CN103307201B - Double-mass flywheel for double-clutch automatic speed changer - Google Patents
Double-mass flywheel for double-clutch automatic speed changer Download PDFInfo
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- CN103307201B CN103307201B CN201310176874.8A CN201310176874A CN103307201B CN 103307201 B CN103307201 B CN 103307201B CN 201310176874 A CN201310176874 A CN 201310176874A CN 103307201 B CN103307201 B CN 103307201B
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- double
- spring
- telophragma
- assembly
- flywheel body
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Abstract
The invention discloses a double-mass flywheel for a double-clutch automatic speed changer. A convex and a concave springs are arranged between a main flywheel body and an auxiliary flywheel body of the double-mass flywheel, power output teeth are arranged in the middle part of a middle disc (41) of a middle disc assembly of the double-mass flywheel, the middle disc is provided with a convex spring cover (412) for assembling an idle speed shock absorption spring of the middle disc assembly, the concave teeth of a middle disc cover (42) of the middle disc assembly adopts a sawtooth shaped structure, the short teeth of the sawtooth shaped structure are of an n-shaped teeth structure (421), and the long teeth (422) tilt to form an upward slope shape. According to the flywheel, torsional oscillation and resonance of a transmission system caused by fluctuation of an engine torque at an idle speed and in a common working condition are avoided, noise of the speed changer and a vehicle body is eliminated, and comfort of the taking is remarkably improved. Meanwhile, power input teeth and the power input teeth of a double-clutch cover assembly are enabled to be maintained in a certain connection status to realize compensation function, the abrasion gap which is unrecoverable caused by hard contact connection between teeth is effectively overcome, and the performance and the use effect of a product is improved.
Description
Technical field
The present invention relates to a kind of automobile clutch, specifically relate to a kind of double mass flywheel of double-clutch automatic gearbox.
Background technique
Clutch is the vitals in automotive transmission, and it is primarily of flywheel, clutch cover and plate assembly, clutch drived disk assy, release bearing and hold-down mechanism and operating mechanism composition, and its important function ensures to have reliable torque transmission capacity exactly.
Along with human living standard to improve constantly with automotive industry flourish, the travelling comfort of vehicle operating is had higher requirement.Particularly to improve the high-end product that travelling comfort, fuel consume and discharge are main feature---the appearance of-double-clutch automatic gearbox (DCT), driving comfortability is significantly promoted, unprecedented stationarity, can promote the discharge of fuel efficiency and reduction carbon dioxide under driving cycle.In the face of premium quality product like this, traditional installation rigidity flywheel between the engine and the gearbox, because there is no vibration damping equipment, the vibration-damping function of clutch carries out torsion damping by the vibration damper in clutch drived disk assy to transmission system, structural limitations is very large, shock-absorbing spring distribution diameter is little, and corner is little, rigidity is large, cannot reach due effectiveness in vibration suppression.Particularly before and after transmission system gear shift, speed ratio there occurs sudden change, and certainly lead to torsional vibration and impact, the double mass flywheel in the urgent need to the excellent tool torsion damping mechanism of structure absorbs torsional vibration in double-clutch automatic gearbox.And existing double mass flywheel friction pair is many, running resistance is large, in torsion damping design, overcomes in idling resonance, damping member layout etc. and there is more problem, is difficult to the vibration damping and vibration isolation of realizing ideal and overcomes the effect that idling resonates.
Summary of the invention
The object of the invention is to overcome above-mentioned deficiency, and a kind of double mass flywheel having good vibration damping and vibration isolation and overcome the double-clutch automatic gearbox that idling resonates is provided.
Object of the present invention realizes by following technical solution: the double mass flywheel of double-clutch automatic gearbox, comprise primary flywheel body, secondary flywheel body, flywheel ring gear, telophragma assembly, between described primary flywheel body and secondary flywheel body, outer arcuate spring is housed, arc spring, in the middle part of the telophragma of described telophragma assembly, Power output tooth is set, the telophragma of described telophragma assembly has " convex " font spring cup in order to install the idling shock-absorbing spring of telophragma assembly, the interior shape tooth of the middle disk cover of described telophragma assembly adopts zigzag structure, its short tooth is " n " type toothing, its long tooth tilts and is configured as upward trend shape in order to penetrate described idling shock-absorbing spring.
