CN103206464A - Method of manufacturing a transmission clutch assembly with reduced squawk - Google Patents
Method of manufacturing a transmission clutch assembly with reduced squawk Download PDFInfo
- Publication number
- CN103206464A CN103206464A CN2013100090709A CN201310009070A CN103206464A CN 103206464 A CN103206464 A CN 103206464A CN 2013100090709 A CN2013100090709 A CN 2013100090709A CN 201310009070 A CN201310009070 A CN 201310009070A CN 103206464 A CN103206464 A CN 103206464A
- Authority
- CN
- China
- Prior art keywords
- clutch
- clutch pack
- mass
- vibration damper
- receiver member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
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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
- F16F15/1414—Masses driven by elastic elements
- F16F15/1421—Metallic springs, e.g. coil or spiral springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/22—Vibration damping
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The present disclosure relates to a method of manufacturing a transmission clutch assembly configured to reduce squawk during engagement, the method including: forming a clutch component; and coupling a plurality of mass dampers to the clutch component to split a mode of vibration for the clutch component during engagement.
Description
Technical field
The present invention relates to uttering long and high-pitched sounds in the transmission for vehicles clutch assembly (or noise) reduces.
Background technique
Modern speed changer comprises clutch assembly, in order to control wheel of vehicle with respect to the relative rotation speed of engine speed.The rotary component that these clutch assemblies are included in engagement and dissociate and replace between the position.During the clutch engagement, clutch component may vibrate with respect to main drive shaft.This vibration can cause being commonly called the disagreeable noise of " (squawk) utters long and high-pitched sounds ".Many existing speed changers are sought by improving speed changer lubricated or use dynamo-electric gearshift control (or electric gear change) to reduce and utter long and high-pitched sounds.Yet the quality that increases one or more clutch assembly assembly will be more effective to change during the engagement vibrational mode of clutch assembly.
7,163, No. 095 U. S. Patent that name is called " clutch assembly with vibration damper " discloses the self-excitation of using the damping ring that is coupled to clutch hub rubbing surface to reduce clutch assembly.Yet owing to need to increase whole clutch hub circumference quality on every side, the efficient of this configuration is lower than instruction of the present invention; And being connected between clutch hub and the damping ring needs friction coupling, unnecessary energy loss during it also causes meshing.
Therefore, the mode of uttering long and high-pitched sounds in a kind of more effective minimizing transmission for vehicles of needs.As disclosed in the present invention, it will be useful using the mass bumper of other types at the clutch hub, for example, be called in name and will instruct about vehicle braking assembly in 12/417, No. 603 U.S.'s non-provisional application of " vehicle braking assembly ".Also need to have a kind of effective ways of making the transmission clutch assembly, so that spring carried mass vibration damper and concentrated vibration damper are connected to the clutch hub.
Summary of the invention
The present invention is directed to one or more the problems referred to above.Other technologies feature and/or advantage will become apparent from following explanation.
An exemplary embodiment relates to the manufacture method that is configured to reduce the transmission clutch assembly of uttering long and high-pitched sounds during the engagement, comprising: make clutch pack; And a plurality of mass bumpers are coupled to clutch pack, so that the vibrational mode of clutch pack during meshing separated.
Another exemplary embodiment relates to the transmission for vehicles engagement sleeve assembly of being made by following operation: make first receiver member at clutch pack; And mass bumper is press-fit in the groove.
Another exemplary embodiment relates to the transmission for vehicles clutch assembly, and it has: clutch pack; First receiver member of making at clutch pack; And the quality of regulation vibration damper that is assembled to receiver member.
An advantage of the present invention is, its instruction reduces uttering long and high-pitched sounds and the manufacture method of the clutch assembly of disagreeable noise during clutch engagement.Some test sample book demonstrates 10 decibels noise reduction.
Another advantage of the present invention is that it has saved the demand to additional fasteners or fastener material (for example, may use) in screw connection or welding procedure.The fitting method that is pressed into disclosed in this invention allows that spring carried mass vibration damper one end is rigidly connected to the clutch hub and the matter piece of a relative end is operated with cantilevered fashion.When vibration damper was connected on the clutch hub, this connecting means is the relative both sides of block clutch hub also.
Further advantage of the present invention is that it allows that mass bumper is connected on clutch hub internal diameter or the external diameter, thereby produces the effectiveness in vibration suppression of wide range.
