CN102918297B - Torsional vibration damper - Google Patents
Torsional vibration damper Download PDFInfo
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- CN102918297B CN102918297B CN201180026813.2A CN201180026813A CN102918297B CN 102918297 B CN102918297 B CN 102918297B CN 201180026813 A CN201180026813 A CN 201180026813A CN 102918297 B CN102918297 B CN 102918297B
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- vibration damper
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- 230000000694 effects Effects 0.000 claims description 7
- 238000013016 damping Methods 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 6
- 238000002485 combustion reaction Methods 0.000 description 6
- 239000011324 bead Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 239000007858 starting material Substances 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000001133 acceleration Effects 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
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction 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
- 238000002955 isolation Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
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
- F16F15/14—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 two and can be bearing in around the spin axis of this torque-vibration damper and go up each other and the flywheel mass of the effect can resisting a spring assembly around described spin axis Finite Twist each other.
Background technique
This torque-vibration damper such as with the form of double mass flywheel by fully openly and be all that series connection uses for a long time.At this, the effect of the spring assembly that two flywheel masses are preferably formed by arc spring around a spin axis opposing is bearing in goes up each other.If torsional vibration enters into this torque-vibration damper, then carry out in this spring assembly when the corresponding compression of spring assembly torque peak intermediate storage and carry out time lag to drivetrain with the output of damping.At this, the quality energizing frequency particularly depending on the internal-combustion engine of such as diesel engine form and the moment need transmitted by this torque-vibration damper of isolating technique.At this, when predetermined structure space condition, owing to must be configured with the spring assembly of high stiffness, along with the increase of the moment that need transmit, damping capacity is also deteriorated.
Therefore disclosed in DE 10 2,004 011 380 A1 be such as, advise a kind of torque-vibration damper combined with centrifugal force pendulum, in this torque-vibration damper, except the spring assembly worked in a circumferential direction between two diskwares, also arrange one arranging with circumferentially distributing and the pendulum mass of the limited pivotable of load-bearing member rotated around the spin axis of torque-vibration damper relative to one and form a vibration canceller matched with rotating speed.Described pendulum mass has high number of components around the axis of oscillation pivotable of described spin axis radially outer and has multiple supporting portion with load-bearing member respectively, and described supporting portion suffers high centrifugal force load.By the spacing (avoiding contacting with each other) that described pendulum mass is necessary to each other, when operational structure space, the operational maximum moment of inertia of described pendulum mass is relatively little.
Summary of the invention
Therefore task of the present invention is, provides a kind of torque-vibration damper of improvement, and it is with low cost and damping element is firmly integrated, reduces number of components simultaneously and achieves simple supporting.
This task will be solved by a kind of torque-vibration damper, it is particularly in the drivetrain of Motor Vehicle, comprise two to be bearing in around the spin axis of this torque-vibration damper and to go up each other and the flywheel mass of the effect can resisting a spring assembly around described spin axis Finite Twist each other, wherein, arrange one and be bearing in central annulus mass pendulum relative to described spin axis, described quality is put when two flywheel masses are reversed by the rotary actuation on limited windup-degree of one of described two flywheel masses.
Can number of components be reduced by the quality part (it can be arranged around described spin axis limited translation) that only a unique quality puts form and construct bearing device in a simpler manner.Quality pendulum carries out by means of relative to rotarily driving of a flywheel mass in sense of rotation, rotational speed or the driving rotated when accelerating change, and described flywheel mass is only born little load and can be supported in a simpler manner.By a unique annular quality pendulum, the moment of inertia of shock-absorption quality can relative to multiple pendulum mass circumferentially distributing such as with 3 to 5 times of risings.The driving of quality pendulum when windup-degree changes at this particularly causing vibration elimination effect by during rotational impact excitation flywheel mass.
Described quality pendulum relative to one of two flywheel masses rotarily drive or rotatable communication this can by means of at least one, preferably multiple equably circumferentially distribute, be torsionally bearing between described quality pendulum with described flywheel mass in other flywheel masses, to put with described flywheel mass and described quality and form force transfering device such as the small gear of toothing respectively and formed.Other force transfering device can be such as rolling geometrical construction, crank hinge and the analog that other moment of torsion transmission coupling element such as rubs sealed.
