CN105179635A - Hydraulic torque converter integrated with parallel axial gear-shifting dual clutches - Google Patents
Hydraulic torque converter integrated with parallel axial gear-shifting dual clutches Download PDFInfo
- Publication number
- CN105179635A CN105179635A CN201510687109.1A CN201510687109A CN105179635A CN 105179635 A CN105179635 A CN 105179635A CN 201510687109 A CN201510687109 A CN 201510687109A CN 105179635 A CN105179635 A CN 105179635A
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- Prior art keywords
- clutch
- torque converter
- fluid torque
- plate
- shift clutch
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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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
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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
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention discloses a hydraulic torque converter integrated with parallel axial gear-shifting dual clutches. The gear-shifting dual clutches are arranged in the hydraulic torque converter in an axial parallel manner. The hydraulic torque converter has the advantages that the gear-shifting dual clutches are integrated in the hydraulic torque converter in the axial parallel manner, multi-piece friction plates in the two gear-shifting clutches are arranged on two sides of a center plate in a bilateral symmetry manner and integrally formed with the middle plate, so that each gear-shifting clutch can transmit torque to the maximum, the clutches are more stable and more gentle during engaging, and the defect of obvious cadence during low-gear low-speed advancing can be overcome.
Description
Technical field
The present invention relates to a kind of fluid torque converter, be particularly applied to the fluid torque converter of a kind of integrated parallel-axis type gearshift double clutch of double-clutch automatic gearbox.
Background technique
Fluid torque converter is applied in automatic transmission, and set up flexibly connecting and transmission between power train and motor, thus make vehicle starting steadily, accelerate even, soft.Owing to having higher transmission efficiency, good fuel economy, and motion speed faster, make double-clutch automatic gearbox be developed by leaps and bounds.But the electric control clutch of double-clutch automatic gearbox is complicated and don't stable, makes the automobile being furnished with double-clutch automatic gearbox easily produce shake when starting to walk, moving ahead under low-grade low-speed situations and easily occurring pause and transition in rhythm or melody sense, thus the travelling comfort that impact is driven.Owing to not connecting twin shaft, traditional fluid torque converter cannot directly be applied in double-clutch automatic gearbox.
Therefore, need to develop a kind of fluid torque converter being integrated with parallel to an axis formula double clutch, replace the double clutch in double-clutch automatic gearbox, fluid torque converter is applied in double-clutch speed changer by the basis of ECU (Electrical Control Unit) not changing double-clutch speed changer, thus makes double-clutch automatic gearbox not only have the high advantage of wet dual clutch transmission transmission efficiency but also there is hydraulic automatic speed variator power character and the good advantage of travelling comfort.
Summary of the invention
Technical problem to be solved by this invention is the fluid torque converter that will provide a kind of integrated parallel-axis type gearshift double clutch, makes that starting is more smooth-going, travelling comfort is high, and overcomes low-grade low speed and to move ahead the obvious defect of pause and transition in rhythm or melody sense.
In order to solve above technical problem, the invention provides the fluid torque converter of a kind of integrated parallel-axis type gearshift double clutch, the built-in gearshift double clutch of described fluid torque converter is the inside being arranged in fluid torque converter in the mode of parallel to an axis.
Described fluid torque converter comprises lid, contiguous block, lock-up clutch, torsional vibration damper, gearshift double clutch and hydraulic circular part, described torsional vibration damper comprises vibration damping clamping hub, shock-absorbing spring and vibration damping drive plate, vibration damping clamping hub is connected with the piston plate of lock-up clutch, and between vibration damping clamping hub and vibration damping drive plate, parallel to an axis places a pair gearshift double clutch.
Described a pair gearshift double clutch comprises shift clutch A and shift clutch B, and shift clutch A is connected with torsional vibration damper by connecting plate with shift clutch B.
Described shift clutch A comprises retainer A, supporting frame A, piston plate A, baffle plate A and multidisc friction plate A, and described retainer A is connected with shaft sleeve plate, and shaft sleeve plate is connected with transmission input shaft one.
