CN201129396Y - Dual mass flywheel torsional vibration damper - Google Patents
Dual mass flywheel torsional vibration damper Download PDFInfo
- Publication number
- CN201129396Y CN201129396Y CNU2007200870452U CN200720087045U CN201129396Y CN 201129396 Y CN201129396 Y CN 201129396Y CN U2007200870452 U CNU2007200870452 U CN U2007200870452U CN 200720087045 U CN200720087045 U CN 200720087045U CN 201129396 Y CN201129396 Y CN 201129396Y
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- China
- Prior art keywords
- flywheel
- spring
- vibration damper
- double mass
- driving plate
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Abstract
The utility model discloses a dual mass flywheel torsional vibration damper, it includes first flywheel, establishes elastic damping device in the first flywheel, with first flywheel coaxial coupling's second flywheel, connects the drive plate on the second flywheel, and the jack catch of drive plate is established in elastic damping device. The utility model discloses broken through the limitation that traditional clutch shock absorber arranged the space, avoided the undulant power transmission system torsional vibration resonance that causes of engine torque under idle speed and the operating mode commonly used basically, showing and improving the car and taking the travelling comfort. The noise of the transmission and the vehicle body under various working conditions is thoroughly eliminated. The structure is simpler. The shock absorber in the original clutch driven disc is cancelled, so that the rotational inertia during gear shifting is small, and the gear shifting is light. And the requirements that the engine works at a low rotating speed, a multi-gear transmission is used and the like are met, so that the fuel economy is indirectly improved, and the emission of harmful gases is reduced. Long service life and stable working performance.
Description
Technical field
The utility model belongs to the vibration damping equipment in the auto parts and components, is specifically related to a kind of engine flywheel vibration damping equipment.
Background technique
The automobile power-transmission system torsional oscillation is one of important root of internal car noise and vibration, and it directly has influence on the life-span of the riding comfort and the component of automobile.And the vibration damping of transmission system is mainly by the vibration damper on the clutch driven plate, owing to be subjected to the structural limitations of driven disc friction plate, the distribution radius of damper spring is little, rigidity is big so the corner of vibration damper is little, can not reach excellent vibration damping effect, there is certain impact in resonance in the time of can't avoiding idling to the component of transmission system.Existing double mass flywheel torshional vibration damper exists friction pair many, and the sealing surface between the friction pair requires high, and friction pair processing request height increases running resistance simultaneously.
Summary of the invention
The purpose of this utility model is to provide a kind of can weaken the double mass flywheel torshional vibration damper that Power Train torsional oscillation and idling do not have resonance, to address the above problem.
The technical solution of the utility model is: the double mass flywheel torshional vibration damper, it comprises first flywheel, establishes elastic shock-absorbing device in first flywheel, with coaxial second flywheel that is connected of first flywheel, connect driving plate on second flywheel, the claw of driving plate is located in the elastic vibration clamper.The elastic vibration clamper of establishing in described first flywheel comprises the spring chamber annular groove of offering on the first flywheel card, establishes at least two limiting stoppers in the spring chamber annular groove, in the spring chamber annular groove between two limiting stoppers cluster spring is set respectively; Connect cover plate on the spring chamber annular groove.
Be provided with axial limiting and compensation device between described first flywheel and the driving plate.
The low rigidity of the utility model utilization reduces the natural frequency on certain single order or a few rank, and it is shifted out the normal revolution district.The rotary inertia of improvement system distributes, the intrinsic torsional vibration characteristic of tuning system.The transient oscillation that suitable damping causes with contingent resonance and impulsive load in decay engine start/stopping process is set.
The utility model has been broken through the limitation of conventional clutch vibration damper arrangement space, has avoided the Power Train torsional resonance that the engine torque fluctuation causes under idling and the operating mode commonly used substantially, has significantly improved vehicle ride comfort.Speed changer and body noise under each operating mode have been eliminated comparatively up hill and dale.Relatively simple for structure.Cancelled the vibration damper in the former clutch driven plate, the rotary inertia when making gear shift is little, and gear shift is light.And satisfy motor more in requirements such as slow-speed of revolution work, use multi-speed transmissions, thus improved fuel economy indirectly, reduced discharge of harmful gases.Long service life, stable work in work.
Description of drawings
The assembly structure chart of Fig. 1 double mass flywheel torshional vibration damper.
The assembly sectional view of Fig. 2 double mass flywheel torshional vibration damper.