This or these be configured to grafting axle and the small gear of corresponding outer toothing had for quality pendulum and driving flywheel is such as bearing in another flywheel by means of plastic bushing in a simpler manner.At this, secondary flywheel can drive described quality to put, and wherein, described small gear such as grafting axle is torsionally received in elementary flywheel.Alternatively, elementary flywheel can drive described quality to put.In this case, grafting axle is torsionally arranged on secondary flywheel mass or the component that is connected with this secondary flywheel mass such as loads in the flange part of the energy storage device of described spring assembly.In without the mode of execution of flywheel mass or when arranging separately described flywheel mass, described quality pendulum controls as driven and corresponding grafting axle or small gear are torsionally arranged in the component of other input sides or outlet side by component such as the diskware of input side or outlet side.
At this, between quality pendulum and the flywheel mass driving this quality to put, can velocity ratio be set, thus when the rotational acceleration of quality pendulum changes, described quality pendulum is driven by with a velocity ratio acceleration or deceleration relatively with sense of rotation.At this, be configured in small gear be a side from flywheel mass and and quality put as the toothing between the opposing party realizes different gear ratio, wherein, the number of teeth and/or functional diameter (FD) can differently be formed.The torsion of quality pendulum can be identical with the sense of rotation of driving flywheel mass, wherein, small gear utilizes corresponding outer toothing to be engaged in locking manner in counterpart profile that is that quality is put or flywheel at radially outer or inner radial rotation relative to the spin axis of torsional vibration damping respectively.If should realize the turn-back of quality pendulum, then such as small gear to be engaged in a toothing part or to be engaged to by means of other outer toothings by means of an outer toothing at radially outer in other toothing parts that are that described quality is put or described flywheel mass.Have been found that by experiment at this, depend on the characteristic of internal-combustion engine, such as depend on cylinder number and thus depend on the torsional vibration be incorporated in drivetrain, the effect of torsional vibration damping is depended on velocity ratio relative to described torsional vibration and is depended on that the sense of rotation that quality is put is such as 2 rank relative to driving flywheel mass.Such as when there are four cylinders and Maximum Torque is the diesel engine more than 300Nm, 1.0 to 1.8, preferably 1.2 to 1.6 drive up than with 0.8 to-0.1, preferably-0.6 to-0.2 step-down ratio be proved to be particularly advantageous.Be understandable that, when internal-combustion engine such as has the individual features of Otto (Otto) motor of different cylinder number (such as between three cylinder to eight cylinders) or diesel engine, different preferred velocity ratios can be favourable.
Quality pendulum can be formed on single type ground.Such as quality pendulum can be formed by sheet material, and wherein, at radially outer, in order to improve moment of inertia, multiple flaggy can fold up and down.In inner radial, quality pendulum can be bearing on bearing flange.The bearing flange of a flywheel mass can at identical or other the bearing device diametrically forming the flywheel mass being used for other.For can directly stretch out from described sheet material to the toothing part that small gear forms toothing or can be formed by the corresponding sheet material parts stretched out.Described bearing device can be slip-or rolling bearing device.In addition, be proved to be particularly advantageously, described quality pendulum by one is formed a toothing and a bearing support load-bearing member and one fixing as being such as formed as on load-bearing member as described in being riveted on cast-or the quality loop of forging piece formed.
At this, described quality pendulum can be arranged on the side opposed with described secondary flywheel mass of an elementary flywheel mass.In this configuration, quality pendulum approximate be arranged on torque-vibration damper outside and towards the wall of internal-combustion engine.Elementary flywheel mass can at least be pressed in radial outer region at this, thus makes quality put the inner radial that can be arranged on an axial bead, and described axial bead such as can receive described starter gear ring.
In addition, in order to improve isolation effect further, can a centrifugal force pendulum be configured effectively to one or two flywheel mass.For this reason, also arrange except described quality pendulum multiple circumferentially distribute, can put relative to the quality of the limited pivotable of a load-bearing member.Such as, can be used as load-bearing member at the flange part of outlet side as primary side loading spring device and pendulum mass be received in the inner radial of this spring assembly.
