CN204164297U - A kind of four turbine fluid torque converters - Google Patents
A kind of four turbine fluid torque converters Download PDFInfo
- Publication number
- CN204164297U CN204164297U CN201420615470.4U CN201420615470U CN204164297U CN 204164297 U CN204164297 U CN 204164297U CN 201420615470 U CN201420615470 U CN 201420615470U CN 204164297 U CN204164297 U CN 204164297U
- Authority
- CN
- China
- Prior art keywords
- turbine
- torque converter
- shaft
- gear
- output shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The utility model discloses a kind of fluid torque converter that four turbines are housed, be primarily characterized in that: this fluid torque converter is provided with four turbines, first turbine is connected with Output Shaft of Hydraulic Torque Converter by the first reduction gear, the first overrunning clutch, the comparatively slow-speed of revolution than time transmitting torque; Second turbine is connected with Output Shaft of Hydraulic Torque Converter by the second reduction gear, the second overrunning clutch, higher rotation speed than time transmitting torque; 3rd turbine is connected with Output Shaft of Hydraulic Torque Converter by the 3rd accelerating gear, the 3rd overrunning clutch, higher rotation speed than time transmitting torque; 4th turbine is connected with Output Shaft of Hydraulic Torque Converter by the 4th accelerating gear, spline, the transmitting torque when high rotating ratio.The utility model patent can provide large torque conversion range and wider higher efficiency range, makes fluid torque converter large in load variations, and changes frequently under operating mode, can not shift gears or few gearshift, can be used for the field such as automobile making and scientific research.
Description
Technical field
The utility model relates to a kind of fluid torque converter that four turbines are housed, and is applicable to that load variations is large and load variations is mechanical frequently, belongs to mechanical transmission fields.
Background technique
Fluid torque converter is the connected element of automatic catch automobile motor and automatic transmission case, and rotating speed and moment of torsion are transmitted in its main effect, also make between motor and automatic transmission case be connected to become nonrigid, to facilitate automatic transmission case self shifter.But existing twin-turbine torque converter only has greater efficiency in medium and higher rotation speed than in scope, the change of some mechanical load greatly, and changes frequent, when load diminishes, fluid torque converter has very high rotating ratio, but the efficiency now obtained is lower, and gearshift is frequent.In sum, twin-turbine torque converter is under mechanical load change greatly and frequently operating mode, and realize high efficiency speed range not enough, this problem needs further improvement.
Model utility content
The purpose of this utility model is to solve the problem, and provides a kind of fluid torque converter with larger torque conversion range and wider high efficiency scope.Be achieved through the following technical solutions:
Four turbine fluid torque converters described in the utility model, are made up of fluid torque converter input shaft, Output Shaft of Hydraulic Torque Converter, pump impeller, the first turbine, the second turbine, the 3rd turbine, the 4th turbine, guide wheel, the first turbine shaft, the second turbine shaft, the 3rd turbine shaft, the 4th turbine shaft, the first gear, the second gear, the 3rd gear, the 4th gear, the 5th gear, the 6th gear, the 7th gear, octadentate wheel, the first overrunning clutch, the second overrunning clutch, the 3rd overrunning clutch, the 4th overrunning clutch, spline.First turbine, the second turbine, the 3rd turbine, the 4th turbine are arranged in order near pump impeller to away from pump impeller, the size of turbine blade increases successively, turbine blade angle increases successively, because pump impeller rotational speed changes, the flow velocity of the working solution that pump impeller stream comes is different with deflection direction, impact on different turbine blades, because the size of turbine blade increases successively, the torque phase of turbine transmission should increase.First turbine is arranged on the first turbine shaft, and the first turbine shaft is provided with the first gear, and the first gear and the 5th gears meshing form the first reduction gear, and the 5th gear is connected with Output Shaft of Hydraulic Torque Converter by the first overrunning clutch.Second turbine is arranged on the second turbine shaft, second turbine shaft is enclosed within outside the first turbine shaft, second turbine shaft is provided with the second gear, and the second gear and the 6th gears meshing form the second reduction gear, and the 6th gear is connected with Output Shaft of Hydraulic Torque Converter by the second overrunning clutch.3rd turbine is arranged on the 3rd turbine shaft, 3rd turbine shaft is enclosed within outside the first turbine shaft, the second turbine shaft, 3rd turbine shaft is provided with the 3rd gear, 3rd gear and the 7th gears meshing form the 3rd accelerating gear, and the 7th gear is connected with Output Shaft of Hydraulic Torque Converter by the 3rd overrunning clutch.4th turbine is arranged on the 4th turbine shaft, 4th turbine shaft is enclosed within outside the first turbine shaft, the second turbine shaft, the 3rd turbine shaft, 4th turbine shaft is provided with the 4th gear, 4th gear and the 8th gears meshing form the 4th accelerating gear, and octadentate wheel is connected with Output Shaft of Hydraulic Torque Converter by spline.Guide wheel is arranged on guide wheel fixed sleeving by the 4th overrunning clutch.