Some aspect and embodiment will manifest in the following description.Should be appreciated that at its wide significance, can put into practice the present invention and need not one or more technical characteristics of these aspects and embodiment.Should be appreciated that these aspects and embodiment only are exemplary and explanatory and unrestricted the present invention.
Explain the present invention hereinafter with reference to accompanying drawing in more detail in the mode of example, identical in the accompanying drawings reference character is used for identical or essentially identical part.When by reference to the accompanying drawings, above technical characteristics of the present invention and advantage and other technologies feature and advantage will easily manifest from the embodiment of following implementation best mode of the present invention.In the accompanying drawing:
Description of drawings
Fig. 1 is the side sectional view that wherein is mounted with the transmission for vehicles of exemplary clutch assembly.
Fig. 2 is the perspective view of the clutch gear shown in Fig. 1.
Fig. 3 is the perspective view of a mass bumper using of the clutch gear with Fig. 2.
Fig. 4 is the plan view of the mass bumper of Fig. 3.
Fig. 5 is the side view of the part of clutch gear among Fig. 2.
Fig. 6 is the side view of another exemplary quality vibration damper.
Fig. 7 is that the displacement of various clutch gears is with respect to the plotted curve of frequency.
Although following embodiment is mentioned illustrative embodiment, it much substitutes, revises and change for those skilled in the art is apparent.Therefore, be intended to broadly treat the theme of claim.
Embodiment
With reference to accompanying drawing, show the utter long and high-pitched sounds different embodiments of the transmission for vehicles with clutch assembly of ability of the reduction with improvement, all in the views, similar sign is represented identical or corresponding part.Realize that by in clutch assembly, using one group of mass bumper remarkable noise reduces.In one embodiment, for example, vibration damper is the spring carried mass vibration damper that is coupled to clutch gear.Mass bumper changes the vibrational mode of clutch gear during meshing, thereby reduces the noise output in the shift process.Two chutes (being also referred to as receiver member or groove) separate with 180 degree on clutch gear.Two vibration dampers are press-fit in the groove, so that vibration damper is connected to clutch gear.This manufacture method produces the lubricated advantage that increases, and namely when mass bumper is coupling in the clutch gear, forms lubrication dam between clutch gear one side and clutch gear opposite side.
In certain embodiments, use the spring carried mass vibration damper to allow multidirectional vibration control.Embodiment with spring carried mass vibration damper has dual functions---because edge effect changes bending and the torsional mode of vibration.Followingly discuss exemplary clutch assembly and manufacture method with reference to accompanying drawing.
Figure 1 illustrates the transmission for vehicles 10 of the compatible reduction noise instruction of hereinafter discussing.In this embodiment, speed changer 10 is six speed automatic transmissions.The speed changer of other types and compatibility of the present invention; Five, seven and eight shift transmissions can be used the mass bumper of the present invention's instruction.In other embodiments, speed changer is manual transmission.The speed changer of any kind be can use, for example electric variable transmission or continuously variable transmission comprised.
As shown in fig. 1, transmission clutch assembly 20 comprises two mass bumpers 30 that are connected to clutch gear 40 external diameters.As discussed below, this connecting means has kept clutch gear internal surface 50 and has been exposed to sealing between other clutch portions gear outer surfaces 60 of speed changer.Like this, manufacture method also produces the clutch lubrication strategy stability of increase.
Some cuts gearbox case 70 shown in Fig. 1.Clutch assembly 20 is positioned at the intermediate portion of speed changer.Illustrated clutch assembly 20 comprises that spline engagement arrives the internal clutch gear 40 of output shaft 80.Clutch gear 40 is positioned on the internal diameter that axle journal is supported on a series of friction plates of clutch gear 40 or clutch 90.Hub 100 centers on clutch at the external diameter of clutch 90.Clutch hub 100 is connected to transmission input shaft 110(as local illustrating among Fig. 1).Piston 120 also is nested in the clutch hub 100.But piston 120 is hydraulic actuatings.It is lubricated to control that input shaft 110 disposes a series of holes (for example 130).It is lubricated to control that output shaft 80 also has a series of holes (for example 140).Piston 120 is hydraulic actuating in this embodiment; Yet in other embodiments, piston can be that electricity is actuated (for example using electric gear change and/or servomotor to start the clutch engagement).In this embodiment, piston 120 is actuated the speed changer rear portion with clutch assembly 20 from the speed changer front portion.Returnning spring 150 is combined between the front and back walls of piston 120 in the clutch assembly 20.