Described shift clutch B comprises retainer B, supporting frame B, piston plate B, baffle plate B and multidisc friction plate B, and the supporting frame B of described shift clutch B is connected with transmission input shaft two.
The supporting frame of described shift clutch A and shift clutch B has some oilholes, in order to logical oil and cooling.
The retainer A of described shift clutch A and the retainer B of shift clutch B links together.
Described lock-up clutch comprises piston plate, friction plate and one-way valve, and friction plate is attached on piston plate, and when lock-up clutch locking, friction plate is fitted with lid; Piston plate and one-way valve are fixed, and piston plate is provided with aperture, make fluid can only from the one-sided inflow of aperture piston plate.
Described hydraulic circular part comprises turbine, guide wheel and pump impeller, and described turbine is connected with the vibration damping drive plate of torsional vibration damper, and described pump impeller welds with lid the shell forming whole fluid torque converter, is provided with described guide wheel between described turbine and described pump impeller.
Described contiguous block is welded on and covers, and its effect is that the moment of torsion of motor is delivered to fluid torque converter.
The dual input shaft of the gearshift double clutch connection gearbox that described fluid torque converter is built-in, is directly installed on double-clutch speed changer.
Fluid torque converter of the present invention has six oil circuit fuel feeding: oil circuit one is oil circuit control, the combination being controlled lock-up clutch by piston plate mobile be separated; Oil circuit two is cooling oil paths, cools shift clutch B; Oil circuit three is oil circuit controls, is moved the work controlling shift clutch B by the piston plate controlling shift clutch B; Oil circuit four is oil circuit controls, is moved the work controlling shift clutch A by the piston controlling shift clutch A; Oil circuit five is cooling oil paths, is cooled shift clutch A by the one-way valve on lockup piston plate; Oil circuit six is cooling oil paths, cools the whole fluid power part of fluid torque converter.
When automobile is in starting boost phase, the moment of torsion of motor is passed to by the contiguous block covered and covers, and lid and pump impeller housing link together, and therefore pump impeller rotates.Oil circuit one and oil circuit six work, fluid enters between lock-up clutch and lid from oil circuit six, oil pressure now on the left of piston plate is greater than the oil pressure on the right side of piston plate, liquid stream moves on the left of piston plate on the right side of piston plate, piston plate can move right, friction plate and lid do not paste and, now lock-up clutch is inoperative, and fluid only plays the effect cooled the fluid power part of whole fluid torque converter.When fluid constantly enters the fluid power part of fluid torque converter by oil circuit one, make the oil pressure on the right side of piston plate be greater than oil pressure on the left of piston plate, liquid stream moves on the right side of piston plate on the left of piston plate, and piston plate can be moved to the left, friction plate will stick together in lid, and produce sliding rubbing.Meanwhile, the pump impeller of rotation drives fluid to rotate, and guide wheel maintains static, and Oil shocking turbine also drives turbine to rotate, and last power is delivered to shift clutch A by turbine.This process is the process of hydraudynamic drive, and automobile can be made more smooth-going when starting.Under this operating mode, oil circuit three is full of high-voltage oil liquid, compresses the piston plate of shift clutch A, and the multidisc friction plate of shift clutch A combines, and shift clutch B is then in the state of separation.Power is delivered to transmission input shaft one by shift clutch A.Meanwhile, oil circuit directly works May Day, constantly cools shift clutch A.
When secondary speed reaches certain value or is close with pump impeller, increase the oil pressure of oil circuit one, when making the oil pressure difference of the piston plate both sides of lock-up clutch reach some values, lock-up clutch friction plate and the cunning covered are rubbed and are terminated, friction plate will along with lid synchronous rotary, clutch locking.Now lid and lock-up clutch are rigidly connected, and Engine torque is directly delivered to shift clutch A or shift clutch B by lock-up clutch.Oil circuit three or oil circuit four are full of high-voltage oil liquid, make the piston plate of shift clutch compacted, and shift clutch A or shift clutch B works, and outputs power to transmission input shaft two.
