CN106369129A - Hydraulic torque converter and vehicle with same - Google Patents
Hydraulic torque converter and vehicle with same Download PDFInfo
- Publication number
- CN106369129A CN106369129A CN201510424382.5A CN201510424382A CN106369129A CN 106369129 A CN106369129 A CN 106369129A CN 201510424382 A CN201510424382 A CN 201510424382A CN 106369129 A CN106369129 A CN 106369129A
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- assembly
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- pump
- turbine
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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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/04—Combined pump-turbine units
-
- 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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The invention provides a hydraulic torque converter. The hydraulic torque converter comprises a pump cover assembly, a pump wheel assembly, a turbine assembly, a guide wheel assembly, a circulation chamber, a locking clutch and a torsional vibration damper assembly, wherein the pump wheel assembly is connected to the pump cover assembly and used to receive power transmitted by the pump cover assembly; the turbine assembly is disposed between the pump cover assembly and the pump wheel assembly; the guide wheel assembly is positioned between the pump wheel assembly and the turbine assembly by a bearing; the circulation chamber is composed through enclosing of the pump wheel assembly, the turbine assembly and the guide wheel assembly; the locking clutch is connected between the turbine assembly and the pump wheel assembly; and the torsional vibration damper assembly is disposed between the turbine assembly and the pump cover assembly. The hydraulic torque converter has the advantages that damping performance is ensured; the axial size of the hydraulic torque converter is greatly reduced; and structural layout in the vehicle is optimized.
Description
Technical field
A kind of the present invention relates to vehicular field, more specifically, the fluid torque-converter of the variator of vehicle.
Background technology
Existing known vehicle fluid torque-converter, it is arranged between electromotor and automatic transmission, the pump impeller of the pump cover being directly connected to including electromotor and pump cover welding and pump impeller is horizontally-opposed and and the automatic transmission turbine being directly connected to, the guide wheel being arranged between pump impeller and turbine.Torque is input to automatic transmission from electromotor by the fluid circulating in the race way being formed each other by pump impeller blade, guide vane and turbo blade.It is provided with one-way clutch that can only be freely rotatable in one direction in guide wheel, play increase torque.Fluid torque-converter is because fluid power transmission efficiency is lower, in order to improve fuel economy, described vehicle fluid torque-converter also can arrange lock-up clutch between input and output, lock-up clutch one end is contacted with pump cover, one end is passed through platen and is connected with output turbine, when operating mode is suitable, it is directly connected to input in conjunction with lock-up clutch and exports.In this case, engine luggine is transferred directly to automatic transmission, for the vibration of electromotor when lock-up clutch of decaying combines, can arrange torsion vibration absorber between platen and turbine.
Lockup clutch of converter and torsion vibration absorber increased fluid torque-converter total length in the axial direction.In recent years, the horizontal space of power assembly is required increasingly to increase, be accompanied by this, the requirement of fluid torque-converter axially compact is also increasingly increased.And power assembly fuel economy is required also increasingly strict, specifically require fluid torque-converter to improve damping performance to increase lock-up clutch locking region.
For the fluid torque-converter tending to axially compact, the fluid torque-converter disclosed in existing Japanese invention patent 2006-118654, it is arranged in below torus by optimization front guide impeller design with by lock-up clutch, reaches the purpose reducing fluid torque-converter axial dimension.But limited by physical dimension, lock-up clutch size diminishes, affected lock-up clutch damping performance.
Content of the invention
The purpose of the present invention is the problems referred to above existing for prior art, proposes a kind of fluid torque-converter effectively reducing fluid torque-converter axial dimension and improving cushioning ability.