As shown in fig. 1, two spring carried mass vibration dampers 30 internally are installed in the clutch gear 40.Spring carried mass vibration damper 30 is connected to the internal surface 50 of clutch gear as described below.
Referring now to Fig. 2, wherein show the clutch gear 40 among Fig. 1 separately.Fig. 2 is the perspective view of clutch gear 40.As shown in the figure, clutch gear 40 is connected to output shaft 80.Clutch gear 40 comprises a series of teeth 160 that take shape on the clutch gear external diameter.Described tooth 160 is used for and clutch plate (for example, as shown in fig. 1 90) engagement.Two spring carried mass vibration dampers 30 are positioned on the internal surface 50 or inner ring of clutch gear 40.In this embodiment, spring carried mass vibration damper 30 is shown to scale.Yet in other embodiments, spring carried mass vibration damper 30 can be different size or structure.In this embodiment, clutch gear 40 is to use powder metallurgy die casting.Can use any existing forming technique, comprise for example turning, milling, punching press or welding, make clutch gear.
As shown in Figure 2, spring carried mass vibration damper 30 is press-fit to the internal surface 50 of clutch gear 40.As shown in Fig. 3 and 4, mass bumper 30 has the spring charge material piece 170 on the cantilevered orientation.Spring charge material piece 170 passes through tie-beam 180 with respect to clutch gear 40 free vibrations.Fig. 3 shows the perspective view of the used spring carried mass vibration damper 30 of the clutch gear 40 of Fig. 2.
As shown in Fig. 3 and 4, mass bumper 30 comprises a spring charge material piece 170.Spring charge material piece 170 is positioned at an end of vibration damper 30.In this embodiment, matter piece 170 is configured to rectangle.The intermediate portion of matter piece 170 comprises hole (or adjustment hole) 190, in order to control the weight of matter piece.Like this, in different speed changers, can implement identical mass bumper 170 structures.By increasing or reduce the size in the hole 190 in the matter piece 170, can carry out the weight of mass bumper and regulate.
As shown in Fig. 3 and 4, at the other end of vibration damper, vibration damper 30 base portions comprise anchoring piece 200.Anchoring piece 200 is triangularity in this embodiment.Anchoring piece 200 comprises two tips that arrange 210 of vibration damper end 220 angledly.Described tip 210 is used for being assembled to the receiver member that forms on the clutch gear.Vibration damper 30 is made by steel.Vibration damper 30 also can be made by other materials, for example the combination of aluminium, stainless steel, polymer or any above-mentioned material.In this embodiment, vibration damper 30 is to use powder metallurgical technique to form.Use bore process to form hole 190 at vibration damper 30.Other forming techniques that it will be understood to those of skill in the art that mass bumper also in protection scope of the present invention, include but not limited to, punching press, milling, die casting or extruding.
As shown in Figure 5, make two receiver members 230 at clutch gear 40.The tip 210 that receiver member 230 is used on the assembly quality vibration damper 30.In this embodiment, receiver member 230 is the U-shaped radial grooves with angle configurations or fillet radius, and this angle configurations or fillet radius are designated as θ in Fig. 5.In the embodiment of Fig. 5, θ is about 30 degree.Therefore, the radian of the receiver member 230 that forms at clutch gear 40 is about 30 degree.In other embodiments, the radian of receiver member is greater than or less than 30 degree.As shown in the figure, tip 210 and receiver member 230 are used for forming between vibration damper 30 and clutch gear 40 being tightly connected.When vibration damper 30 inserted receiver member 230, the two inner ring 50 at for example clutch gear shown in Fig. 1 40 formed lubrication dam or sealing.
Cooperate technology that tip 210 is fitted into receiver member 230 by being pressed into.The force applications of any kind be can use, (for example) punching press, hydraulic pressure, compression joint technique comprised.Therefore, the manufacture method that is configured to reduce the transmission clutch assembly of uttering long and high-pitched sounds during the engagement comprises: make clutch pack (for example, the clutch gear shown in Fig. 2 40); A plurality of mass bumpers (for example, 30 shown in Fig. 2) are press-fit to clutch pack, so that the vibrational mode of clutch pack during meshing separated.As discussed, can use Modern Manufacturing Technology, comprise milling, punching press, die casting, turning, injection moulding or welding, make vibration damper.
