of rotation can be set at radially outer or inner radial structure toothing by ground, both sides.For small gear 512 is received on the flange part 509, extrude dome 543 from this flange part, small gear 512 axially is received on the described dome across by means of bolt 541
The reference character table
1 torque-vibration damper
2 spin axiss
3 flywheel masses
4 flywheel masses
5 permanent openings
6 bearing devices
7 spring assemblies
8 arc springs
9 flange parts
10 arms
11 quality pendulum
12 small gears
13 outer toothings
14 outer toothings
15 toothing spares
16 toothing spares
17 toothings
18 toothings
19 bearing members
20 bearing devices
21 load-bearing members
22 quality loops
23 rivets
24 dead slots
25 bridge members
26 beads
27 guide bearings
28 plastic bushings
29 are recessed into shaped part
30 rivets
31 sliding bearings
32 stopping-off pieces
33 starter gear rings
34 diskwares
35 diskwares
36 abrasion protection shells
37 seal rings
38 openings
39 centring pins
101 torque-vibration dampers
109 flange parts
115 toothing spares
140 dead slots
141 pendulum masses
201 torque-vibration dampers
209 flange parts
211 quality pendulum
212 small gears
213 outer toothings
214 outer toothings
215 toothing spares
216 toothing spares
217 toothings
218 toothings
301 torque-vibration dampers
304 flywheel masses
309 flange parts
311 quality pendulum
312 small gears
313 outer toothings
314 outer toothings
401 torque-vibration dampers
403 flywheel masses
409 flange parts
411 quality pendulum
412 small gears
413 outer toothings
414 outer toothings
415 toothing spares
416 toothing spares
417 toothings
418 toothings
440 dead slots
441 bolts
442 guard rings
501 torque-vibration dampers
503 flywheel masses
509 flange parts
511 quality pendulum
512 small gears
513 outer toothings
514 outer toothings
515 toothing spares
516 toothing spares
517 toothings
518 toothings
541 bolts
543 domes
The X-X line of dissecting
The Y-Y line of dissecting
Claims (10)
1. torque-vibration damper (1,101,201,301,401,501), particularly be in the drivetrain of Motor Vehicle, comprise that two can be bearing in around the spin axis (2) of this torque-vibration damper and go up each other and can center on the each other flywheel mass (3,4 of Finite Twist of effect that described spin axis resists a spring assembly (7), 304,403,503), it is characterized in that, arrange one and be bearing in the annular quality pendulum (11 of central authorities with respect to described spin axis (2), 211,311,411,511), described quality is put when two flywheel masses are reversed each other by described two flywheel masses (3,4,304,403,503) rotary actuation on limited windup-degree one of.
2. according to claim 1 torque-vibration damper (1,101,201,301,401,501), it is characterized in that, at least one can be bearing in with reversing in other flywheel masses (3), with flywheel mass (4,304,403,503) and quality pendulum (11,211,311,411,511) small gear (12,212,312,412 of formation force transfering device, 512) at described quality pendulum (11,211,311,411,511) Yu between the described flywheel mass (4,304,403,503) work.
3. according to claim 2 torque-vibration damper (1,201,401,501) is characterized in that described force transfering device such as toothing (17,18; 217,218; 417,418; 517,518) has the different drive ratios that a flywheel mass (4,304,403,503) and described quality are put (11,211,311,411,511).
4. according to claim 2 torque-vibration damper (1,101,201,301,401,501), it is characterized in that described quality pendulum (11,211,311,411,511) form a toothing (18 by one, 218,318,418,518) and the quality loop (22) that is fixed on the described load-bearing member of the load-bearing member (21) and of a bearing device (20) form.
5. each torque-vibration damper (1,101,201,301) in 4 according to claim 1 is characterized in that described quality pendulum (11,211,311) is driven by a level flywheel mass (4,304).
6. each torque-vibration damper (401,501) in 4 according to claim 1 is characterized in that, described small gear (412,512) can reverse configuration is driven by an elementary flywheel mass (403,503) to level flywheel mass and described quality pendulum (411,511).
7. each torque-vibration damper (1,101,201 in 6 according to claim 1,301,401,501), it is characterized in that described quality pendulum (11,211,311,411,511) be arranged on an elementary flywheel mass (3,403,503) with the opposed side of described secondary flywheel mass (4,304) on.
8. each torque-vibration damper (201) in 7 according to claim 1 is characterized in that described quality pendulum (211) is driven on the sense of rotation of described torque-vibration damper (201).
9. each torque-vibration damper (1,101,301,401,501) in 7 according to claim 1, it is characterized in that described quality pendulum (11,311,411,511) is against described torque-vibration damper (1,101,301,401,501) sense of rotation is driven.