Fig. 3 first flywheel structure master looks schematic representation.
Fig. 4 first flywheel structure cross-sectional schematic.
Fig. 5 driving plate master looks schematic representation.
Fig. 6 driving plate structure cross-sectional schematic.
Fig. 7 second flywheel and driving plate connection diagram.
Fig. 8 driving plate axial limiting and compensation device structural representation.
Wherein: the 1st, limiting stopper, 2 is first spring seats, 3 is first springs, 4 is first slide blocks, and 5 is second springs, and 6 is second slide blocks, 7 is the 3rd springs, and 8 is the 3rd slide blocks, and 9 is the 4th springs, 10 is second spring seats, the 11st, and flywheel ring gear, the 12nd, driving plate, the 12-1 axis hole, 12-2 encircles platform, 12-3 riveted holes, the 12-4 fitting recess, 12-5 claw, 12-6 are annular grooves, the 13rd, bearing, 14 is first flywheels, 14-1 is the spring chamber annular groove, 14-2 is a shaft part, 14-3 draw-in groove, the 15th, fore bearing of speed changer, the 16th, shrouding disc, 17 is second flywheels, the 18th, bearing, the 19th, axial limiting and compensation device, 19-1 is a damping fin, and 19-2 is a steel disc, and 19-3 is a belleville spring, 19-4 is the circle baffle plate, the 20th, and spring cabin liner.
Embodiment
Present embodiment is used for technical solutions of the utility model for explaining that protection domain of the present utility model is not limited to following structure.
Shown in Fig. 3,4, the card of first flywheel 14 is offered spring chamber annular groove 14-1, and the shaft part 14-2 of first flywheel 14 is used for realizing axial socket with second flywheel 17.
As shown in Figure 1, establish elastic vibration clamper in the spring chamber annular groove 14-1 of first Flywheel disc 14.Elastic vibration clamper comprises in the spring chamber annular groove 14-1 that establishes in the spring chamber annular groove 14-1 between 1, two limiting stopper 1 of at least two limiting stoppers cluster spring is set respectively.Along the circle spacing three limiting stoppers 1 are set in the annular groove of this example medi-spring chamber, evenly are provided with.Cluster spring is composed in series by two springs at least, establishes slide block between two springs.This example medi-spring group is made up of the spring 3,5,7,9 of four series connection, establishes slide block between adjacent two springs, and promptly slide block 4,6,8.The two ends of every group of spring are provided with spring seat 2,10.This structure forms 3 groups of elastic shock-absorbing devices.The spring length difference of four series connection in every group of spring, first spring 3 increases successively to the length of the 4th spring 9.Series connection realizes multistage effectiveness in vibration suppression, and transmits bigger moment of torsion by many groups Parallel Control.
As shown in Figure 2, second flywheel 17 and first flywheel 14 are by bearing 18 sockets, connect driving plate 12 on second flywheel 17, the claw 12-5 of driving plate 12 driving plates is located in the elastic shock-absorbing device, and it is that claw 12-5 contacts with spring seat 2,10 that the claw 12-5 of driving plate 12 contacts with every group of spring one end spring seat end face.
Second flywheel 17 and driving plate 12 connection diagrams are riveted between second flywheel 17 and the driving plate 12 as shown in Figure 7.
As shown in Figure 1, 2, driving plate 12 is located in the spring chamber annular groove 14-1 of first flywheel 14 claw 12-5 by fitting recess 12-4 is pressed on the bearing 13, and claw 12-5 contacts with spring seat 2,10.Spring chamber annular groove 14-1 goes up and connects cover plate 16, and cover plate 16 is connected with limiting stopper 1, and limiting stopper 1 is connected with first flywheel 14, and claw 12-5 and both sides limiting stopper 1 are gapped.
Shown in Fig. 2,8, be provided with axial limiting and compensation device 19 between first flywheel 14 and the driving plate 12.Axial limiting and compensation device 19 are located in the other annular groove 12-6 of the ring platform 12-2 of driving plate 12, and axial limiting and compensation device 19 comprise stacked be located at damping fin 19-1, the steel disc 19-2 in the annular groove 12-6, belleville spring 19-3 and circle baffle plate 19-4 on the driving plate; Circle baffle plate 19-4 is connected with first Flywheel disc 14, and circle baffle plate 19-4 covers belleville spring 19-3, realizes axial limiting.