Of the present invention further improvement is: the first damping clamping piece, the second damping clamping piece are housed respectively between described primary flywheel body and telophragma assembly, between secondary flywheel body and telophragma assembly, between described telophragma assembly and the first damping clamping piece, the second damping clamping piece, butterfly spring are housed.Thus substantially constant axial pressing force is kept in the thinning scope that the second, first damping clamping piece is certain, play the effect of effectively resisting damping vibration attenuation, for system provides stable damping.
After adopting the present invention, by idling fluctuation, the side below " convex " font spring cup of telophragma is constantly driven between idling shock-absorbing spring and the long tooth of middle disk cover and form idling vibration damping structure, idling resonance absorb by idling shock-absorbing spring, avoid the power train torsional resonance that motor torque ripple causes under idling and conventional operating mode, eliminate speed changer and body noise, significantly improve the travelling comfort taken.Simultaneously, " n " type tooth of middle disk cover is subject to the effect of idling shock-absorbing spring, make the power of Power output tooth and double clutch cap assembly input tooth and keep certain coupled condition, play compensating action, the expendable wearing clearance that the hard contact effectively overcome between tooth and tooth connects and causes, thus improve performance and the using effect of product.
Accompanying drawing explanation
Below in conjunction with accompanying drawing and mode of execution, the present invention is described in further detail.
Fig. 1 is the structural representation of the double mass flywheel of double-clutch automatic gearbox of the present invention.
Fig. 2 is the A-A sectional view of Fig. 1.
Fig. 3 is the X-X partial sectional view of Fig. 1.
Fig. 4 is the structural representation of the telophragma assembly in Fig. 1.
Fig. 5 is the middle disk cover structural representation of the telophragma assembly in Fig. 4.
Fig. 6 is the structural representation of the secondary flywheel body in Fig. 1.
Embodiment
As shown in Figure 1 to Figure 3, the double mass flywheel of double-clutch automatic gearbox of the present invention, comprise primary flywheel body 1, secondary flywheel body 6, flywheel ring gear 11, telophragma assembly 4(comprise telophragma 41, middle disk cover 42, idling shock-absorbing spring 43), between described primary flywheel body 1 and secondary flywheel body 6, (by cambered way 7) is equipped with outer arcuate spring 8, arc spring 9(and spring seat 10).
As shown in Figure 2, first damping clamping piece 3, second damping clamping piece 2 is housed respectively between described primary flywheel body 1 and telophragma assembly 4, between secondary flywheel body 6 and telophragma assembly 4, by major and minor flywheel body 1,6, outer, arc spring 8,9, the vibration damper centre that form such as telophragma assembly 4 arranges axial elasticity structure, namely between described telophragma assembly 4 and the first damping clamping piece 3, second damping clamping piece 2, butterfly spring 5 is housed.Thus substantially constant axial pressing force is kept in the second, first damping clamping piece 2,3 certain thinning scopes, play the effect of effectively resisting damping vibration attenuation, for system provides stable damping.
As shown in Figure 1 and Figure 2, between described primary flywheel body 1 and secondary flywheel body 6, elastic damping mechanism is set, namely inside primary flywheel body 1 and secondary flywheel body 6, ring-like vallecular cavity is provided with, in order to have installed outer, the arc spring 8,9 of damping effect, the two ends of described outer arcuate spring 8 be provided with arc length be 0.3 ~ 0.4 times of outer arcuate spring 8 within the scope of arc spring 9, the end face close-fitting of arc spring 9 is on spring seat 10.The working principle that the geometric angle being respectively arranged with two jump ring boss 16(jump ring boss two sides in the middle of the annular vallecular cavity of major and minor flywheel body 1,6 arranges when meeting circumference rotation and spring seat 10 end face matches requires), in order to clamp outer, arc spring 8,9 and spring seat 10, play position-limiting action.During work, two claw 411 driving spring seats 10 of the telophragma 41 of telophragma assembly 4, first compress outer arcuate spring 8 and work, form the first order vibration damping of main vibration damping; When reaching certain corner (outer arcuate spring 8 arc length deducts the corner that namely central angle corresponding to two arc spring 9 arc length be main vibration damping one-level vibration damping), arc spring 9 starts docking and starts working by compression, the state that formation is outer, arc spring 8,9 works together, realizes the object of main vibration damping secondary vibration damping.Because only have outer arcuate spring 8 to work in main vibration damping one-level vibration damping, rigidity is very little, meets job requirement during normal traveling.When vehicle acceleration, moment of torsion can meet job requirement with the secondary vibration damping of main vibration damping when strengthening.Its design science is reasonable, reaches good effectiveness in vibration suppression.