Under gearshift operating mode, between the supporting frame that fluid enters shift clutch A and shift clutch B respectively by oil circuit three and oil circuit four and piston plate, the fluid entered from oil circuit three can make the piston of shift clutch B move right, and the fluid entered from oil circuit four can make the piston of shift clutch A be moved to the left.What suppose transmission input shaft one correspondence is gear one and gear three, transmission input shaft two correspondence be gear two.When after vehicle starting, when changing to second gear from one grade, increase the oil pressure of oil circuit three and keep the oil pressure of oil circuit four constant, on the left of the piston plate of shift clutch A, oil pressure is greater than oil pressure on the right side of piston plate, piston plate moves to the right and the multidisc friction plate of shift clutch A is fitted, shift clutch A starts working, and shift clutch B is separated, and now power is delivered in two clutch gearbox by the transmission input shaft one be connected with shift clutch A.When automobile accelerates to change to third gear from second gear, increase the oil pressure of oil circuit four and keep the oil pressure of oil circuit three constant, shift clutch B is in the pre-state combined, on the right side of the piston plate of now shift clutch B, oil pressure is greater than oil pressure on the left of piston plate, piston plate moves to the left and the multidisc friction plate of shift clutch B is fitted, shift clutch B starts working, and shift clutch A is separated, now power is delivered in two clutch gearbox by the transmission input shaft two be connected with shift clutch B.Meanwhile, oil circuit five works, and cools shift clutch B.
Under each operating mode, oil circuit six is the working state being full of fluid all the time, and fluid, by the oilhole on shift clutch A and shift clutch B, cools gearshift double clutch.
Superior effect of the present invention is:
1) the present invention's double clutch of shifting gears adopts the mode of parallel to an axis to be integrated in fluid torque converter inside, multidisc friction plate in two shift clutch is symmetrically arranged in center plate both sides and with its as one, ensureing that each shift clutch can transmitting torque to greatest extent, making clutch more steady, soft when engaging;
2) the axial-radial size of the present invention's two shift clutch is more or less the same, and ensureing that each shift clutch can transmitting torque to greatest extent, making shift clutch more steady, soft when engaging;
3) fluid torque converter of the present invention can connect twin shaft, makes it possible to this fluid torque converter to be applied in double-clutch speed changer;
4) this fluid torque converter is replaced the double clutch in double-clutch automatic gearbox by the present invention, makes double-clutch automatic gearbox both have the high advantage of wet dual clutch transmission transmission efficiency, has again hydraulic automatic speed variator power character and the good advantage of travelling comfort;
5) gearshift double clutch is integrated in fluid torque converter by the present invention, can utilize the hydraudynamic drive of fluid torque converter in vehicle starting process, makes that starting is more smooth-going, travelling comfort is high, and overcomes low-grade low speed and to move ahead the obvious defect of pause and transition in rhythm or melody sense;
6) design be installed in series with double clutch and fluid torque converter is compared, and more compact structure of the present invention more can save space.
Accompanying drawing explanation
The Figure of description forming a application's part is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is structural representation of the present invention;
Fig. 2 is asphalt channel one of the present invention;
Fig. 3 is asphalt channel two of the present invention;
Fig. 4 is asphalt channel three of the present invention;
Fig. 5 is asphalt channel four of the present invention;
Fig. 6 is asphalt channel five of the present invention;
Fig. 7 is asphalt channel six of the present invention;
Number in the figure explanation
1-lid; 2-contiguous block;
3-lock-up clutch; 4-torsional vibration damper;
5-gearshift double clutch; 6-turbine;
7-guide wheel; 8-pump impeller;
9-lock-up clutch piston plate; 10-friction plate;
11-vibration damping clamping hub; 12-shock-absorbing spring;
13-vibration damping drive plate; 14-rivet;
15-rivet;
16-gear shift sleeve A;
17-retainer A; 18-multidisc friction plate A;
19-baffle plate A; 20-supporting frame A;
21-piston plate A;
22-shaft sleeve plate; 23-rivet;
24-connecting plate; 25-rivet;
26-gear shift sleeve B;
27-retainer B; 28-multidisc friction plate B;
29-baffle plate B; 30-supporting frame B;
31-piston plate B;
32-one-way valve; 33-rivet;
34-rivet; 35-transmission input shaft one;
36-transmission input shaft two.