Concrete: damping fin 19-1 is made by high-abrasive material, is attached to the inboard of driving plate, the attenuation of can wearing and tearing in time; Steel disc 19-2 is stuck in by 4 claws in the draw-in groove 14-3 on the shaft part 14-2 of first flywheel 14, and making between the belleville spring 19-3 and first flywheel 14 does not have relative movement, prevents belleville spring accelerated wear test; Belleville spring 19-3 can keep constant substantially impacting force in the certain attenuation scope of damping fin, for system provides stable damping; The circle baffle plate is screwed on first flywheel by 8 bolts hole, provides limit function for second fly wheel assembly simultaneously.
As shown in Figure 2, covering liner 20 at spring chamber annular groove 14-1 wall surface, when reducing the elastic vibration clamper motion to the wearing and tearing of first flywheel 14.
Establish fore bearing 15 of speed changer in first flywheel, 14 axis holes.Guarantee the function of traditional flywheel.
The vibration damping of this device is to stir spring seat by the claw 12-5 on the driving plate 12 to come pressure spring, realize the function of vibration damper, and the moment of torsion of motor is delivered to second flywheel, 17, the second flywheels 17 from first flywheel 14 by clutch driven plate moment of torsion is delivered in the transmission system again.Axial limiting and compensation device 19 make between damping fin 19-1 and the driving plate 12 and form damping, and can compensate wearing and tearing in running, limit the axial motion of second flywheel 17 simultaneously.
Claims (9)
1, a kind of double mass flywheel torshional vibration damper, it comprises first flywheel, it is characterized in that establishing elastic vibration clamper in first flywheel, with coaxial second flywheel that is connected of first flywheel, connect driving plate on second flywheel, the claw of driving plate is located in the elastic shock-absorbing device; The elastic vibration clamper of establishing in described first flywheel comprises the spring chamber annular groove of offering on the first flywheel card, establishes at least two limiting stoppers in the spring chamber annular groove, in the spring chamber annular groove between two limiting stoppers cluster spring is set respectively; Connect cover plate on the spring chamber annular groove.
2, double mass flywheel torshional vibration damper according to claim 1 is characterized in that described cluster spring is composed in series by two springs at least, establishes slide block between two springs, and spring can be inside and outside edge cover form.
3, as double mass flywheel torshional vibration damper as described in the claim 2, it is characterized in that the two ends of every group of spring are provided with spring seat.
4, as double mass flywheel torshional vibration damper as described in the claim 3, it is characterized in that the claw of driving plate contacts with every group of spring one end spring seat end face.
5, as double mass flywheel torshional vibration damper as described in claim 1 or 2 or 3 or 4, it is characterized in that along the circle spacing three limiting stoppers being set in the described spring chamber annular groove, in the spring chamber annular groove between per two limiting stoppers cluster spring is set respectively, cluster spring is made up of the spring of four series connection, establishes slide block between adjacent two springs.
6, as double mass flywheel torshional vibration damper as described in the claim 4, it is characterized in that being provided with driving plate axial limiting and compensation device between the driving plate and first Flywheel disc.
7, as double mass flywheel torshional vibration damper as described in the claim 6, it is characterized in that described axial limiting and compensation device comprise stacked damping fin, steel disc and the belleville spring that is located on the driving plate, the circle baffle plate is connected with first Flywheel disc, and the circle baffle plate covers belleville spring.
8, double mass flywheel torshional vibration damper according to claim 1 is characterized in that first Flywheel disc is provided with flywheel ring gear.