For solving the above problems, according to an aspect of the present invention, provide a kind of fluid torque-converter, comprising: pump cover assembly；Pump wheel assembly, it is connected with described pump cover assembly, and for receiving the power of described pump cover assembly transmission；Turbine assembly, it is arranged between described pump cover assembly and described pump wheel assembly；Guide wheel assembly, it is positioned between described pump wheel assembly and described turbine assembly by bearing；Torus, it is surrounded by described pump wheel assembly, described turbine assembly and described guide wheel assembly；Lock-up clutch, it is connected between described turbine assembly and described pump wheel assembly；And torsional balancer assembly, it is arranged between described turbine assembly and described pump cover assembly.
Alternatively, described lock-up clutch is arranged between the turbine shroud of described turbine assembly and the pump impeller housing of described pump wheel assembly along the outside of described torus radial direction.
Alternatively, described lock-up clutch also includes friction plate, and described friction plate connects to described turbine shroud, and described lock-up clutch passes through to connect turbine shroud described in described friction plate.
Alternatively, described friction plate tilts with regard to described pump impeller housing connection surface.
Alternatively, described torsion vibration absorber assembly includes clamping disk, damping spring, passive disk hole output flange: described clamping disk connects the turbine shroud to described turbine assembly and the power for receiving its transmission；Described damping spring connects described clamping disk and described driven disc respectively, and for power is transferred to described driven disc；Described output flange one end is connected with described driven disc, and the other end is used for connecting to transmission input shaft.
Alternatively, described torsion vibration absorber assembly is arranged between described turbine shroud and the pump cover of described pump cover assembly along described turbine shroud radial outside.
Alternatively, described torsion vibration absorber assembly has vertically less than the outermost thickness of described turbine shroud.
Alternatively, described damping spring includes the first mutually nested damping spring and the second damping spring.
Alternatively, described pump wheel assembly and described guide wheel assembly are axially positioned by thrust bearing；
And/or described turbine assembly and described guide wheel assembly are axially positioned by thrust bearing.
According to another aspect of the present invention, also provide a kind of vehicle, comprising: oil pump, variator and foregoing fluid torque-converter.
Alternatively, the circulation intracavity between described turbine assembly and described pump wheel assembly forms lock-up clutch release oil pocket, forms lock-up clutch and be combined oil pocket in the cavity between described turbine assembly and described pump wheel assembly；And the gap between the input shaft of the support shaft in described oil pump and described variator is lock-up clutch release action oil circuit, the centre bore of the input shaft of described variator is lock-up clutch combination oil circuit.
Alternatively, when the work fluid in described lock-up clutch release action oil circuit is recycled to described lock-up clutch release oil pocket, described lock-up clutch is in off-position；Motor torque passes sequentially through described pump cover assembly, described pump wheel assembly, described torus, described torsion vibration absorber are transferred to the input shaft of described variator；When work fluid in described lock-up clutch combination oil circuit is recycled to described lock-up clutch with reference to oil pocket, described lock-up clutch is in binding site；Motor torque passes sequentially through described pump cover assembly, described pump wheel assembly, described lock-up clutch, described turbine assembly, described torsion vibration absorber are transferred to the input shaft of described variator.
Compared with prior art, above-mentioned fluid torque-converter has the advantage that
1st, no matter torsional balancer is arranged on fluid torque-converter radial outside or inner side to prior art fluid torque-converter, torsion vibration absorber on the direction be axially directed to engine side all than turbine shroud closer to engine side.The torsion vibration absorber assembly of fluid torque-converter described herein is contained in axial space between lock-up clutch and the pump cover directly over turbine radial direction, it is less than turbine shroud on the direction pointing to engine side in the axial direction, largely reduce the axial dimension of fluid torque-converter.
2nd, the lock-up clutch axle of described fluid torque-converter is arranged on directly over torus, it is directly connected to pump impeller housing and turbine shroud, turbine shroud is directly as the piston of lock-up clutch, the extra piston element of fluid torque-converter and the axial gap with other adjacent components required for piston element, greatly reduce fluid torque-converter axial dimension compared to existing technology.
