CN103307201A - 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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- CN103307201A CN103307201A CN2013101768748A CN201310176874A CN103307201A CN 103307201 A CN103307201 A CN 103307201A CN 2013101768748 A CN2013101768748 A CN 2013101768748A CN 201310176874 A CN201310176874 A CN 201310176874A CN 103307201 A CN103307201 A CN 103307201A
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- telophragma
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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 the automotive transmission, and it mainly is made up of flywheel, clutch cover and plate assembly, clutch drived disk assy, release bearing and hold-down mechanism and operating mechanism, and its important function guarantees to have reliable torque transmission capacity exactly.
Along with human living standard's flourish with automotive industry of improving constantly, the travelling comfort of vehicle operating is had higher requirement.Particularly to improve the appearance of the high-end product that travelling comfort, fuel consume and discharging are main feature----double-clutch automatic gearbox (DCT), driving comfortability is significantly promoted, unprecedented stationarity can promote fuel efficiency and reduce emission of carbon-dioxide under driving cycle.In the face of premium quality product like this, traditional rigidity flywheel that is installed between motor and the gearbox, because there is not vibration damping equipment, the vibration-damping function of clutch is by the vibration damper in the clutch drived disk assy transmission system to be carried out torsion damping, the structure narrow limitation is very big, the shock-absorbing spring distribution diameter is little, and corner is little, rigidity is big, can't reach due effectiveness in vibration suppression.Particularly sudden change has taken place in speed ratio before and after the transmission system gear shift, certainly leads to torsional vibration and impacts, and the double mass flywheel that presses for the good tool torsion damping mechanism of structure absorbs torsional vibration in double-clutch automatic gearbox.And existing double mass flywheel friction pair is many, and running resistance is big, in torsion damping design, overcome aspects such as idling resonance, damping member layout and exist more problem, and the vibration damping and vibration isolation that is difficult to realize ideal and overcome the effect that idling resonates.
Summary of the invention
The objective of the invention is to overcome above-mentioned deficiency, and a kind of double mass flywheel that has the favorable damping vibration isolation and overcome the double-clutch automatic gearbox of idling resonance is provided.
Purpose of the present invention realizes by following technical solution: the double mass flywheel of double-clutch automatic gearbox, comprise the primary flywheel body, the secondary flywheel body, flywheel ring gear, the telophragma assembly, between described primary flywheel body and secondary flywheel body, the outer arcuate spring is housed, the arc spring, telophragma middle part at described telophragma assembly arranges the power output gear, the telophragma of described telophragma assembly has " protruding " font spring cup in order to the idling shock-absorbing spring of telophragma assembly to be installed, the interior shape tooth of the middle disk cover of described telophragma assembly adopts zigzag structure, its short tooth is " n " type toothing, and its long tooth perk is configured as the upward trend shape in order to penetrate described idling shock-absorbing spring.
Of the present invention further the improvement is: between described primary flywheel body and the telophragma assembly, between secondary flywheel body and the telophragma assembly the first damping clamping piece, the second damping clamping piece are housed respectively, between described telophragma assembly and the first damping clamping piece, the second damping clamping piece butterfly spring is housed.Thereby in the certain attenuation scope of second, the first damping clamping piece, keep constant substantially axial pressing force, play the effect of effective resistance damping vibration attenuation, for system provides stable damping.
After adopting the present invention, side below " protruding " font spring cup of telophragma is constantly driven between the long tooth of idling shock-absorbing spring and middle disk cover form the idling vibration damping structure, idling resonance is absorbed by the idling shock-absorbing spring, avoided the power train torsional resonance that the engine torque fluctuation causes under idling and the operating mode commonly used, eliminate speed changer and body noise, significantly improved the travelling comfort of taking.Simultaneously, " n " type tooth of middle disk cover is subjected to the effect of idling shock-absorbing spring, make the power input tooth of power output gear and double clutch cap assembly keep certain coupled condition, play compensating action, overcome effectively that rigid contact between tooth and the tooth connects and the expendable wearing clearance that causes, thereby improved performance and the using effect of product.