Accompanying drawing explanation
The present invention is elaborated by means of the embodiment in Fig. 1 to 12.At this illustrate:
Fig. 1: the phantom observed from transmission side being torque-vibration damper of the present invention;
Fig. 2: the phantom observed from engine side being the torque-vibration damper of Fig. 1;
Fig. 3: be the sectional view of the torque-vibration damper in Fig. 1 along the line Y-Y that dissects;
Fig. 4: be the sectional view of the torque-vibration damper in Fig. 1 along the line X-X that dissects;
Fig. 5: the disintegration figure being the torque-vibration damper in Fig. 1;
Fig. 6: the phantom being the torque-vibration damper relative to the torque-vibration damper change in Fig. 1, with having subtend relative to the quality pendulum that the flywheel mass driven rotates with having gear ratio;
Fig. 7: the phantom being the torque-vibration damper changed relative to the torque-vibration damper of Fig. 6, has the quality pendulum rotated with having gear ratio relative to the flywheel mass driven in the same way;
Fig. 8: the phantom being the torque-vibration damper changed relative to the torque-vibration damper of Fig. 6, there is subtend relative to the flywheel mass driven without the quality pendulum that rotates of gear ratio ground;
Fig. 9: the phantom being a kind of torque-vibration damper, has the quality pendulum driven by elementary flywheel mass;
Figure 10: the phantom being the torque-vibration damper in Fig. 9;
Figure 11: the phantom being a kind of torque-vibration damper, has the quality pendulum driven by elementary flywheel mass and the small gear bearing device changed relative to the torque-vibration damper of Fig. 9; With
Figure 12: the phantom being the torque-vibration damper in Figure 11.
Embodiment
Fig. 1 and 2 illustrates from transmission side (Fig. 1) and from engine side (Fig. 2) and to rotate around spin axis 2 and to be received in the torque-vibration damper 1 bent axle of internal-combustion engine, such as four cylinder diesel engine, and it is the form of double mass flywheel.These two flywheel masses 3,4 can go up the limited use ground displacement mutually of resisting spring assembly 7 by means of bearing device 6 each other, wherein, flywheel mass 3 to be fixed on bent axle by means of permanent opening 5 as elementary flywheel mass and flywheel mass 4 is used as to need the counter of friction clutch fixed thereon at input side, and described spring assembly is made up of two arc springs 8 at this.For this reason, elementary flywheel mass 3 arranges some invisible recessed forming sections and the arm 10 that radial direction widens is set in secondary flywheel mass 4 on the flange part be connected with this secondary flywheel mass.
Except the torsional vibration damping function of flywheel mass 3,4 can resisting spring assembly 7 Finite Twist, described torque-vibration damper is also provided with the quality pendulum 11 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 torsionally and be received in described elementary flywheel mass 3 with circumferentially 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 flange part 9 and quality put toothing part 15 in 11, 16 form the toothing 17 rested on planetary type gear transmission unit, 18, in described planetary type gear transmission unit, elementary flywheel mass 3 can be considered that being connected to secondary flywheel mass 4 and quality puts bridge member between 11, quality pendulum 11 described in namely described secondary flywheel mass 4 rotary actuation.Toothing 17 to be arranged on flange part 9 and toothing 18 is arranged on quality pendulum 11 at radially outer in inner radial at this, thus the driving that quality is put is carried out in reverse sense of rotation.In addition, by the outer toothing 14 of the toothing 18 on quality pendulum 11 relative on flange part 9 and thus the larger diameter of toothing 17 in secondary flywheel mass 4 realizes the drive up ratio of quality pendulum 11 relative to secondary flywheel mass 4.