3rd, described fluid torque-converter torsion vibration absorber input connects turbine assembly, and torsion vibration absorber outfan connects driven disc and output flange；When lock-up clutch combines, turbine assembly is mechanically connected with pump wheel assembly, forms turbine amortisseur, and damping performance is more preferable than prior art individual pen amortisseur performance.
Brief description
Fig. 1 is the top half along axis of the fluid torque-converter sectional view involved by the first embodiment of the present invention；And
Fig. 2 is the top half along axis of the fluid torque-converter sectional view involved by second embodiment of the present invention.
Specific embodiment
Fig. 1 illustrates the top half along axis of the fluid torque-converter sectional view involved by the first embodiment of the present invention.The fluid torque-converter 1 of present embodiment can be applicable to be equipped with the vehicle of automatic transmission, and it is arranged between electromotor and automatic transmission gear shift mechanism (not shown).In the following description, for convenience, will be close to engine side (right side in Fig. 1) and be referred to as " front " or " front ", will be far from engine side (left side in Fig. 1) and be referred to as " afterwards " or " rear ".
Fluid torque-converter 1 primary structure includes pump cover assembly 10, pump wheel assembly 20, turbine assembly 30, turbine assembly 40, lock-up clutch 50 and torsion vibration absorber assembly 60.In a state of use, it is full of work fluid by the pump impeller housing 21 in the pump cover 11 and pump wheel assembly 20 in pump cover assembly 10 in the cavity of the fluid torque-converter 1 being surrounded all the time.
Pump cover assembly 10 is arranged on the rear of fluid torque-converter 1, including pump cover 11, lead 12 and bolt block 13.Pump cover 11 is one of two principal characters of composition fluid torque-converter 1 main cavity.Lead 12 is welded on the center of pump cover 11, to realize the cooperation with the central hole of the crankshaft of the unshowned electromotor of Fig. 1, is that fluid torque-converter 1 is installed to and play the guiding role on electromotor.It has been equally spaced multiple bolt blocks 13 in pump cover 11 in a circumferential direction along fluid torque-converter 1 position, and fluid torque-converter 1 can have been connected to the unshowned engine flywheel of Fig. 1 by multiple bolts accordingly.
Pump wheel assembly 20 is arranged on the front of fluid torque-converter 1, including pump impeller housing 21, pump impeller 22, pump impeller blade 25, pump impeller hub 23 and pump impeller bushing 24.Pump impeller housing 21 is axially opposite with pump cover 11 and is welded to connect, its bending section 21b including in the radial outside anchor ring 21a vertical with fluid torque-converter 1 axis and rearward swelling.Multiple turbo blades 25 have been equally spaced it inside bending section 21b and on the circumferencial direction of turbine 22.In bending section 21b, radially inner end is welded with an axially arranged T-shaped pump impeller hub 23, in pump impeller hub 23 inner radius force fit one pump impeller bushing 24.When the engine runs, pump cover assembly 10 and pump wheel assembly 20 therewith together with rotate, it is filled in the work fluid in fluid torque-converter 1 along the flow passage that formed of bending section 21b and pump impeller blade 25 of pump impeller housing 21, produce axle center rotation one side circumferentially side and liquor stream p that forwards flows around pump impeller housing 21.
Turbine assembly 30 includes turbine shroud 31, turbine 32 and turbo blade 33.Turbine shroud 31 is oppositely arranged in the axial direction with pump impeller housing 21, and it includes becoming an anchor ring 31a, the bending section 31b forwards swelling and the anchor ring 31c vertical with fluid torque-converter 1 axis of minute angle with fluid torque-converter 1 axis in radial outside.It has been equally spaced multiple turbo blades 33 inside bending section 31b and on the circumferencial direction of turbine 32, lock-up clutch friction plate 51 has been bonded with arc surface 31a.Liquor stream p of pump impeller is directed in turbine shroud 31, the flow passage being formed via bending section 31b and the turbo blade 33 of turbine shroud 31, and generation rotates an edge inner circumferential side and liquor stream w rearward flowing around the axle center of turbine shroud 31.Liquor stream w acts on turbo blade 33, promotes turbine to rotate along the direction that pump impeller rotates.