Description of drawings
The present invention is described in further detail below in conjunction with accompanying drawing and mode of execution.
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 among Fig. 1.
Fig. 5 is the middle disk cover structural representation of the telophragma assembly among Fig. 4.
Fig. 6 is the structural representation of the secondary flywheel body among 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 that 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), (by cambered way 7) is equipped with outer arcuate spring 8, arc spring 9(and spring seat 10 between described primary flywheel body 1 and secondary flywheel body 6).
As shown in Figure 2, between described primary flywheel body 1 and the telophragma assembly 4, between secondary flywheel body 6 and the telophragma assembly 4 the first damping clamping piece 3, the second damping clamping piece 2 are housed respectively, by major and minor flywheel body 1,6, outside, in the middle of the vibration damper formed such as arc spring 8,9, telophragma assembly 4 the axial elasticity structure is set, namely between described telophragma assembly 4 and the first damping clamping piece 3, the second damping clamping piece 2, butterfly spring 5 is housed.Thereby in second, the first damping clamping piece 2,3 certain attenuation scopes, keep constant substantially axial pressing force, play the effect of effective resistance 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 be provided with ring-like vallecular cavity at primary flywheel body 1 and secondary flywheel body 6 inboards, in order to outer, the arc spring 8,9 of damping effect to be installed, arc spring 9 in the two ends of described outer arcuate spring 8 are provided with 0.3～0.4 times of scope that arc length is outer arcuate spring 8, the end face close-fitting of arc spring 9 is on spring seat 10.Be not provided with how much of two jump ring boss 16(jump ring boss two sides in major and minor flywheel body 1,6 annular vallecular cavity intermediate section
When the angle setting meets circumferential rotate and the working principle that matches of spring seat 10 end faces require),, arc spring 8 outer in order to clamping, 9 and spring seat 10 plays position-limiting action.During work, two claws, the 411 driving spring seats 10 of the telophragma 41 of telophragma assembly 4, compression outer arcuate spring 8 is worked earlier, forms the first order vibration damping of main vibration damping; When reaching certain corner (central angle that outer arcuate spring 8 arc length deduct two arc spring 9 arc length correspondences namely is the corner of main vibration damping one-level vibration damping), arc spring 9 begins butt joint and starts working by compression, form state outer, that arc spring 8,9 is worked together, realize the purpose of main vibration damping secondary vibration damping.Because have only outer arcuate spring 8 to work, rigidity is very little in main vibration damping one-level vibration damping, satisfies the job requirement when normally travelling.When vehicle accelerates, moment of torsion can satisfy job requirement with the secondary vibration damping of main vibration damping when strengthening.Its design science is reasonable, reaches the favorable damping effect.
As shown in Figure 4, described telophragma assembly 4 is provided with pre-vibration damping and compensation mechanism, namely at telophragma 41 middle parts of described telophragma assembly 4 power output gear 413 is set, the telophragma 41 of described telophragma assembly 4 has " protruding " font spring cup 412(and adopts punching press flange technology, at " protruding " font flange edge auxiliary hole is set rationally and satisfies the flanging process requirement) in order to the idling shock-absorbing spring 43 of telophragma assembly 4 to be installed, the outside of telophragma is satisfied and second, the first damping clamping piece 2,3 cooperation installation requirement.As shown in Figure 1, power imports the master by motor into through flywheel ring gear 11, secondary flywheel body 1,6, again by outside the elastic damping mechanism, the arc spring, by the master, between the jump ring boss of secondary flywheel body and the telophragma claw 411 outside circumferentially rotating to compress, interior shock-absorbing spring 8,9, at last with power output gear 413 outputs of power by telophragma 41 middle parts, the power output gear 413 of telophragma 41 and the power of double clutch input fluted disc are connected, thereby with the cap assembly of transmission of power to the double clutch, import gearbox into through the clutch drived disk assy spline again, finish power transmission process.As shown in Figure 5, the interior shape tooth of the middle disk cover 42 of described telophragma assembly 4 adopts the zigzag structure design, and its short tooth is that " n " type toothing 421(is namely by the shape style of rectangle openings at one side, warp again