The utility model compares the advantage of prior art:
1, the 3rd turbine, the 4th adopts accelerating gear to be connected between turbine with Output Shaft of Hydraulic Torque Converter, makes fluid torque converter under low operating mode, obtains high rotating ratio, expand the torque range of fluid torque converter, decrease gearshift number of times simultaneously.
2, the first turbine, the second turbine, the 3rd are connected with overrunning clutch between turbine with Output Shaft of Hydraulic Torque Converter.Along with the continuous increase of rotating ratio, when the moment of the first turbine transmission gradually become zero then change direction time, the first overrunning clutch unclamps, and the first turbine is no longer to Output Shaft of Hydraulic Torque Converter Driving Torque.When rotating ratio increases to certain value, the moment of the second turbine transmission gradually becomes zero and then changes direction, and the second overrunning clutch unclamps, and the second turbine is no longer to Output Shaft of Hydraulic Torque Converter Driving Torque.When rotating ratio continues to increase, the 3rd overrunning clutch unclamps, and the 3rd turbine is no longer to Output Shaft of Hydraulic Torque Converter Driving Torque, and only remaining 4th turbine is to Output Shaft of Hydraulic Torque Converter Driving Torque.Effectively expand the torque range of fluid torque converter, improve the efficiency of fluid torque converter under high rotating ratio.
3, guide wheel is arranged on guide wheel fixed sleeving by the 4th overrunning clutch, when secondary speed is lower, turbine outlet place liquid flow impact is on the concave surface of guide vane, 4th overrunning clutch locking, fluid torque converter plays increase torsional interaction, when secondary speed is elevated to a certain degree, the impact force of fluid torque converter to guide wheel is reverse, 4th overrunning clutch unclamps, and fluid torque converter proceeds to the working condition of Coupler, improves the efficiency of fluid torque converter.
Accompanying drawing explanation
Fig. 1 is the layout schematic diagram of four turbine fluid torque converters described in the utility model.
Embodiment
Below in conjunction with accompanying drawing, the utility model will be further described.
1-fluid torque converter input shaft; 2-Output Shaft of Hydraulic Torque Converter; 3-pump impeller; 4-the first turbine; 5-the second turbine; 6-the three turbine; 7-the four turbine; 8-guide wheel; 9-the four overrunning clutch; 10-guide wheel fixed sleeving; 11-the four gear; 12-the three gear; 13-the second gear; 14-the first gear; 15-the first turbine shaft; 16-the second turbine shaft; 17-the three turbine shaft; 18-the four turbine shaft; 19-spline; 20-the three overrunning clutch; 21-the second overrunning clutch; 22-the first overrunning clutch; 23-the octadentate wheel; 24-the seven gear; 25-the six gear; 26-the five gear.
Be described further below in conjunction with example figure.