As shown in Figure 4, described telophragma assembly 4 is provided with pre-vibration damping and compensation mechanism, namely Power output tooth 413 is set in the middle part of the telophragma 41 of described telophragma assembly 4, the telophragma 41 of described telophragma assembly 4 has " convex " font spring cup 412(and adopts punching press flange technology, auxiliary hole is rationally set at " convex " font flange edge and meets flanging process requirement) in order to install the idling shock-absorbing spring 43 of telophragma assembly 4, the outside of telophragma meets the cooperation installation requirement with the second, first damping clamping piece 2,3.As shown in Figure 1, power imports master by motor into through flywheel ring gear 11, secondary flywheel body 1, 6, again by outside elastic damping mechanism, arc spring, by master, between the jump ring boss of secondary flywheel body and telophragma claw 411 outside circumference is rotated and is compressed, interior shock-absorbing spring 8, 9, finally power is exported by the Power output tooth 413 in the middle part of telophragma 41, the Power output tooth 413 of telophragma 41 is connected with the power input fluted disc of double clutch, thus by transmission of power to the cap assembly on double clutch, gearbox is imported into again through clutch drived disk assy spline, complete power transmission process.As shown in Figure 5, the interior shape tooth of the middle disk cover 42 of described telophragma assembly 4 adopts zigzag structure design, its short tooth be " n " type toothing 421(namely by rectangle openings at one side shape style, form through 90 degree of double bendings again), its long tooth 422 tilts and is configured as upward trend shape, in order to penetrate the idling shock-absorbing spring 43 of telophragma assembly 4.When telophragma lid 42 circumference is rotated, idling shock-absorbing spring 43 is compressed by its long tooth 422, contact the Power output tooth 413 of telophragma 41 after making the certain design angle of its " n " type tooth 421 circumferential movement, the jump ring boss being then only telophragma claw 411 and major and minor flywheel body 1,6 relatively rotate that compression is outer, arc spring 8,9 and cause main shock absorber section work.As shown in Figure 4, the angle of the gap portion circumferential movement contact between " n " type tooth 421 of middle disk cover and the Power output tooth 413 of telophragma, is pre-vibration damping angle.During vehicle idling, made by the fluctuation during idling straight flange of diaphragm flexures inclusion cavity side card spring under " convex " font spring cup of telophragma 41 constantly drive between idling shock-absorbing spring 43 and the long tooth 422 of middle disk cover and form idling vibration damping structure, idling resonance absorb by idling shock-absorbing spring 43, avoid the power train torsional resonance that motor torque ripple causes under idling and conventional operating mode, eliminate speed changer and body noise, significantly improve the travelling comfort taken.Simultaneously, " n " type tooth 421 of middle disk cover is subject to the effect of idling shock-absorbing spring 43, the power of the Power output tooth 413 of telophragma 41 and double clutch cap assembly input tooth is continued insurance forever and holds certain coupled condition, play compensating action, the expendable wearing clearance that the hard contact effectively overcome between tooth and tooth connects and causes, thus improve performance and the using effect of product.
As shown in Figure 1, Figure 2 with shown in Fig. 6, top between described primary flywheel body 1 and secondary flywheel body 6 connects the orientation type that location adopts " crescent moon " type boss and " crescent moon " type heavy stand (the mark N in Fig. 6) close-fitting, namely in the joint of primary flywheel body 1 sidewall upper whole go out four (two groups) " crescent moon " type heavy stands, go out corresponding " crescent moon " type boss in the relevant position shaping of secondary flywheel body 6 joint equally.As shown in Figure 2, major and minor both flywheel bodies are close-fitting relation, during installation, major and minor flywheel body 1,6 arranges accurate docking by this location, ensure that the correctness of position relationship on the one hand, on the other hand, serve good sealing locating effect, be convenient to the enforcement of follow-up welded seal technique.The location of " crescent moon " type boss and heavy stand, while consideration thin walled structures, takes into account positioning accurate parasexuality and fixing, has good science.Shown in institute Fig. 2, bottom between described primary flywheel body 1 and secondary flywheel body 6 connects employing laser welding technology, and " Y " type groove (as Fig. 2 the marks M) designing technique of 60 ± 5 ° is adopted at its weld, improve welding space, increase the area of laser bonding, improve the fixing of welding.Enhance sealing effect, after making welding, profile is more attractive in appearance simultaneously.As shown in Figure 2, the connection between described flywheel ring gear 11 and secondary flywheel body 6 adopts the close-fitting mode (as Fig. 2 marks P) of cone 1 ± 0.5 ° and interference 0.25 ~ 0.45mm partially, and adopts laser welding technology.