Fig. 3 and Fig. 4 illustrates the sectional view along line X-X or Y-Y that dissect of the torque-vibration damper 1 in Fig. 1.Described elementary flywheel mass 3 is received on bearing member 19 regularly, described secondary flywheel mass 4 by means of be arranged on permanent opening 5 inner radial bearing device 6, torsionally receive as rolling bearing.Quality pendulum 11 described permanent opening 5 radially outer by means of bearing device 20(this be sliding bearing device) be torsionally received on described bearing member 19.Guide bearing 27 for receiving unshowned transmission input shaft is arranged on described bearing member 19 in inner radial.
Quality pendulum 11 is made up of load-bearing member 21 and quality loop 22 in two style, and described load-bearing member is made up of sheet material.Load-bearing member and quality loop are interconnected by means of rivet 23.The situation that load-bearing member is forming the toothing part 16 that is axially shaped has corresponding dead slot 24, and described toothing part is spaced from each other in a circumferential direction respectively by corresponding bridge member 25.In inner radial, for the formation of the axial bead 26 of bearing device 20 on load-bearing member 21 is shaped.
The grafting axle of small gear 12 as having its outer toothing 13,14 is torsionally bearing in the respective openings in elementary flywheel mass 3 by means of plastic bushing 28.When two flywheel masses 3,4 are reversed each other, arc spring 8 to be compressed at the arm 10 of outlet side by the flange part 9 be connected with secondary flywheel mass 4 by means of rivet 30 by the recessed forming section 29 of elementary flywheel mass at input side.Described torsion is such as carried out when transmitting the moment of torsion be input to by internal-combustion engine in torque-vibration damper 1.At this, rotational impact, whirling vibration etc. to be stored in spring assembly 7 by improving windup-degree in short-term and to export to time lag again, thus realize vibration damping.Along with the change of windup-degree, described small gear 12 is driven by means of described toothing 18, wherein, this small gear is to be configured with the quality pendulum 11 of predetermined moment of inertia described in the velocity ratio reverse direction actuation set of toothing 17, thus eliminate the momentum introduced by rotational impact and whirling vibration, thus realize the isolating technique of improvement generally.At this, be proved especially effectively for vibration is eliminated, the velocity ratio that secondary flywheel mass 4 and quality are put between 11 is 1.0 to 1.8, particularly between 1.6 and 1.2.
Fig. 5 illustrates torque-vibration damper 1 with the form of disintegration figure, has the bearing member 19 receiving guide bearing 27, is received in described bearing member load-bearing member 21 swivel bearing, and described load-bearing member has by means of the fixing quality loop 22 of rivet 23 and sliding bearing 31.In addition, elementary flywheel mass 3 is fixed with stopping-off piece 32 with described bearing member 19 and is connected with feeling relieved, and wherein, after being screwed onto on bent axle, is fixed connection by permanent opening 5.This external radially outer of elementary flywheel mass 3 receives starter gear ring 33 and becomes complete by diskware 34,35 and abrasion protection shell 36 and seal ring 37 when forming the doughnut that inner radial is opened wide, and puts into arc spring 8 and insert flange part 9 in described doughnut.Small gear 12 is bearing in the opening 38 of elementary flywheel mass 3.Flange part 9 is riveted by means of rivet 30 and secondary flywheel mass 4.Centring pin 39 is put in described secondary flywheel mass 4 to receive the clutch pressure plate of a friction clutch with feeling relieved.
Fig. 6 illustrates the phantom of the torque-vibration damper 101 of the torque-vibration damper 1 be similar in Fig. 1 to 5, in this torque-vibration damper, on flange part 109 additionally and between the dead slot 140 forming toothing part 115, receive one in the both sides of flange part 109 at circumference can relative to the pendulum mass 141 of flange part 109 limited translation to form centrifugal force pendulum, just as such as disclosed in DE 10 2,004 011 380 A1.
Fig. 7 illustrates the phantom of the torque-vibration damper 201 of the torque-vibration damper 1 be similar in Fig. 1 to 6.Be with their difference, the rotating Vortex arranging quality pendulum 11 drives, its mode is, the outer toothing 213,214 of small gear 212 respectively with flange part 209 or toothing part 215,216 that quality puts 211 form toothing 217,218 at radially outer.In an identical manner, in other mode of execution, toothing can be configured in inner radial respectively.