As shown in Figure 1, four turbine fluid torque converters described in the utility model, comprise fluid torque converter input shaft 1, Output Shaft of Hydraulic Torque Converter 2, pump impeller 3, first turbine 4, second turbine 5, 3rd turbine 6, 4th turbine 7, guide wheel 8, guide wheel fixed sleeving 10, first turbine shaft 15, second turbine shaft 16, 3rd turbine shaft 17, 4th turbine shaft 18, first gear 14, second gear 13, 3rd gear 12, 4th gear 11, 5th gear 26, 6th gear 25, 7th gear 24, octadentate wheel 23, first overrunning clutch 22, second overrunning clutch 21, 3rd overrunning clutch 20, 4th overrunning clutch 9, spline 19.The rotation rotarily driving pump impeller 3 blade of fluid torque converter input shaft 1, working solution is under the drive of pump impeller 3 blade, turbine blade is rushed at certain speed and liquid flow path direction, liquid stream is after impulse turbine, due to active force reaction force relation, liquid stream flows out turbine and rushes at guide wheel 8, and then flows into pump impeller 3 along certain direction, completes a circulation.When secondary speed is elevated to a certain degree, liquid stream is reverse to the impact force of guide wheel 8, guide wheel 8 freely with turbine rotating in same direction, torque-converters enters the working condition of Coupler.
When load is very large, the rotation rotarily driving pump impeller 3 blade of fluid torque converter input shaft 1, working solution is under the drive of pump impeller 3 blade, the forward face of the first turbine 4 is rushed at certain speed, the first turbine 4 is driven to rotate, first turbine 4 is arranged on the first turbine shaft 15, power passes on the first gear 14 by the first turbine shaft 15, due to the engagement of the first gear 14 and the 5th gear 26, power is delivered to the 5th gear 26 from the first gear 14, 5th gear 26 is connected on Output Shaft of Hydraulic Torque Converter 2 by the first overrunning clutch 22, power is delivered on Output Shaft of Hydraulic Torque Converter 2 by the 5th gear 26 and the first overrunning clutch 22.The moment M1 of Output Shaft of Hydraulic Torque Converter 2 is reached from pump impeller 3, engage the first reduction gear of formation by the first gear 14 and the 5th gear 26 and increase, thus output torque M2 is very large, converter torque ratio M2/M1 is very large, now, the moment that second turbine 5, the 3rd turbine 6, the 4th turbine 7 transmit is very little, and rotating ratio i is very low, obtains higher converter torque ratio and high efficiency.Along with load reduces, working solution is under the drive of pump impeller 3 blade, flow velocity accelerates and direction gradually deviation occurs, the moment that first turbine 4 transmits reduces rapidly, the moment that second turbine 5 transmits increases gradually, the moment that 3rd turbine 6, the 4th turbine 7 transmit remains unchanged, and total output torque reduces gradually, and rotating ratio i increases gradually.During to a certain rotating ratio i41, the first turbine 4 carry-over moment near zero.Rotating ratio i increases again, working solution impacts the back side of the first turbine 4 blade, make the sense of rotation of the first turbine 4 reverse, first turbine 4 transmitting torque changes direction, and the first overrunning clutch 22 is unclamped, first turbine 4 and Output Shaft of Hydraulic Torque Converter 2 are thrown off and dally, and be now the second turbine 5, the moment of the 3rd turbine 6, the 4th turbine 7 reaches Output Shaft of Hydraulic Torque Converter 2, become the working state of the fluid torque converter of three turbines.
Now, the rotation rotarily driving pump impeller 3 blade of fluid torque converter input shaft 1, working solution is under the drive of pump impeller 3 blade, the concave surface of the second turbine 5 blade is rushed at certain speed, the second turbine 5 is driven to rotate, second turbine 5 is arranged on the second turbine shaft 16, power passes on the second gear 13 by the second turbine shaft 16, due to the engagement of the second gear 13 and the 6th gear 25, power is delivered to the 6th gear 25 from the second gear 13, 6th gear 25 is connected on Output Shaft of Hydraulic Torque Converter 2 by the second overrunning clutch 21, power is delivered on Output Shaft of Hydraulic Torque Converter 2 by the 6th gear 25 and the second overrunning clutch 21.The moment M1 of Output Shaft of Hydraulic Torque Converter 2 is reached from pump impeller 3, engage the reduction gear of formation by the second gear 13 and the 6th gear 25 and increase, thus output torque M2 is larger, converter torque ratio M2/M1 is larger, now, the moment that 3rd turbine 6, the 4th turbine 7 transmit is very little, and rotating ratio i is lower, obtains higher converter torque ratio and higher efficiency.Along with load continues to reduce, working solution is under the drive of pump impeller 3 blade, flow velocity accelerates and direction gradually deviation occurs, the moment that second turbine 5 transmits reduces rapidly, the moment that 3rd turbine 6 transmits increases gradually, the moment that 4th turbine 7 transmits remains unchanged, and total output torque reduces gradually, and rotating ratio increases gradually.During to a certain rotating ratio i42, the second turbine 5 carry-over moment near zero.Rotating ratio i increases again, working solution impacts the back side of the second turbine 5 blade, make the sense of rotation of the second turbine 5 reverse, second turbine 5 transmitting torque changes direction, and the second overrunning clutch 21 is unclamped, second turbine 5 and Output Shaft of Hydraulic Torque Converter 2 are thrown off and dally, and be now the 3rd turbine 6, the moment of the 4th turbine 7 reaches Output Shaft of Hydraulic Torque Converter 2, become the working state of the fluid torque converter of two turbines.