As shown in Figure 1, the structure that described lateral gap that is outer, adjacent two joints of arc spring 8,9 employing spring is all large than medial gap, larger than installment state 5 ~ 10 ° of the central angle free state that its arc spring center line is right, and the curve bath between the arcuate shape of its installment state and major and minor flywheel body 1,6 inwall matches.Described cambered way 7 adopts high abrasion resisting material thermoforming to be made, and the right central angle free state of its arc is less than installment state 4 ~ 8 °, and the curve bath between the arcuate shape of its installment state and major and minor flywheel body 1,6 inwall matches.
As shown in figures 1 and 3, described primary flywheel body 1 adopts overall locating pin structure, by modern punching press shaping technique, namely on the matrix of described primary flywheel body 1 whole go out locating stud 13, change the Split type structure mode of close-fitting assembling between traditional positioning hole and locating stud, greatly promote precision and the reliability of part, make the positioning performance of product better, balance is more superior.Before double mass flywheel of the present invention assembling, whole Cleaning of Parts is clean, is full of high temperature grease in outer, arc spring 8,9 and arcuate furrow.As shown in Figure 6, described secondary flywheel body 6 inwall is provided with rectangle heavy stand 61, can hold the fine impurity that outer, arc spring 8,9 moves and produces in lubricating grease, ensure its efficient normal work.Outside its rectangle heavy stand because be protruding come, in the connection of secondary flywheel body 6 and flywheel ring gear 11, good positioning action can be played to flywheel ring gear again, make it connect more reliable.
Claims (6)
1. the double mass flywheel of double-clutch automatic gearbox, comprise primary flywheel body (1), secondary flywheel body (6), flywheel ring gear (11), telophragma assembly (4), between described primary flywheel body (1) and secondary flywheel body (6), outer arcuate spring (8) is housed, arc spring (9), it is characterized in that: at telophragma (41) middle part of described telophragma assembly (4), Power output tooth (413) is set, the telophragma (41) of described telophragma assembly (4) has " convex " font spring cup (412) in order to install the idling shock-absorbing spring (43) of telophragma assembly (4), the interior shape tooth of the middle disk cover (42) of described telophragma assembly (4) adopts zigzag structure, its short tooth is " n " type toothing (421), its long tooth (422) tilts and is configured as upward trend shape in order to penetrate described idling shock-absorbing spring (43).
2. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 1, it is characterized in that: the first damping clamping piece (3), the second damping clamping piece (2) are housed respectively between described primary flywheel body (1) and telophragma assembly (4), between secondary flywheel body (6) and telophragma assembly (4), between described telophragma assembly (4) and the first damping clamping piece (3), the second damping clamping piece (2), butterfly spring (5) is housed.
3. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 1 or 2, it is characterized in that: the two ends of described outer arcuate spring (8) be provided with arc length be 0.3 ~ 0.4 times of outer arcuate spring (8) within the scope of arc spring (9), the end face close-fitting of arc spring (9) is on spring seat (10).
4. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 3, it is characterized in that: the structure that described lateral gap that is outer, adjacent two joints of arc spring (8,9) employing spring is all large than medial gap, larger than installment state 5 ~ 10 ° of the central angle free state that its arc spring center line is right, and the curve bath between the arcuate shape of its installment state and major and minor flywheel body (1,6) inwall matches.
5. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 1 or 2, it is characterized in that: the top between described primary flywheel body (1) and secondary flywheel body (6) connects the orientation type that location adopts " crescent moon " type boss and " crescent moon " type heavy stand close-fitting, and the bottom between described primary flywheel body (1) and secondary flywheel body (6) connects " Y " type groove mode of employing 60 ± 5 °.
6. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 1 or 2, it is characterized in that: described primary flywheel body (1) adopts overall locating pin structure, by punching press shaping technique, namely on the matrix of described primary flywheel body (1) whole go out locating stud (13).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310176874.8A CN103307201B (en) | 2013-05-14 | 2013-05-14 | Double-mass flywheel for double-clutch automatic speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310176874.8A CN103307201B (en) | 2013-05-14 | 2013-05-14 | Double-mass flywheel for double-clutch automatic speed changer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103307201A CN103307201A (en) | 2013-09-18 |
| CN103307201B true CN103307201B (en) | 2015-03-11 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310176874.8A Expired - Fee Related CN103307201B (en) | 2013-05-14 | 2013-05-14 | Double-mass flywheel for double-clutch automatic speed changer |
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| CN (1) | CN103307201B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108730409B (en) * | 2017-04-20 | 2020-05-01 | 上海汽车集团股份有限公司 | Automobile and dual mass flywheel |
| DE102020121270A1 (en) * | 2019-09-02 | 2021-03-04 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper with centrifugal pendulum and pre-damper |
| CN114857214B (en) * | 2022-04-25 | 2022-11-18 | 湖北三环离合器有限公司 | Dual-mass flywheel integrated with multistage damping system |
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| EP1760356A1 (en) * | 2005-08-31 | 2007-03-07 | Valeo Embrayages | Friction clutch, in particular for motor vehicle, comprising differentiated friction means and pre-assembled module for this friction clutch |
| CN101260908A (en) * | 2007-02-08 | 2008-09-10 | 卢克摩擦片和离合器两合公司 | Torsion vibration damper |
| CN101737451A (en) * | 2009-12-30 | 2010-06-16 | 上海萨克斯动力总成部件系统有限公司 | Novel clutch driven disc intersection angle expansion damping device |
| CN101788032A (en) * | 2009-12-30 | 2010-07-28 | 上海萨克斯动力总成部件系统有限公司 | Novel vibration damper of clutch driven plate, with rotation angle added |
| CN202007859U (en) * | 2011-03-30 | 2011-10-12 | 比亚迪股份有限公司 | Torsion shock absorber and clutch cover assembly comprising torsion shock absorber |
| CN203348428U (en) * | 2013-05-14 | 2013-12-18 | 浙江华信汽车零部件有限公司 | Double-flywheel of automatic transmission with double clutches |
| CN203743304U (en) * | 2013-05-14 | 2014-07-30 | 浙江华信汽车零部件有限公司 | Dual mass flywheel for double clutch automatic gearbox |
-
2013
- 2013-05-14 CN CN201310176874.8A patent/CN103307201B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1760356A1 (en) * | 2005-08-31 | 2007-03-07 | Valeo Embrayages | Friction clutch, in particular for motor vehicle, comprising differentiated friction means and pre-assembled module for this friction clutch |
| CN101260908A (en) * | 2007-02-08 | 2008-09-10 | 卢克摩擦片和离合器两合公司 | Torsion vibration damper |
| CN101737451A (en) * | 2009-12-30 | 2010-06-16 | 上海萨克斯动力总成部件系统有限公司 | Novel clutch driven disc intersection angle expansion damping device |
| CN101788032A (en) * | 2009-12-30 | 2010-07-28 | 上海萨克斯动力总成部件系统有限公司 | Novel vibration damper of clutch driven plate, with rotation angle added |
| CN202007859U (en) * | 2011-03-30 | 2011-10-12 | 比亚迪股份有限公司 | Torsion shock absorber and clutch cover assembly comprising torsion shock absorber |
| CN203348428U (en) * | 2013-05-14 | 2013-12-18 | 浙江华信汽车零部件有限公司 | Double-flywheel of automatic transmission with double clutches |
| CN203743304U (en) * | 2013-05-14 | 2014-07-30 | 浙江华信汽车零部件有限公司 | Dual mass flywheel for double clutch automatic gearbox |
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| CN103307201A (en) | 2013-09-18 |
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Effective date of registration: 20151020 Address after: 325207 No. two, No. 288, development road, Ruian economic and Technological Development Zone, Zhejiang Patentee after: WENZHOU RHYGUAN MACHINERY Co.,Ltd. Address before: North Ruian City Tangxia town Wenzhou city Zhejiang province 325204 Luofeng international automobile distribution base Patentee before: ZHEJIANG HUAXIN AUTOMOBILE PARTS Co.,Ltd. |
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Effective date of registration: 20160222 Address after: North Ruian City Tangxia town Wenzhou city Zhejiang province 325204 Luofeng international automobile distribution base Patentee after: ZHEJIANG HUAXIN AUTOMOBILE PARTS Co.,Ltd. Address before: 325207 No. two, No. 288, development road, Ruian economic and Technological Development Zone, Zhejiang Patentee before: WENZHOU RHYGUAN MACHINERY Co.,Ltd. |
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Granted publication date: 20150311 |