Be pressed into cooperation technology and can form lubrication dam between clutch pack and mass bumper, this place that is connected between receiver member and the mass bumper fully forms fluid-tight (for example shown in Fig. 2).
Referring now to Fig. 6, wherein show the optional environment for the spring carried mass vibration damper 300 that is implemented into the transmission clutch gear.Mass bumper 300 shown in Fig. 6 has setting 320 rectangle spring charge material piece 310 at one end.Narrow link 330 places intermediate portion, and it is as the cantilever between matter piece 310 and the anchoring piece 340.Anchoring piece 340 is arranged at the other end 350 of vibration damper.In this embodiment, anchoring piece 340 has two-part.First portion 360 is rectangle parts.Second portion 370 has the angle configurations of α with respect to the central shaft A of mass bumper 300.α is about 45 ° in this embodiment.At the end 350 of vibration damper 300, anchoring piece 340 forms two triangular pointed 380.Tip on the anchoring piece also is used for being attached to the compatible receiver member that is formed on the clutch gear.
In this embodiment, mass bumper is of a size of 20mm x30mm.It is thick that link is about 1mm.In other embodiments, the size of mass bumper and structure can change.
Referring now to Fig. 7, wherein show some the exemplary test result by the different clutch gears of plotted curve 400 expressions.The y axle is the displacement of clutch during meshing.Displacement is measured with the form of millimeter.The x axle is the frequency of representing with hertz.Line A represents to take from wherein not the data in conjunction with the clutch gear of any vibration damper.The hub edge maximum displacement of being represented by line A is about 0.0007mm and takes place with the frequency of 578Hz.This 578Hz baseline is the amplitude present position of the oscillating curve of clutch hub during meshing.
As shown in Figure 7, line B and C represent the test data from the clutch hub that wherein combines the spring carried mass vibration damper (for example, shown in Fig. 2-3 and above-mentioned the disclosing).Compare with the amplitude of the clutch gear of no mass bumper, the displacement that is connected with the clutch gear of spring carried mass vibration damper has the less amplitude of essence.As shown in Figure 7, relevant with C with line B hub has the vibrational mode of cutting apart.The double mode maximum displacement of cutting apart the clutch hub to be avoiding and clutch resonance coupling, and avoids the noise unstability.The amplitude (or maximum value) of the displacement relative frequency curve of line B is about 0.0001mm.This occurs in about 585Hz.The amplitude of the displacement relative frequency curve of line C also is about 0.0001mm.This occurs in about 569Hz.
As illustrated in above, the spring carried mass vibration damper of discussing about Fig. 2 to 4 has reduced undesired vibration at both direction at least.Test result as discussed below proves that the torque that the spring carried mass vibration damper also reduces in the clutch assembly changes.Referring now to table 1, wherein show the test data of the hub of the advantage that contrasts the clutch hub and have this instruction.The torque of measuring each clutch hub in the speed changer under the different pressures level changes.Under the 0.86MPa total pressure, there is the clutch hub of the no vibration damper of clutch hub ratio of vibration damper to demonstrate significantly reduced torque variation (90Nm compares 290Nm).At 0.99MPa each clutch hub is taken a sample.Under this pressure, the torque of the hub of no vibration damper experience 550Nm changes, and the torque that has the clutch of vibration damper only to experience 290Nm changes.Carry out next measurement at 1.13MPa.The torque of the clutch hub experience 850Nm of no vibration damper changes, and has the torque of the clutch hub experience 730Nm of vibration damper to change.At last, under the highest test pressure (1.26MPa), the torque of the clutch hub of no vibration damper experience 880Nm changes.The torque that has the clutch hub of vibration damper only to experience 290Nm changes.
Table 1: the test result that has and do not have the clutch hub of vibration damper
Those skilled in the art will recognize put into practice various alternate design of the present invention and embodiment in the protection domain of claim.For example, dissimilar mass bumpers can be attached to clutch pack, includes, but are not limited to the lumped mass vibration damper.And different transmission assemblies can be benefited from vibration damping disclosed in this invention and be pressed into compounding technique (for example, clutch plunger, other clutch hubs etc.).