Now, the rotation rotarily driving pump impeller 3 blade of fluid torque converter input shaft 1, working solution is under the drive of pump impeller 3 blade, the forward face of the 3rd turbine 6 is rushed at certain speed, the 3rd turbine 6 is driven to rotate, 3rd turbine 6 is arranged on the 3rd turbine shaft 17, power passes on the 3rd gear 12 by the 3rd turbine shaft 17, due to the engagement of the 3rd gear 12 and the 7th gear 24, power is delivered to the 7th gear 24 from the 3rd gear 12, 7th gear 24 is connected on Output Shaft of Hydraulic Torque Converter 2 by the 3rd overrunning clutch 20, power is delivered on Output Shaft of Hydraulic Torque Converter 2 by the 7th gear 24 and the 3rd overrunning clutch 20.The moment M1 of Output Shaft of Hydraulic Torque Converter 2 is reached from pump impeller 3, engage the accelerating gear of formation by the 3rd gear 12 and the 7th gear 24 and reduce, thus output torque M2 is less, converter torque ratio M2/M1 is less, now, the moment that 4th turbine 7 transmits is very little, and rotating ratio is higher, obtains the converter torque ratio lower than three turbine fluid torque converters and high efficiency.Along with load reduces, working solution is under the drive of pump impeller 3 blade, flow velocity accelerates and direction gradually deviation occurs, the moment that 3rd turbine 6 transmits reduces rapidly, the moment that 3rd turbine 6 transmits increases gradually, the moment that 4th turbine 7 transmits remains unchanged, and total output torque continues to reduce, and rotating ratio continues to increase.During to a certain rotating ratio i43, the 3rd turbine 6 carry-over moment near zero.Rotating ratio i increases again, working solution impacts the back side of the 3rd turbine 6 blade, make the sense of rotation of the 3rd turbine 6 reverse, 3rd turbine 6 transmitting torque changes direction, and the 3rd overrunning clutch 20 is unclamped, 3rd turbine 6 is thrown off with Output Shaft of Hydraulic Torque Converter 2 and dallies, and is now that the moment of the 4th turbine 7 reaches Output Shaft of Hydraulic Torque Converter 2, becomes the working state of the fluid torque converter of single turbine.
Now, the rotation rotarily driving pump impeller 3 blade of fluid torque converter input shaft 1, working solution is under the drive of pump impeller 3 blade, the concave surface of the 4th turbine 7 blade is rushed at certain speed, the 4th turbine 7 is driven to rotate, 4th turbine 7 is arranged on the 4th turbine shaft 18, power passes on the 4th gear 11 by the 4th turbine shaft 18, because the 4th gear 11 and octadentate take turns the engagement of 23, power is delivered to octadentate wheel 23 from the 4th gear 11, octadentate wheel 23 is connected on Output Shaft of Hydraulic Torque Converter 2 by spline 19, power is delivered on Output Shaft of Hydraulic Torque Converter 2 by octadentate wheel 23 and spline 19.Reach the moment M1 of Output Shaft of Hydraulic Torque Converter 2 from pump impeller 3, engaged the accelerating gear of formation by the 4th gear 11 and octadentate wheel 23 and reduced, thus output torque M2 is very little, and converter torque ratio M2/M1 is very little, and rotating ratio is very high.When the 4th turbine 7 rotating speed is elevated to a certain degree, liquid stream is reverse to guide wheel 8 impact force, and the 4th overrunning clutch 9 unclamps, and guide wheel 8 dallies, and torque-converters proceeds to Coupler working condition, obtains the converter torque ratio lower than two turbine fluid torque converters and higher efficiency.