10. each torque-vibration damper (101 in 7 according to claim 1,201,301), it is characterized in that, except also arrange outside the described quality pendulum (211,311) a plurality of that distribute at circumference, can be with respect to the quality pendulum (141) of the limited pivot of a load-bearing member.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010022098 | 2010-05-31 | ||
| DE102010022098.1 | 2010-05-31 | ||
| PCT/DE2011/001085 WO2011150911A2 (en) | 2010-05-31 | 2011-05-19 | Rotary vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102918297A true CN102918297A (en) | 2013-02-06 |
| CN102918297B CN102918297B (en) | 2015-06-17 |
Family
ID=44718964
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201180026813.2A Expired - Fee Related CN102918297B (en) | 2010-05-31 | 2011-05-19 | Torsional vibration damper |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN102918297B (en) |
| DE (2) | DE112011101864A5 (en) |
| WO (1) | WO2011150911A2 (en) |
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| CN108138898A (en) * | 2015-10-20 | 2018-06-08 | 法雷奥离合器公司 | For the torque-vibration damper of fluid dynamic torque coupling arrangement |
| CN112424503A (en) * | 2018-07-03 | 2021-02-26 | 奥迪股份公司 | Torsional vibration damper |
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| DE102012219728A1 (en) * | 2012-10-29 | 2014-04-30 | Zf Friedrichshafen Ag | Hybrid drive module and powertrain |
| DE102013212522A1 (en) | 2013-06-27 | 2014-12-31 | Schaeffler Technologies Gmbh & Co. Kg | torsional vibration dampers |
| DE102014015542B4 (en) * | 2014-10-20 | 2022-06-30 | Mtu Friedrichshafen Gmbh | measuring device |
| DE102017130544A1 (en) | 2017-12-19 | 2019-06-19 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| WO2019141309A1 (en) | 2018-01-17 | 2019-07-25 | Schaeffler Technologies AG & Co. KG | Annular vibration damper device |
| DE102018130818A1 (en) | 2018-01-17 | 2019-07-18 | Schaeffler Technologies AG & Co. KG | Ringtilgereinrichtung |
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| DE102018113592A1 (en) | 2018-06-07 | 2019-12-12 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| DE102018117448A1 (en) | 2018-07-19 | 2020-01-23 | Schaeffler Technologies AG & Co. KG | Speed-adaptive damper device |
| DE102018126532A1 (en) | 2018-10-24 | 2020-04-30 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper |
| CN110966348B (en) * | 2020-01-12 | 2023-01-31 | 华东交通大学 | Automobile dual-mass flywheel adopting double-layer damping springs |
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| CN1109563A (en) * | 1993-12-22 | 1995-10-04 | 菲希特尔及萨克斯有限公司 | Torsional vibration damper with a planetary gearset |
| US6019683A (en) * | 1996-03-08 | 2000-02-01 | Fichtel & Sachs Ag | Two part flywheel for a motor vehicle, the two part flywheel having a torsional vibration damper |
| GB2346194A (en) * | 1996-01-18 | 2000-08-02 | Luk Lamellen & Kupplungsbau | Apparatus for damping fluctuations of torque |
| EP1122461B1 (en) * | 2000-01-31 | 2004-10-06 | ZF Sachs AG | Torsional vibration damper |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009042805A1 (en) * | 2008-11-24 | 2010-05-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device for motor vehicle, has planetary wheels divided into two partial gear wheels that are rotated around axis of rotation, where torque applied to device is transmitted over one of partial gear wheels |
-
2011
- 2011-05-19 DE DE112011101864T patent/DE112011101864A5/en not_active Ceased
- 2011-05-19 WO PCT/DE2011/001085 patent/WO2011150911A2/en active Application Filing
- 2011-05-19 DE DE201110101977 patent/DE102011101977A1/en not_active Withdrawn
- 2011-05-19 CN CN201180026813.2A patent/CN102918297B/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1109563A (en) * | 1993-12-22 | 1995-10-04 | 菲希特尔及萨克斯有限公司 | Torsional vibration damper with a planetary gearset |
| GB2346194A (en) * | 1996-01-18 | 2000-08-02 | Luk Lamellen & Kupplungsbau | Apparatus for damping fluctuations of torque |
| US6019683A (en) * | 1996-03-08 | 2000-02-01 | Fichtel & Sachs Ag | Two part flywheel for a motor vehicle, the two part flywheel having a torsional vibration damper |
| EP1122461B1 (en) * | 2000-01-31 | 2004-10-06 | ZF Sachs AG | Torsional vibration damper |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108138898A (en) * | 2015-10-20 | 2018-06-08 | 法雷奥离合器公司 | For the torque-vibration damper of fluid dynamic torque coupling arrangement |
| CN108138898B (en) * | 2015-10-20 | 2020-09-08 | 法雷奥凯佩科液力变矩器(南京)有限公司 | Torsional vibration damper for a hydrodynamic torque coupling |
| CN107796343A (en) * | 2017-11-17 | 2018-03-13 | 杭州航验环境技术有限公司 | A kind of high-precision positioner and high accuracy positioning householder method |
| CN107796343B (en) * | 2017-11-17 | 2024-05-10 | 杭州航验环境技术有限公司 | High-precision positioning device and high-precision positioning auxiliary method |
| CN112424503A (en) * | 2018-07-03 | 2021-02-26 | 奥迪股份公司 | Torsional vibration damper |
| CN112424503B (en) * | 2018-07-03 | 2022-05-17 | 奥迪股份公司 | Torsional vibration damper |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011150911A2 (en) | 2011-12-08 |
| WO2011150911A3 (en) | 2012-04-12 |
| DE102011101977A1 (en) | 2011-12-01 |
| DE112011101864A5 (en) | 2013-03-28 |
| CN102918297B (en) | 2015-06-17 |
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