The double bending of 90 degree constitutes), its long tooth 422 perks are configured as the upward trend shape, in order to penetrate the idling shock-absorbing spring 43 of telophragma assembly 4.When telophragma lid 42 circumferentially rotates, by its long tooth 422 compression idling shock-absorbing springs 43, make the power output gear 413 of contact telophragma 41 behind the certain design angle of its " n " type tooth 421 circumferential movement, be only then that telophragma claw 411 and major and minor flywheel body 1,6 jump ring boss relatively rotate that compression is outer, arc spring 8,9 and cause that main vibration damping partly works.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 gear 413 of telophragma is pre-vibration damping angle.During vehicle idling, fluctuation during by idling constantly drives between the long tooth 422 of idling shock-absorbing spring 43 and middle disk cover the straight flange of spring inclusion cavity side card spring below telophragma 41 " protruding " the font spring cup and forms the idling vibration damping structure, idling resonance is absorbed by idling shock-absorbing spring 43, avoided the power train torsional resonance that the engine torque fluctuation causes under idling and the operating mode commonly used, eliminate speed changer and body noise, significantly improved the travelling comfort of taking.Simultaneously, " n " type tooth 421 of middle disk cover is subjected to the effect of idling shock-absorbing spring 43, the power input tooth of the power output gear 413 of telophragma 41 and double clutch cap assembly is continued insurance forever hold certain coupled condition, play compensating action, overcome effectively that rigid contact between tooth and the tooth connects and the expendable wearing clearance that causes, thereby improved performance and the using effect of product.
As Fig. 1, Fig. 2 and shown in Figure 6, top between described primary flywheel body 1 and the secondary flywheel body 6 connects the orientation type that " crescent moon " type boss and " crescent moon " type heavy stand (the mark N among Fig. 6) close-fitting are adopted in the location, namely put in order out four (two groups) " crescent moon " type heavy stands in the joint of primary flywheel body 1 sidewall upper, go out corresponding " crescent moon " type boss in the relevant position shaping of secondary flywheel body 6 joint equally.As shown in Figure 2, both are the close-fitting relation major and minor flywheel body, and during installation, major and minor flywheel body 1,6 arranges accurate butt joint by this location, have guaranteed the correctness of position relation on the one hand, on the other hand, have played good sealing locating effect, are convenient to
Follow-up welded seal implementation of processes.Accurate positioning and fixing when considering thin walled structures, are taken into account in the location of " crescent moon " type boss and heavy stand, have good science.Institute is shown in Figure 2, bottom between described primary flywheel body 1 and the secondary flywheel body 6 connects adopts laser welding technology, and adopt " Y " type groove (marking M as Fig. 2) designing technique of 60 ± 5 ° at its weld, improved the welding space, increase the area of laser bonding, improved the fixing of welding.Strengthened sealing effect simultaneously, made welding back profile more attractive in appearance.As shown in Figure 2, the close-fitting mode (marking P as Fig. 2) of 1 ± 0.5 ° of inclined to one side awl and interference 0.25～0.45mm is adopted in the connection between described flywheel ring gear 11 and the secondary flywheel body 6, and adopts laser welding technology.
As shown in Figure 1, described outer, outer side clearance that arc spring 8,9 adopts adjacent two joints of springs is the structure bigger than interior side clearance all, the right central angle free state of its arc spring center line is bigger 5～10 ° than installment state, and the curve bath between the arcuate shape of its installment state and major and minor flywheel body 1,6 inwalls matches.Described cambered way 7 adopts the high abrasion resisting material thermoformings to be made, and the right central angle free state of its arc is littler 4～8 ° than installment state, and the curve bath between the arcuate shape of its installment state and major and minor flywheel body 1,6 inwalls matches.