Embodiment
Below in conjunction with accompanying drawing, embodiments of the invention are described in detail, but the multitude of different ways that the present invention can be defined by the claims and cover is implemented.
Embodiments of the invention are described in detail below in conjunction with Fig. 1.
Fig. 1 shows the structural representation of the embodiment of the present invention.As shown in Figure 1, the invention provides a kind of fluid torque converter of integrated parallel-axis type gearshift double clutch, comprise lid 1, contiguous block 2, lock-up clutch 3, torsional vibration damper 4, gearshift double clutch 5, turbine 6, guide wheel 7 and pump impeller 8.
Described contiguous block 2 is welded on lid 1, and its effect is that the moment of torsion of motor is delivered to fluid torque converter.
Described lock-up clutch 3 comprises piston plate 9 and friction plate 10, and friction plate 10 is attached on piston plate 9, and when lock-up clutch lock 3 stops, friction plate 10 is fitted with lid 1.Lock-up clutch 3 fixes an one-way valve 32 by rivet 33, makes fluid can only from one-way valve 32 1 side inflow.
Described torsional vibration damper 4 comprises vibration damping clamping hub 11, shock-absorbing spring 12 and vibration damping drive plate 13, and vibration damping clamping hub 11 is connected with piston plate 9 by rivet 14.Between vibration damping clamping hub 11 and vibration damping drive plate 13, parallel to an axis places a pair gearshift double clutch, and gearshift double clutch comprises shift clutch A16 and shift clutch B26.Shift clutch A16, shift clutch B26 are fixed by connecting plate 24 and vibration damping drive plate 13, are connected respectively with rivet 15 with 25.
Described shift clutch A16 comprises retainer A17, multidisc friction plate A18, baffle plate A19, supporting frame A20 and piston plate A21.The retainer A17 of shift clutch A16 is connected with shaft sleeve plate 22 by rivet 23, and shaft sleeve plate 22 is connected with transmission input shaft 1 by spline, in order to transmit power.
Described shift clutch B26 comprises retainer B27, multidisc friction plate B28, baffle plate B29, supporting frame B30 and piston plate B31.The supporting frame B30 of described shift clutch B is connected with transmission input shaft 2 36.Supporting frame A20, B30 of shift clutch A16 and shift clutch B26 some oilholes are opened respectively, in order to logical oil and cooling.
Described turbine 6 is linked together by rivet 34 and vibration damping drive plate 13.Pump impeller 8 is linked together with lid 1 by the mode of welding, forms the shell of whole fluid torque converter.Between turbine 6 and pump impeller 8, installed guide wheel 7, described turbine 6, guide wheel 7 and pump impeller 8 are hydraulic circular parts of this fluid torque converter.