Guide wheel assembly 40 is arranged between pump impeller housing 21 and turbine shroud 31, and it includes guide wheel 41, guide vane 42, guide wheel rear cover plate 43, cover plate 44 and guide wheel stator 46 in front of guide wheel.Wherein guide wheel 41, guide vane 42 and guide wheel rear cover plate 43 setting are integrated, and in front of guide wheel, cover plate 44 interference press-fits in guide wheel 41.Guide wheel stator 46 is passed through spline and is connected with the oil pump support shaft 80 being fixed on that case of transmission automatic.Liquor stream w of turbine is directed in guide wheel, and the runner through guide vane 42 forms liquor stream d, flow back in pump impeller, forms the liquor stream circulation of fluid torque-converter 1 torus t.Guide wheel 41 and guide wheel stator 46 are provided with along the circumferential direction uniform multiple rollers 45 and the corresponding voussoir 47 of one-way clutch in the space between radial direction, and guide wheel 41 is equivalent to the outer ring of one-way clutch, and guide wheel stator 46 is equivalent to one-way clutch inner ring.Roller 44 makes guide wheel 41 freely rotatable in one direction with the compound action of voussoir 47, and is then fixed in opposite direction.The axial location of guide wheel assembly 40 is limited by the thrust bearing b2 between cover plate 44 and turbine shroud anchor ring 31c in front of the thrust bearing b1 being arranged between pump impeller hub 23 and guide wheel rear cover plate 43 and guide wheel.When turbine 32 is relatively low with the ratio of pump impeller 22 rotating speed (generally less than 0.8 ~ 0.9), the rotation direction that the liquor stream active force that turbine liquor stream w is formed to guide wheel assembly 40 is allowed with one-way clutch mutually makes guide wheel 41 fixing on the contrary, now forms torque increase effect；In turbine assembly 32 with pump wheel assembly 22 rotating speed when comparing high, the liquor stream active force that turbine liquor stream w is formed to guide wheel assembly 40 is identical with the rotation direction that one-way clutch is allowed and allow guide wheel 41 freely rotatable, now do not have torque increase to act on.
Lock-up clutch 50 is arranged on directly over torus, the turbine shroud 31 anchor ring 31a that radially outside is stretched out is as the support chip of the friction plate 51 of lock-up clutch 50, and the pump impeller housing 21 anchor ring 21a that radially outside is stretched out is as another acting surface of lock-up clutch friction pair.Described lock-up clutch 50 need not extra single piston, work fluid can be done directly on anchor ring 31a, with reach so that lock-up clutch 50 is combined or release effect.When operating mode is suitable, can be directly connected to input in conjunction with lock-up clutch and export, motor torque passes through pump cover assembly 10, pump wheel assembly 20 is transferred directly to turbine assembly 30 via lock-up clutch 50.For example, lock-up clutch 50 can be directly connected to pump impeller housing 21 and turbine shroud 31, when lock-up clutch 50 combines, the rotary inertia of turbine assembly 30 is applied directly to pump wheel assembly 20 one end, the turbine amortisseur that this inertia transfer configurations are formed be more beneficial for lock-up clutch with reference to when weaken the vibration that electromotor is transferred to variator.