The utility model mainly provides the fluid torque converter that four turbines are housed; under load variations greatly and frequently operating mode, improve the torque conversion range of fluid torque converter and wider higher efficiency range is provided; reduce gearshift number of times; when not deviating from the utility model essence; the structural configuration of four turbine fluid torque converters can be done corresponding change, but these corresponding changes all should belong within the claims belonging to the utility model.
Claims (5)
1. a turbine fluid torque converter, comprise pump impeller, first turbine, second turbine, 3rd turbine, 4th turbine, guide wheel, first turbine shaft, second turbine shaft, 3rd turbine shaft, 4th turbine shaft, first reduction gear, second reduction gear, 3rd accelerating gear, 4th accelerating gear, first overrunning clutch, second overrunning clutch, 3rd overrunning clutch, 4th overrunning clutch, spline, guide wheel fixed sleeving, fluid torque converter input shaft, Output Shaft of Hydraulic Torque Converter, it is characterized in that: in described fluid torque converter, adopt four turbines, first turbine, second turbine, 3rd turbine, 4th turbine is arranged in order near pump impeller to away from pump impeller, the size of turbine blade increases successively, turbine blade angle increases successively, because pump impeller rotational speed changes, the flow velocity of the working solution that pump impeller stream comes is different with deflection direction, impact on different turbine blades, because the size of turbine blade increases successively, the torque phase of turbine transmission should increase.
2. a kind of four turbine fluid torque converters according to claim 1, it is characterized in that: described second turbine shaft is enclosed within outside the first turbine shaft, described 3rd turbine shaft is enclosed within outside the first turbine shaft, the second turbine shaft, and described 4th turbine shaft is enclosed within outside the first turbine shaft, the second turbine shaft, the 3rd turbine shaft.
3. a kind of four turbine fluid torque converters according to claim 1, it is characterized in that: described first turbine is connected with the first reduction gear with between Output Shaft of Hydraulic Torque Converter, described second turbine is connected with the second reduction gear with between Output Shaft of Hydraulic Torque Converter, described 3rd is connected with the 3rd accelerating gear between turbine with Output Shaft of Hydraulic Torque Converter, and the described 4th is connected with the 4th accelerating gear between turbine with Output Shaft of Hydraulic Torque Converter.
4. a kind of four turbine fluid torque converters according to claim 1, it is characterized in that: described first reduction gear is connected with Output Shaft of Hydraulic Torque Converter the first overrunning clutch, described second reduction gear is connected with Output Shaft of Hydraulic Torque Converter the second overrunning clutch, described 3rd accelerating gear is connected with Output Shaft of Hydraulic Torque Converter the 3rd overrunning clutch, uses spline joint between described 4th turbine and Output Shaft of Hydraulic Torque Converter 2.