Fig. 8 illustrates the torque-vibration damper 301 corresponding to described torque-vibration damper 1,101,201, and it is had and is driven by the counterrotating of secondary flywheel mass 4 by means of flange part 309.By being configured with the outer toothing 313,314 of same diameter when being configured with small gear 312 of the identical number of teeth, between flange part 309 and quality put 311, there is not velocity ratio in other words velocity ratio is adjusted to 1.0.
Fig. 9 and 10 illustrates the phantom of torque-vibration damper 401 and such partial view, and in described partial view, quality pendulum 411 is driven by elementary flywheel mass 403.For this reason, flange part 409 receives and has bolt 441, small gear 412 is fixed by means of guard ring 442 and is torsionally received on described bolt.Elementary flywheel mass 403 comprises some dead slots 440 with toothing part 415, and the outer toothing 413 of described toothing part and small gear forms toothing 417, and the outer toothing 414 with toothing part 416 forms the toothing 418 with quality pendulum 411.Shown embodiment, corresponding to the torque-vibration damper 1,101,301 in Fig. 1 to 5,6 and 8, is shown quality pendulum 41 1 and is driven by the counterrotating of elementary flywheel mass 403.
Change ground relative to the torque-vibration damper 401 of Fig. 9 and 10, Figure 11 and 12 illustrates phantom and a partial view of torque-vibration damper 501, has equally and puts 511 by the quality of elementary flywheel mass 503 rotary actuation.Oppositely slow down with the velocity ratio of torque-vibration damper 401 unlike, quality pendulum 511, such as between-0.8 and-0.1, preferably between-0.5 and-0.3.For this reason, the outer toothing 513 towards the toothing 517 of elementary flywheel mass 503 has the diameter larger than the outer toothing 514 of the toothing 518 towards quality pendulum 511 or the large number of teeth.Be understandable that, construct at radially outer or inner radial the rotary actuation that toothing can arrange identical sense of rotation by both sides.In order to be received on flange part 509 by small gear 512, extrude dome 543 from this flange part, small gear 512 is axially received on described dome across by means of bolt 541
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 parts
16 toothing parts
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 recessed forming sections
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 parts
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 parts
216 toothing parts
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 parts
416 toothing parts
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 parts
516 toothing parts
517 toothings
518 toothings
541 bolts
543 domes
X-X dissects line
Y-Y dissects line
Claims (9)
1. a torque-vibration damper (1, 101, 201, 301, 401, 501), particularly be in the drivetrain of Motor Vehicle, comprise two to be bearing in around the spin axis of this torque-vibration damper (2) and to go up each other and the flywheel mass (3 of the effect can resisting a spring assembly (7) around described spin axis Finite Twist each other, 4, 304, 403, 503), it is characterized in that, arrange one and be bearing in central annulus mass pendulum (11 relative 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) one of rotary actuation on limited windup-degree, at least one is torsionally bearing in a flywheel mass (3), with another flywheel mass (4, 304, 403, 503) and quality pendulum (11, 211, 311, 411, 511) small gear (12 of force transfering device is formed, 212, 312, 412, 512) at described quality pendulum (11, 211, 311, 411, 511) with another flywheel mass (4 described, 304, 403, 503) work between.
2. torque-vibration damper according to claim 1 (1,201,401,501), is characterized in that, described force transfering device is as toothing (17,18; 217,218; 417,418; 517,518) there is the different drive ratios of described another flywheel mass (4,304,403,503) and described quality pendulum (11,211,311,411,511).
3. torque-vibration damper according to claim 1 (1,101,201,301,401,501), it is characterized in that, described quality pendulum (11,211,311,411,511) toothing (18 is formed by one, 218,318,418,518) and the load-bearing member (21) and of a bearing device (20) be fixed on quality loop (22) on described load-bearing member and formed.
4. torque-vibration damper according to claim 1 (1,101,201,301), is characterized in that, described quality pendulum (11,211,311) is driven by a level flywheel mass (4,304).
5. torque-vibration damper (401 according to claim 1,501), it is characterized in that, described small gear (412,512) can reverse configuration to a level flywheel mass and described quality pendulum (411,511) driven by an elementary flywheel mass (403,503).