9, as double mass flywheel torshional vibration damper as described in the claim 5, it is characterized in that the spring length difference of four series connection in every group of spring, the length of four springs of first spring to the increases successively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200870452U CN201129396Y (en) | 2007-09-20 | 2007-09-20 | Dual mass flywheel torsional vibration damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007200870452U CN201129396Y (en) | 2007-09-20 | 2007-09-20 | Dual mass flywheel torsional vibration damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201129396Y true CN201129396Y (en) | 2008-10-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007200870452U Expired - Lifetime CN201129396Y (en) | 2007-09-20 | 2007-09-20 | Dual mass flywheel torsional vibration damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201129396Y (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102278416A (en) * | 2011-06-30 | 2011-12-14 | 奇瑞汽车股份有限公司 | Torsional absorber |
| CN102384242A (en) * | 2011-11-24 | 2012-03-21 | 张家港大研车辆部件有限公司 | Crankshaft pulley |
| CN102606677A (en) * | 2012-03-29 | 2012-07-25 | 浙江吉利汽车研究院有限公司 | Damping flywheel device in automobile engine |
| CN102072277B (en) * | 2009-01-07 | 2014-07-30 | 艾勒根传动工程有限责任公司 | Torsional vibration damper |
| CN104198181A (en) * | 2014-07-31 | 2014-12-10 | 长城汽车股份有限公司 | Method and system for resonance detection of dual mass flywheel |
| TWI604141B (en) * | 2016-11-07 | 2017-11-01 | 財團法人工業技術研究院 | Shock absorber and semi-active type shock absorbing method |
| CN107816508A (en) * | 2017-11-17 | 2018-03-20 | 合肥工业大学 | A kind of torsional vibration damper and clutch of integrated dynamic vibration absorber |
| CN108119605A (en) * | 2017-12-22 | 2018-06-05 | 宁波宏协股份有限公司 | A kind of double mass flywheel with sliding shoe formula centrifugal pendulum |
| WO2020133070A1 (en) * | 2018-12-27 | 2020-07-02 | Nanjing Valeo Clutch Co., Ltd. | Flywheel apparatus for use with vehicles |
| CN111577776A (en) * | 2020-06-18 | 2020-08-25 | 福建省晋江市科华汽配有限公司 | Damping coupling and damping connection method |
-
2007
- 2007-09-20 CN CNU2007200870452U patent/CN201129396Y/en not_active Expired - Lifetime
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102072277B (en) * | 2009-01-07 | 2014-07-30 | 艾勒根传动工程有限责任公司 | Torsional vibration damper |
| CN102278416B (en) * | 2011-06-30 | 2013-01-02 | 奇瑞汽车股份有限公司 | Torsional absorber |
| CN102278416A (en) * | 2011-06-30 | 2011-12-14 | 奇瑞汽车股份有限公司 | Torsional absorber |
| CN102384242B (en) * | 2011-11-24 | 2013-01-30 | 张家港大研车辆部件有限公司 | Crankshaft pulley |
| CN102384242A (en) * | 2011-11-24 | 2012-03-21 | 张家港大研车辆部件有限公司 | Crankshaft pulley |
| CN102606677A (en) * | 2012-03-29 | 2012-07-25 | 浙江吉利汽车研究院有限公司 | Damping flywheel device in automobile engine |
| CN102606677B (en) * | 2012-03-29 | 2014-07-16 | 浙江吉利汽车研究院有限公司 | Damping flywheel device in automobile engine |
| CN104198181A (en) * | 2014-07-31 | 2014-12-10 | 长城汽车股份有限公司 | Method and system for resonance detection of dual mass flywheel |
| CN104198181B (en) * | 2014-07-31 | 2017-02-01 | 长城汽车股份有限公司 | Method and system for resonance detection of dual mass flywheel |
| TWI604141B (en) * | 2016-11-07 | 2017-11-01 | 財團法人工業技術研究院 | Shock absorber and semi-active type shock absorbing method |
| CN107816508A (en) * | 2017-11-17 | 2018-03-20 | 合肥工业大学 | A kind of torsional vibration damper and clutch of integrated dynamic vibration absorber |
| CN108119605A (en) * | 2017-12-22 | 2018-06-05 | 宁波宏协股份有限公司 | A kind of double mass flywheel with sliding shoe formula centrifugal pendulum |
| WO2020133070A1 (en) * | 2018-12-27 | 2020-07-02 | Nanjing Valeo Clutch Co., Ltd. | Flywheel apparatus for use with vehicles |
| CN111577776A (en) * | 2020-06-18 | 2020-08-25 | 福建省晋江市科华汽配有限公司 | Damping coupling and damping connection method |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: DONGFENG COMMERCIAL VEHICLE CO., LTD. Free format text: FORMER OWNER: DONGFENG AUTOMOBILE CO., LTD. Effective date: 20131211 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| COR | Change of bibliographic data |
Free format text: CORRECT: ADDRESS; FROM: 430056 WUHAN, HUBEI PROVINCE TO: 442001 SHIYAN, HUBEI PROVINCE |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20131211 Address after: 442001 Shiyan City, Hubei province city Zhangwan District Road No. 2 Patentee after: Dongfeng Commercial Vehicle Co.,Ltd. Address before: 430056 intellectual property section, No. 10 commercial vehicle technology center, Dongfeng Road, Wuhan economic and Technological Development Zone, Wuhan, Hubei Patentee before: DONGFENG MOTER Co.,Ltd. |
|
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20081008 |