Torsion vibration absorber assembly 60 is arranged on directly over turbine shroud 31 radial direction, including clamping disk 61, damping spring 62, driven disc 63 and output flange 65.Clamping disk 61 is directly welded in turbine shroud bending section 31b upper end, forms the input of torsion vibration absorber assembly 60.Driven disc 63 as torsion vibration absorber assembly 60 output connects output flange 65 by rivet 64.The damping spring 62a with small diameter is embedded in and has in larger-diameter damping spring 62b, form one group of damping spring 62, multigroup damping spring 62 is distributed in the multiple arcs groove that clamping disk 61 and driven disc 63 are formed, and one end connects clamping disk 61, and one end connects driven disc 63.It is provided with the sealing ring 66 of isolation fluid between the anchor ring of output flange 65 and turbine shroud 31, is provided with the sealing ring 67 of isolation fluid and transmission input shaft 70 between, thus the fluid that ensures to work in torus t does not flow to outside torus chamber.Torsion vibration absorber assembly 60 displacement in the axial direction is limited with the thrust bearing b3 that is arranged between pump cover 11 and output flange 65 by damping spring 62.When lock-up clutch 50 discharges, motor torque passes through pump cover assembly 10, pump wheel assembly 20 is delivered to torus t, through the effect output of torus t fluid power to turbine assembly 30, it is input to transmission input shaft 70 through torsion vibration absorber assembly 60 again, now engine luggine is completely by the fluid power effect isolation of torus t；When lock-up clutch 50 combines, pump wheel assembly 20 and turbine assembly 30 are mechanically connected, motor torque passes through pump cover assembly 10, pump wheel assembly 20 is transferred directly to turbine assembly 30 via lock-up clutch 50, now by the cushioning effect of torsion vibration absorber assembly 60, engine luggine is greatly attenuated.The Optimum utilization by space for the described torsion vibration absorber assembly 60, torsion vibration absorber assembly is arranged on directly over turbine shroud 31, it is less than turbine shroud on the direction pointing to engine side in the axial direction, largely reduce the axial dimension of fluid torque-converter, outstanding damping effect can also be kept simultaneously.
In radially inner side and the stage casing of fluid torque-converter 1, compare existing known fluid torque-converter, it need not design self-contained piston part, thus reduces the axial dimension of device；Radial outside in fluid torque-converter 1, torsion vibration absorber assembly 60 is contained in axial space between lock-up clutch 50 and the pump cover 11 directly over turbine shroud 31 radial direction, it is less than turbine shroud 31 in axial forward direction, the axial dimension equally reducing fluid torque-converter 1 to a great extent.Therefore, the fluid torque-converter 1 of the present invention more they tend in the axial direction compact.
Additionally, this fluid torque-converter 1 can be directly connected to pump impeller housing 21 and turbine shroud 31, when lock-up clutch 50 combines, pump wheel assembly 20 is mechanically connected with turbine assembly 30, forms turbine amortisseur, and its damping performance is more preferable than prior art individual pen amortisseur performance.
The top half along axis of the fluid torque-converter sectional view involved by second embodiment of the present invention is shown in Fig. 2.It is had differences with the internal structure of the fluid torque-converter of first embodiment, thus driven disc 63 is adjusted to and is connected to output flange 65 by rivet 64 in front.The fluid torque-converter internal structure layout of this type so can be better conformed to.
Will be detailed below the work process of fluid torque-converter 1.In vehicle start, under the operating modes such as shift speed change, fluid torque-converter 1 annular space between oil pump support shaft 80 and transmission input shaft 70 is constantly filled with certain pressure work fluid to torus t, form the release oil circuit r of lock-up clutch 50, under the high-voltage oil liquid effect in release oil circuit r, lock-up clutch 50 is pushed to front and discharges completely, motor torque passes through pump cover assembly 10 and pump wheel assembly 20 transmits torus t, through the effect output of torus t fluid power to turbine assembly 30, it is input to transmission input shaft 70 through torsion vibration absorber assembly 60 again, now engine luggine is completely by the fluid power effect isolation of torus t.