Claims (10)
1. a manufacture method that is configured to reduce the transmission clutch assembly of uttering long and high-pitched sounds during the engagement is characterized in that, comprising:
Make clutch pack; And
A plurality of mass bumpers are coupled to clutch pack, so that the vibrational mode of clutch pack during meshing separated.
2. method according to claim 1 is characterized in that, coupling comprises mass bumper is press-fit to clutch pack.
3. method according to claim 1 is characterized in that, further comprises:
Between clutch pack and mass bumper, form lubrication dam.
4. method according to claim 3 is characterized in that, forms lubrication dam and comprises:
Make receiver member at clutch pack, so that mass bumper can be fitted into them at least in part.
5. method according to claim 4 is characterized in that, makes receiver member and is included in and makes groove on the clutch pack.
6. a transmission for vehicles engagement sleeve assembly is characterized in that, is made by following technology:
Make first receiver member at clutch pack: and
Mass bumper is press-fit to groove.
7. clutch pack according to claim 6 is characterized in that, further comprises:
Between clutch pack and mass bumper, form lubrication dam.
8. clutch pack according to claim 6 is characterized in that, first receiver member is radial groove.
9. clutch pack according to claim 6 is characterized in that, mass bumper is the spring carried mass vibration damper.
10. clutch pack according to claim 9 is characterized in that, further comprises:
Make second receiver member at clutch pack; And
Wherein mass bumper comprises a plurality of tips that can be assembled to first and second receiver members.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/351,447 | 2012-01-17 | ||
| US13/351,447 US20120111693A1 (en) | 2009-04-02 | 2012-01-17 | Method of Manufacturing a Transmission Clutch Assembly with Reduced Squawk |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103206464A true CN103206464A (en) | 2013-07-17 |
| CN103206464B CN103206464B (en) | 2016-09-07 |
Family
ID=48693351
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310009070.9A Expired - Fee Related CN103206464B (en) | 2012-01-17 | 2013-01-10 | It is configured to reduce the manufacture method of the transmission clutch assembly uttered long and high-pitched sounds |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN103206464B (en) |
| DE (1) | DE102013200228A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043285A (en) * | 2019-11-20 | 2020-04-21 | 东风汽车有限公司 | Resonance frequency control device and method for left suspension of gearbox |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6050380A (en) * | 1997-05-09 | 2000-04-18 | Mannesmann Sachs Ag | Friction clutch with a compensating system |
| US20020017443A1 (en) * | 2000-08-03 | 2002-02-14 | Mannesmann Sachs Ag | Clutch disk |
| US20040074712A1 (en) * | 2002-10-22 | 2004-04-22 | Ford Global Technologies, Inc. | Brake assembly with tuned mass damper |
| US20050183922A1 (en) * | 2004-02-20 | 2005-08-25 | Springer James A. | Clutch assembly with vibration damper |
| CN101006258A (en) * | 2004-08-24 | 2007-07-25 | 谢夫勒两合公司 | Device for damping rotary oscillations |
-
2013
- 2013-01-10 CN CN201310009070.9A patent/CN103206464B/en not_active Expired - Fee Related
- 2013-01-10 DE DE201310200228 patent/DE102013200228A1/en not_active Withdrawn
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6050380A (en) * | 1997-05-09 | 2000-04-18 | Mannesmann Sachs Ag | Friction clutch with a compensating system |
| US20020017443A1 (en) * | 2000-08-03 | 2002-02-14 | Mannesmann Sachs Ag | Clutch disk |
| US20040074712A1 (en) * | 2002-10-22 | 2004-04-22 | Ford Global Technologies, Inc. | Brake assembly with tuned mass damper |
| US20050183922A1 (en) * | 2004-02-20 | 2005-08-25 | Springer James A. | Clutch assembly with vibration damper |
| CN101006258A (en) * | 2004-08-24 | 2007-07-25 | 谢夫勒两合公司 | Device for damping rotary oscillations |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043285A (en) * | 2019-11-20 | 2020-04-21 | 东风汽车有限公司 | Resonance frequency control device and method for left suspension of gearbox |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102013200228A1 (en) | 2013-07-18 |
| CN103206464B (en) | 2016-09-07 |
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