6. the torque-vibration damper (1,101,201 any one of claim 4 to 5,301,401,501), it is characterized in that, described quality pendulum (11,211,311,411,511) an elementary flywheel mass (3,403 is arranged on, 503) on the side opposed with described secondary flywheel mass (4,304).
7. the torque-vibration damper (201) any one of claim 1 to 5, is characterized in that, described quality pendulum (211) is driven in the sense of rotation of described torque-vibration damper (201).
8. the torque-vibration damper (1,101,301 any one of claim 1 to 5,401,501), it is characterized in that, described quality pendulum (11,311,411,511) against described torque-vibration damper (1,101,301,401,501) sense of rotation is driven.
9. the torque-vibration damper (101 any one of claim 1 to 5,201,301), it is characterized in that, also arrange outside described quality pendulum (211,311) multiple circumferentially distribute, can relative to quality pendulum (141) of the limited pivotable of a load-bearing member.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010022098.1 | 2010-05-31 | ||
| DE102010022098 | 2010-05-31 | ||
| PCT/DE2011/001085 WO2011150911A2 (en) | 2010-05-31 | 2011-05-19 | Rotary vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102918297A CN102918297A (en) | 2013-02-06 |
| CN102918297B true 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) | DE102011101977A1 (en) |
| WO (1) | WO2011150911A2 (en) |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| US9939057B2 (en) * | 2015-10-20 | 2018-04-10 | Valeo Embrayages | Torsional vibration damper for hydrokinetic torque coupling device |
| 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 |
| DE102017130544A1 (en) | 2017-12-19 | 2019-06-19 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| DE102018100923A1 (en) | 2018-01-17 | 2019-07-18 | Schaeffler Technologies AG & Co. KG | Ringtilgereinrichtung |
| WO2019141309A1 (en) | 2018-01-17 | 2019-07-25 | Schaeffler Technologies AG & Co. KG | Annular vibration damper device |
| DE102019100359A1 (en) | 2018-01-17 | 2019-07-18 | Schaeffler Technologies AG & Co. KG | Ringtilgereinrichtung |
| DE102019100378A1 (en) | 2018-01-17 | 2019-07-18 | Schaeffler Technologies AG & Co. KG | Ringtilgereinrichtung |
| DE102018130818A1 (en) | 2018-01-17 | 2019-07-18 | Schaeffler Technologies AG & Co. KG | Ringtilgereinrichtung |
| DE102018126752A1 (en) | 2018-01-17 | 2019-07-18 | Schaeffler Technologies AG & Co. KG | Ring pendulum with raceway insert |
| DE102018106272A1 (en) | 2018-03-19 | 2019-09-19 | Schaeffler Technologies AG & Co. KG | Ringtilgereinrichtung |
| DE102018108295A1 (en) | 2018-04-09 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| DE102018108560A1 (en) | 2018-04-11 | 2019-10-17 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| DE102018112285A1 (en) | 2018-05-23 | 2019-11-28 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| DE102018113592A1 (en) | 2018-06-07 | 2019-12-12 | Schaeffler Technologies AG & Co. KG | Ring shuttle |
| DE102018210945B4 (en) * | 2018-07-03 | 2021-12-09 | Audi Ag | Torsional vibration damper |
| 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 |
Citations (4)
| 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 |
| 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 |
Family Cites Families (1)
| 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 DE201110101977 patent/DE102011101977A1/en not_active Withdrawn
- 2011-05-19 CN CN201180026813.2A patent/CN102918297B/en not_active Expired - Fee Related
- 2011-05-19 DE DE112011101864T patent/DE112011101864A5/en not_active Ceased
- 2011-05-19 WO PCT/DE2011/001085 patent/WO2011150911A2/en active Application Filing
Patent Citations (4)
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112011101864A5 (en) | 2013-03-28 |
| WO2011150911A3 (en) | 2012-04-12 |
| WO2011150911A2 (en) | 2011-12-08 |
| CN102918297A (en) | 2013-02-06 |
| DE102011101977A1 (en) | 2011-12-01 |
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