Fluid torque-converter 1, when lock-up clutch 50 discharges, leads to the overall transmission efficiency of fluid torque-converter 1 low due to the fluid power effect of torus t, during operating mode therefore generally beyond vehicle start and shift speed change etc. combines lock-up clutch 50.Now fluid torque-converter 1 is constantly filled with certain pressure work fluid between turbine 32 and pump cover 11 in the center in the hole of transmission input shaft 70, form the combination oil circuit a of lock-up clutch 50, with reference under the high-voltage oil liquid effect in oil circuit a, lock-up clutch 50 is pushed to rear and combines, pump wheel assembly 20 is mechanically connected with turbine assembly 30, motor torque passes through pump cover assembly 10, pump wheel assembly 20, lock-up clutch 50 and turbine assembly are transferred to torsion vibration absorber assembly 60, through damping spring 62 effect output to output flange 65 and transmission input shaft 70, engine luggine is weakened by torsion vibration absorber assembly 60 completely.
In lock-up clutch 50 cohesive process, for avoiding the unexpected enormous impact combining and producing, by controlling with reference to the oil liquid pressure that works in oil circuit a, make lock-up clutch 50 be first in slipping state, then be transitioned into and be completely combined.
As above with reference to the accompanying drawings the specific embodiment of the present invention is described in detail.Those skilled in the art can carry out equivalent remodeling or modification to feature specific in embodiment according to the above description.Certainly, the embodiment that these change also will fall in the protection domain that claims are covered.
Claims (12)
1. a kind of fluid torque-converter is it is characterised in that include:
Pump cover assembly；
Pump wheel assembly, it is connected with described pump cover assembly, and for receiving the power of described pump cover assembly transmission；
Turbine assembly, it is arranged between described pump cover assembly and described pump wheel assembly；
Guide wheel assembly, it is positioned between described pump wheel assembly and described turbine assembly by bearing；
Torus, it is surrounded by described pump wheel assembly, described turbine assembly and described guide wheel assembly；
Lock-up clutch, it is connected between described turbine assembly and described pump wheel assembly；And
Torsional balancer assembly, it is arranged between described turbine assembly and described pump cover assembly.
2. fluid torque-converter according to claim 1 it is characterised in that:
Described lock-up clutch is arranged between the turbine shroud of described turbine assembly and the pump impeller housing of described pump wheel assembly along the outside of described torus radial direction.
3. it is characterised in that described lock-up clutch also includes friction plate, described friction plate connects to described turbine shroud fluid torque-converter according to claim 2, and described lock-up clutch passes through to connect turbine shroud described in described friction plate.
4. fluid torque-converter according to claim 3 it is characterised in that:
Described friction plate tilts with regard to described pump impeller housing connection surface.
5. the fluid torque-converter according to Claims 1-4 any one it is characterised in that:
Described torsion vibration absorber assembly includes clamping disk, damping spring, passive disk hole output flange: described clamping disk connects the turbine shroud to described turbine assembly and the power for receiving its transmission；Described damping spring connects described clamping disk and described driven disc respectively, and for power is transferred to described driven disc；Described output flange one end is connected with described driven disc, and the other end is used for connecting to transmission input shaft.
6. fluid torque-converter according to claim 5 it is characterised in that:
Described torsion vibration absorber assembly is arranged between described turbine shroud and the pump cover of described pump cover assembly along described turbine shroud radial outside.
7. fluid torque-converter according to claim 6 it is characterised in that:
Described torsion vibration absorber assembly has vertically less than the outermost thickness of described turbine shroud.
8. fluid torque-converter according to claim 5 it is characterised in that:
Described damping spring includes the first mutually nested damping spring and the second damping spring.
9. the fluid torque-converter according to Claims 1-4 any one it is characterised in that:
Described pump wheel assembly and described guide wheel assembly are axially positioned by thrust bearing；
And/or described turbine assembly and described guide wheel assembly are axially positioned by thrust bearing.
10. a kind of vehicle is it is characterised in that include: oil pump, variator and the fluid torque-converter as described in claim 1 to 9 any one.
11. vehicles according to claim 10 it is characterised in that:
Circulation intracavity between described turbine assembly and described pump wheel assembly forms lock-up clutch release oil pocket, forms lock-up clutch and be combined oil pocket in the cavity between described turbine assembly and described pump wheel assembly；And the gap between the input shaft of the support shaft in described oil pump and described variator is lock-up clutch release action oil circuit, the centre bore of the input shaft of described variator is lock-up clutch combination oil circuit.