See Fig. 2, oil circuit one is oil circuit control, by the movement of control piston plate 9 be used for control lock-up clutch 3 combination be separated; When automobile is in starting boost phase, the moment of torsion of motor passes on lid 1 by contiguous block 2, and lid 1 and pump impeller 8 link together, and therefore pump impeller 8 rotates.Fluid constantly enters the fluid power part of fluid torque converter by oil circuit one, the oil pressure on the right side of lock-up clutch piston plate 9 is made to be greater than oil pressure on the left of piston plate 9, liquid stream moves on the right side of piston plate 9 on the left of piston plate 9, piston plate 9 can be moved to the left, friction plate 10 will stick together in lid 1, and produce sliding rubbing.Meanwhile, the pump impeller 8 of rotation drives fluid to rotate, and guide wheel 7 maintains static, and Oil shocking turbine 6 also drives turbine 6 to rotate, turbine 6 by transmission of power to shift clutch A16 and shift clutch B26.This process is the process of hydraudynamic drive, and automobile can be made more smooth-going when starting.When turbine 6 rotating speed reaches certain value or is close with pump impeller 8, increase the oil pressure of oil circuit one, when the oil pressure difference of piston plate 9 both sides reaches some values, friction plate 10 rubs with the cunning on lid 1 and terminates, and friction plate 10 will along with lid 1 synchronous rotary, lock-up clutch 3 locking.Now lid 1 and lock-up clutch 3 are rigidly connected, and Engine torque is directly delivered to shift clutch A16 and shift clutch B26 by lock-up clutch 3.
See Fig. 3, oil circuit two is cooling oil paths, and effect cools shift clutch B26.Enter in the chamber of shift clutch B26 by the hydraulic circular part of fluid torque converter, finally flowed out by lock-up clutch 3 and the chamber that lid 1 is formed, form circulation fluid.
See Fig. 4, oil circuit three is oil circuit controls, moves the work of solenoidoperated cluthes B26 by the piston plate B31 controlling shift clutch B26; Under locking and gearshift operating mode, fluid enters between the supporting frame B30 of shift clutch B26 and piston plate B31, and oil pressure is greater than oil pressure on the left of piston plate B31 on the right side of making the piston plate B31 of shift clutch B26, piston plate B31 moves to the left and the multidisc friction plate B28 of clutch B26 is fitted, and shift clutch B26 starts working.Power is delivered to two clutch gearbox from shift clutch B26 by transmission input shaft 2 36.
See Fig. 5, oil circuit four is oil circuit controls, moves by the piston plate A21 controlling shift clutch A16 the work controlling shift clutch B16; Under starting and locking operating mode, fluid enters between the supporting frame A20 of shift clutch A16 and piston plate A21, and oil pressure is greater than oil pressure on the right side of piston plate A21 on the left of making the piston plate A21 of shift clutch A16, piston plate A21 moves to the right and the multidisc friction plate A18 of shift clutch A16 is fit together, shift clutch A16 starts working, and power is delivered to two clutch gearbox from clutch A16 by transmission input shaft 1.
See Fig. 6, oil circuit five is cooling oil paths, and effect cools shift clutch A16.Fluid enters by lock-up clutch 3 and the chamber of lid 1, and control fluid by one-way valve 32 and flow in shift clutch A16, the hydraulic circular part eventually through fluid torque converter flows out, formation circulation fluid.
See Fig. 7, oil circuit six is cooling oil paths, and its effect cools the fluid power part of whole fluid torque converter.When automobile is in starting boost phase, fluid enters between lock-up clutch 3 and lid 1 from oil circuit five, oil pressure now on the left of piston plate 9 is greater than the oil pressure on the right side of piston plate 9, liquid stream moves on the left of piston plate 9 on the right side of piston plate 9, piston plate 9 can move right, friction plate 10 and lid 1 do not paste and, now lock-up clutch 3 is inoperative, and fluid plays the effect cooled the fluid power part of whole fluid torque converter.
The foregoing is only preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., within all should being included in protection scope of the present invention.
Claims (10)
1. a fluid torque converter for integrated parallel-axis type gearshift double clutch, is characterized in that: the built-in gearshift double clutch of described fluid torque converter is the inside being arranged in fluid torque converter in the mode of parallel to an axis.
2. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 1, it is characterized in that: described fluid torque converter comprises lid, contiguous block, lock-up clutch, torsional vibration damper, gearshift double clutch and hydraulic circular part, described torsional vibration damper comprises vibration damping clamping hub, shock-absorbing spring and vibration damping drive plate, vibration damping clamping hub is connected with the piston plate of lock-up clutch, and between vibration damping clamping hub and vibration damping drive plate, parallel to an axis places a pair gearshift double clutch.
3. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 2, it is characterized in that: described a pair gearshift double clutch comprises shift clutch A and shift clutch B, and shift clutch A is connected with torsional vibration damper by connecting plate with shift clutch B.
4. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 3, it is characterized in that: described shift clutch A comprises retainer A, supporting frame A, piston plate A, baffle plate A and multidisc friction plate A, described retainer A is connected with shaft sleeve plate, and shaft sleeve plate is connected with transmission input shaft one.
5. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 3, it is characterized in that: described shift clutch B comprises retainer B, supporting frame B, piston plate B, baffle plate B and multidisc friction plate B, and the supporting frame B of described shift clutch B is connected with transmission input shaft two.
6. the fluid torque converter of the integrated parallel-axis type gearshift double clutch according to claim 4 or 5, it is characterized in that: the supporting frame of described shift clutch A and shift clutch B has some oilholes, the retainer A of described shift clutch A and the retainer B of shift clutch B links together.
7. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 2, it is characterized in that: described lock-up clutch comprises piston plate, friction plate and one-way valve, friction plate is attached on piston plate, and piston plate and one-way valve are fixed, and piston plate is provided with aperture.
8. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 2, it is characterized in that: described hydraulic circular part comprises turbine, guide wheel and pump impeller, described turbine is connected with the vibration damping drive plate of torsional vibration damper, described pump impeller welds with lid the shell forming whole fluid torque converter, is provided with described guide wheel between described turbine and described pump impeller.
9. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 2, is characterized in that: described contiguous block is welded on and covers.
10. the fluid torque converter of integrated parallel-axis type gearshift double clutch according to claim 1, is characterized in that: the built-in gearshift double clutch of described fluid torque converter connects the input shaft of two gearboxes, is directly installed on double-clutch speed changer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510687109.1A CN105179635A (en) | 2015-10-22 | 2015-10-22 | Hydraulic torque converter integrated with parallel axial gear-shifting dual clutches |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510687109.1A CN105179635A (en) | 2015-10-22 | 2015-10-22 | Hydraulic torque converter integrated with parallel axial gear-shifting dual clutches |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105179635A true CN105179635A (en) | 2015-12-23 |
Family
ID=54901942
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510687109.1A Pending CN105179635A (en) | 2015-10-22 | 2015-10-22 | Hydraulic torque converter integrated with parallel axial gear-shifting dual clutches |
Country Status (1)
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| CN (1) | CN105179635A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110039987A (en) * | 2018-01-16 | 2019-07-23 | 舍弗勒技术股份两合公司 | Connection component and hybrid power system |
| CN113811704A (en) * | 2019-05-10 | 2021-12-17 | 株式会社法雷奥凯佩科 | Hydrokinetic torque coupling device having a lockup clutch with a dual piston assembly and a selectable one-way clutch |
| KR20230103871A (en) * | 2021-12-30 | 2023-07-07 | 주식회사 카펙발레오 | Torque converter for vehilce |
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| CN205064750U (en) * | 2015-10-22 | 2016-03-02 | 上海萨克斯动力总成部件***有限公司 | Integrated parallel shaft type double clutch's that shifts gears torque converter |
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|---|---|---|---|---|
| CN110039987A (en) * | 2018-01-16 | 2019-07-23 | 舍弗勒技术股份两合公司 | Connection component and hybrid power system |
| CN113811704A (en) * | 2019-05-10 | 2021-12-17 | 株式会社法雷奥凯佩科 | Hydrokinetic torque coupling device having a lockup clutch with a dual piston assembly and a selectable one-way clutch |
| KR20230103871A (en) * | 2021-12-30 | 2023-07-07 | 주식회사 카펙발레오 | Torque converter for vehilce |
| KR102594506B1 (en) | 2021-12-30 | 2023-10-27 | 주식회사 카펙발레오 | Torque converter for vehilce |
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