5. a kind of four turbine fluid torque converters according to claim 1, is characterized in that: described guide wheel is arranged on guide wheel fixed sleeving with the 4th overrunning clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420615470.4U CN204164297U (en) | 2014-10-23 | 2014-10-23 | A kind of four turbine fluid torque converters |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420615470.4U CN204164297U (en) | 2014-10-23 | 2014-10-23 | A kind of four turbine fluid torque converters |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204164297U true CN204164297U (en) | 2015-02-18 |
Family
ID=52537987
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420615470.4U Expired - Fee Related CN204164297U (en) | 2014-10-23 | 2014-10-23 | A kind of four turbine fluid torque converters |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204164297U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106224484A (en) * | 2015-08-03 | 2016-12-14 | 熵零股份有限公司 | Energy adjustment system |
| CN108343721A (en) * | 2017-01-24 | 2018-07-31 | 黎文超 | Hydraulic transmission box |
| CN113330232A (en) * | 2019-01-17 | 2021-08-31 | 米哈伊尔·马戈梅多维奇·奥马洛夫 | Fluid power automatic transmission device |
| RU2788351C1 (en) * | 2022-06-14 | 2023-01-17 | Федеральное государственное казенное военное образовательное учреждение высшего образования "Военный учебно-научный центр Военно-воздушных сил "Военно-воздушная академия имени профессора Н.Е. Жуковского и Ю.А. Гагарина" (г. Воронеж) Министерства обороны Российской Федерации | Hydromechanical transmission torque converter for separate drive of driving axles of wheel drive |
-
2014
- 2014-10-23 CN CN201420615470.4U patent/CN204164297U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106224484A (en) * | 2015-08-03 | 2016-12-14 | 熵零股份有限公司 | Energy adjustment system |
| CN108343721A (en) * | 2017-01-24 | 2018-07-31 | 黎文超 | Hydraulic transmission box |
| CN108343721B (en) * | 2017-01-24 | 2021-05-04 | 黎文超 | Hydraulic transmission case |
| CN113330232A (en) * | 2019-01-17 | 2021-08-31 | 米哈伊尔·马戈梅多维奇·奥马洛夫 | Fluid power automatic transmission device |
| KR20210118114A (en) * | 2019-01-17 | 2021-09-29 | 미하일 마고메도비치 오마로프 | hydrodynamic automatic transmission |
| EP3926211A4 (en) * | 2019-01-17 | 2023-04-19 | Omarov, Mikhail Magomedovich | Hydrodynamic automatic transmission |
| CN113330232B (en) * | 2019-01-17 | 2023-11-10 | 米哈伊尔·马戈梅多维奇·奥马洛夫 | Fluid power automatic transmission device |
| KR102643146B1 (en) | 2019-01-17 | 2024-03-04 | 미하일 마고메도비치 오마로프 | Hydrodynamic automatic transmission |
| RU2788351C1 (en) * | 2022-06-14 | 2023-01-17 | Федеральное государственное казенное военное образовательное учреждение высшего образования "Военный учебно-научный центр Военно-воздушных сил "Военно-воздушная академия имени профессора Н.Е. Жуковского и Ю.А. Гагарина" (г. Воронеж) Министерства обороны Российской Федерации | Hydromechanical transmission torque converter for separate drive of driving axles of wheel drive |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN205298454U (en) | Hydraulic pressure machinery infinitely variable transmission for loader | |
| CN204164297U (en) | A kind of four turbine fluid torque converters | |
| CN101408244B (en) | Mechanical hydraulic stepless speed changer and method and vehicle mechanical hydraulic stepless speed changer | |
| CN106090181A (en) | A kind of compound two-space fluid coupling and starter | |
| CN201875086U (en) | Hydraulic torque converter with speed reducer | |
| CN204323063U (en) | A kind of seven gear speed changing structures | |
| CN201241945Y (en) | Speed variator for small-sized engineering machinery | |
| CN204239660U (en) | A kind of fluid torque converter that three turbines are housed | |
| WO2017005181A1 (en) | Compound harmonic gear transmission hydraulic coupler, and starter | |
| CN203146745U (en) | Hydraulic torque converter | |
| CN202612499U (en) | Positive and negative bidirectional input variable speed mechanism | |
| CN103322157B (en) | Hydraulic mechanical torque converter | |
| WO2016112810A1 (en) | Composite impeller-type hydraulic torque converter and continuously variable transmission | |
| CN202579891U (en) | Wheel excavator transmission mechanism | |
| CN202017749U (en) | Worm gear driving device with hydraulic power worm group | |
| CN107166007B (en) | The automatic transmission structure of automobile-used nine gear | |
| CN202017748U (en) | Hydraulic power and mechanical power combined transmission system | |
| CN104595437A (en) | Composite continuously-variable transmission | |
| CN206092889U (en) | Box speed reducer | |
| CN220930102U (en) | Torque converter pump impeller and turbine torque converter | |
| CN104500682B (en) | A kind of compound postpositional gear box type fluid coupling and starter | |
| JP2007333212A5 (en) | ||
| CN106122426A (en) | A kind of starter of composite impeller type fluid torque-converter | |
| RU2695477C1 (en) | Hydromechanical transmission | |
| WO2016112803A1 (en) | Composite guide-vane-adjustable hydraulic torque converter and continuously variable transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150218 Termination date: 20151023 |
|
| EXPY | Termination of patent right or utility model |