12. vehicles according to claim 11 it is characterised in that:
When work fluid in described lock-up clutch release action oil circuit is recycled to described lock-up clutch release oil pocket, described lock-up clutch is in off-position；Motor torque passes sequentially through described pump cover assembly, described pump wheel assembly, described torus, described torsion vibration absorber are transferred to the input shaft of described variator；
When work fluid in described lock-up clutch combination oil circuit is recycled to described lock-up clutch with reference to oil pocket, described lock-up clutch is in binding site；Motor torque passes sequentially through described pump cover assembly, described pump wheel assembly, described lock-up clutch, described turbine assembly, described torsion vibration absorber are transferred to the input shaft of described variator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510424382.5A CN106369129A (en) | 2015-07-20 | 2015-07-20 | Hydraulic torque converter and vehicle with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510424382.5A CN106369129A (en) | 2015-07-20 | 2015-07-20 | Hydraulic torque converter and vehicle with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106369129A true CN106369129A (en) | 2017-02-01 |
Family
ID=57879657
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510424382.5A Pending CN106369129A (en) | 2015-07-20 | 2015-07-20 | Hydraulic torque converter and vehicle with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106369129A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107100979A (en) * | 2017-04-13 | 2017-08-29 | 祁晋 | A kind of new automobile fluid torque-converter and the automobile with the fluid torque-converter |
| WO2020051873A1 (en) * | 2018-09-14 | 2020-03-19 | Schaeffler Technologies AG & Co. KG | Pilot assembly, processing method of pilot assembly and hydraulic torque converter |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006118654A (en) * | 2004-10-22 | 2006-05-11 | Toyota Motor Corp | Fluid transmission device |
| US20150021137A1 (en) * | 2013-07-19 | 2015-01-22 | Schaeffler Technologies Gmbh & Co. Kg | Two pass multi-function torque converter |
| US20150027110A1 (en) * | 2013-07-23 | 2015-01-29 | Schaeffler Technologies Gmbh & Co. Kg | Torque converter including an elastic element preloading an axially movable turbine |
| CN204267639U (en) * | 2014-09-24 | 2015-04-15 | 重庆红宇精密工业有限责任公司 | A kind of fluid torque converter that the sliding cooling that rubs can be provided |
| WO2015081953A1 (en) * | 2013-12-02 | 2015-06-11 | Schaeffler Technologies AG & Co. KG | Device for transmitting torque |
-
2015
- 2015-07-20 CN CN201510424382.5A patent/CN106369129A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006118654A (en) * | 2004-10-22 | 2006-05-11 | Toyota Motor Corp | Fluid transmission device |
| US20150021137A1 (en) * | 2013-07-19 | 2015-01-22 | Schaeffler Technologies Gmbh & Co. Kg | Two pass multi-function torque converter |
| US20150027110A1 (en) * | 2013-07-23 | 2015-01-29 | Schaeffler Technologies Gmbh & Co. Kg | Torque converter including an elastic element preloading an axially movable turbine |
| WO2015081953A1 (en) * | 2013-12-02 | 2015-06-11 | Schaeffler Technologies AG & Co. KG | Device for transmitting torque |
| CN204267639U (en) * | 2014-09-24 | 2015-04-15 | 重庆红宇精密工业有限责任公司 | A kind of fluid torque converter that the sliding cooling that rubs can be provided |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107100979A (en) * | 2017-04-13 | 2017-08-29 | 祁晋 | A kind of new automobile fluid torque-converter and the automobile with the fluid torque-converter |
| WO2020051873A1 (en) * | 2018-09-14 | 2020-03-19 | Schaeffler Technologies AG & Co. KG | Pilot assembly, processing method of pilot assembly and hydraulic torque converter |
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Application publication date: 20170201 |
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