As shown in figures 1 and 3, described primary flywheel body 1 adopts whole locating pin structure, by modern punching press shaping technique, namely put in order out locating stud 13 at the matrix of described primary flywheel body 1, changed the split mode of structure of close-fitting assembling between traditional positioning hole and the locating stud, promote part precision and reliability greatly, make the positioning performance of product better, balance is more superior.Before the double mass flywheel of the present invention assembling, all parts clean up, outer, arc spring 8,9 and arcuate furrow in be full of high temperature grease.As shown in Figure 6, described secondary flywheel body 6 inwalls are provided with rectangle heavy stand 61, can hold the fine impurity that produces in outer, arc spring 8,9 motions and the lubricating grease, guarantee its efficient proper functioning.Its rectangle heavy stand outside is because be that projection is come, and can play good positioning action to flywheel ring gear in being connected of secondary flywheel body 6 and flywheel ring gear 11 again, makes its connection more reliable.
Claims (8)
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: telophragma (41) middle part at described telophragma assembly (4) arranges power output gear (413), the telophragma (41) of described telophragma assembly (4) has " protruding " font spring cup (412) in order to the idling shock-absorbing spring (43) of telophragma assembly (4) to be installed, 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), and its long tooth (422) perk is configured as the 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: between described primary flywheel body (1) and the telophragma assembly (4), between secondary flywheel body (6) and the telophragma assembly (4) the first damping clamping piece (3), the second damping clamping piece (2) are housed respectively, 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 arc spring (9) in the two ends of described outer arcuate spring (8) are provided with 0.3～0.4 times of scope that arc length is outer arcuate spring (8), 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: described outer, outer side clearance that arc spring (8,9) adopts adjacent two joints of spring is the structure bigger than interior side clearance all, the right central angle free state of its arc spring center line is bigger 5～10 ° than installment state, and the curve bath between the arcuate shape of its installment state and major and minor flywheel body (1, the 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 the secondary flywheel body (6) connects the orientation type that " crescent moon " type boss and " crescent moon " type heavy stand close-fitting are adopted in the location, and the bottom between described primary flywheel body (1) and the secondary flywheel body (6) connects 60 ± 5 ° " Y " type groove mode that adopts.
6. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 5 is characterized in that: 1 ± 0.5 ° of the inclined to one side awl of connection employing between described flywheel ring gear (11) and the secondary flywheel body (6) and the close-fitting mode of interference 0.25～0.45mm.
7. 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 whole locating pin structure, namely puts in order out locating stud (13) at the matrix of described primary flywheel body (1).
8. the double mass flywheel of double-clutch automatic gearbox as claimed in claim 7, it is characterized in that: described secondary flywheel body (6) inwall is provided with rectangle heavy stand (61).
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 |
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| Publication Number | Publication Date |
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| CN103307201A true CN103307201A (en) | 2013-09-18 |
| CN103307201B CN103307201B (en) | 2015-03-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| 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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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108730409A (en) * | 2017-04-20 | 2018-11-02 | 上海汽车集团股份有限公司 | Automobile and double mass flywheel |
| CN114341523A (en) * | 2019-09-02 | 2022-04-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper with centrifugal pendulum and predamper |
| CN114857214A (en) * | 2022-04-25 | 2022-08-05 | 湖北三环离合器有限公司 | Dual-mass flywheel integrated with multistage damping system |
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| 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 |
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| 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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2013
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Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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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 |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108730409A (en) * | 2017-04-20 | 2018-11-02 | 上海汽车集团股份有限公司 | Automobile and double mass flywheel |
| CN114341523A (en) * | 2019-09-02 | 2022-04-12 | 舍弗勒技术股份两合公司 | Torsional vibration damper with centrifugal pendulum and predamper |
| CN114341523B (en) * | 2019-09-02 | 2024-03-05 | 舍弗勒技术股份两合公司 | Torsional vibration damper with centrifugal pendulum and pre-damper |
| CN114857214A (en) * | 2022-04-25 | 2022-08-05 | 湖北三环离合器有限公司 | Dual-mass flywheel integrated with multistage damping system |
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| CN103307201B (en) | 2015-03-11 |
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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 |
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| CF01 | Termination of patent right due to non-payment of annual fee |