CN107084241A - Torque-converters with variable pitch guide wheel and bypass clutch - Google Patents
Torque-converters with variable pitch guide wheel and bypass clutch Download PDFInfo
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- CN107084241A CN107084241A CN201710083751.8A CN201710083751A CN107084241A CN 107084241 A CN107084241 A CN 107084241A CN 201710083751 A CN201710083751 A CN 201710083751A CN 107084241 A CN107084241 A CN 107084241A
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- guide wheel
- torque
- target
- skidded
- transmission device
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- 238000007599 discharging Methods 0.000 claims 1
- 239000012530 fluid Substances 0.000 description 40
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- 238000000926 separation method Methods 0.000 description 5
- 239000002783 friction material Substances 0.000 description 4
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/14—Control of torque converter lock-up clutches
- F16H61/143—Control of torque converter lock-up clutches using electric control means
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/14—Control of torque converter lock-up clutches
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/48—Control of exclusively fluid gearing hydrodynamic
- F16H61/50—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit
- F16H61/52—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades
- F16H61/56—Control of exclusively fluid gearing hydrodynamic controlled by changing the flow, force, or reaction of the liquid in the working circuit, while maintaining a completely filled working circuit by altering the position of blades to change the blade angle
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/14—Control of torque converter lock-up clutches
- F16H61/143—Control of torque converter lock-up clutches using electric control means
- F16H2061/145—Control of torque converter lock-up clutches using electric control means for controlling slip, e.g. approaching target slip value
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The present invention relates to a kind of torque-converters with variable pitch guide wheel and bypass clutch.Transmission device includes the torque-converters with variable pitch guide wheel and bypass clutch.These parts are controlled to keep target slip speed with both of which.In the first mode, bypass clutch discharges completely, and controls by changing the pitch of guide vane to skid.In a second mode, guide wheel is maintained at the position most tightened, and controls to skid by changing the torque capacity of bypass clutch.Depending on what kind of vehicle operating is carrying out, target skidding is calculated based on a variety of input signals.
Description
The cross reference of related application
The application is the part continuation application for the 14/457th, No. 265 U. S. application submitted for 12nd in August in 2014, should
U. S. application entire disclosure is contained in this by quoting.
Technical field
This disclosure relates to automotive trannsmission system field.More particularly, this disclosure relates to have variable pitch guide wheel
The torque-converters of (variable pitch stator).
Background technology
Many vehicles are used in wide vehicle speed range (including both forward travel and reverse motion).However, some classes
The engine of type can only in narrow velocity interval high-efficiency operation.So, generally using can be under multiple gearratio efficiently
The transmission device of transimission power.When vehicle is in low speed, transmission device is operated generally under high transmission ratio so that engine is turned round
Square doubles to improve acceleration.During in high speed, transmission device is set to operate permission and quiet, fuel-efficient under underneath drive ratio
Cruise association engine speed.Generally, transmission device has mounted to the housing of vehicle structure, driven by engine crankshaft
Input shaft and generally via differential assembly drive wheel of vehicle output shaft, the differential assembly allow in turn inside diameter
When left wheel and right wheel rotated with slightly different rotating speed.
Even if selecting very high gearratio, in stationary vehicle, the input speed of gearbox is also zero.Due to internal combustion hair
Motivation can not produce moment of torsion when rotating speed is zero, therefore use generally between engine and transmission input shaft some classes
The apparatus for starting of type.Common apparatus for starting for automatic transmission is fluid coupling.Fluid coupling be have with
Annular shape is around the pump impeller of transmission device axis and the hydrodynamic torque transmitting device of turbine.When pump impeller rotates soon than turbine
When, pump impeller makes fluid be rotated in ring, to place a torque on turbine and resistive torque is applied on pump impeller.Torque-converters is
Also include the fluid coupling for being kept non-rotary guide wheel.Guide wheel is redirected to flowing so that be applied to the moment of torsion of turbine
More than the resistive torque being applied on pump impeller.When the vehicle is still, turbine is also static, but pump impeller can be connected to engine song
Axle.The speed discrepancy between pump impeller and turbine is attributed to, pump impeller resists the rotation of bent axle.Resistive torque is sufficiently small, is not enough to it
Make engine stall.However, in addition to the fuel needed for unloaded idling, engine must consume extra fuel, so as to overcome
Resistive torque.Many times of engine torque is transferred to the gearbox input for being connected to turbine.
The content of the invention
A kind of transmission device includes torque-converters and controller.The torque-converters include pump impeller, turbine, variable pitch guide wheel and
Bypass clutch.In the first mode, controller is configured as being maintained at and most compact torque-converters characteristic by guide wheel pitch
The torque capacity of regulation bypass clutch is with the holding target skidding between turbine and pump impeller while corresponding setting.Controller
It is reduced to zero in response to the bypass clutch torque capacity and is transformed into second mode.In a second mode, controller by with
It is set to and adjusts guide wheel pitch to keep the target to skid while bypass clutch torque capacity is remained into zero.Controller
Most compact setting is reached in response to guide wheel pitch and returns to first mode.Depending on being carrying out what kind of operation,
The target, which is skidded, can be based on multiple standards.During starting event, target is skidded can be based on pedal position, vehicle speed
Degree, manifold pressure, atmospheric pressure, road grade and/or vehicle mass.During shift occurances, target is skidded can be based on hair
Motivation moment of torsion and/or elapsed time.During the reverse event of moment of torsion, target, which is skidded, can be based on engine torque.
A kind of method for controlling transmission device includes repeatedly measurement slip speed and adjusts the moment of torsion of bypass clutch
Capacity and guide wheel pitch.When guide wheel pitch is in complete deflated state, the moment of torsion of by-pass clutch is adjusted based on slip speed
Capacity.When bypass clutch is kept completely separate, guide wheel pitch is adjusted based on slip speed.In certain embodiments, it can pass through
Change single solenoidal electric current to control both guide wheel pitch and bypass clutch torque capacity.In other embodiments, may be used
To adjust both using two single solenoids.
According to the present invention there is provided a kind of method for controlling transmission device, including：Repeatedly between measurement turbine and pump impeller
Slip speed；When guide wheel pitch is in complete deflated state, the moment of torsion for adjusting bypass clutch based on the slip speed holds
Amount；When bypass clutch is kept completely separate, the guide wheel pitch is adjusted based on the slip speed.
According to one embodiment of present invention, the torque capacity of regulation bypass clutch and regulation guide wheel pitch include
Change single solenoidal electric current.
According to one embodiment of present invention, the torque capacity of regulation bypass clutch includes changing first solenoidal the
One electric current, regulation guide wheel pitch includes changing the second solenoidal second electric current.
According to the present invention there is provided a kind of method for accelerating vehicle, including：When bypass clutch discharges completely, it is based on
The target derived from pedal position and car speed is skidded and led based on the skidding of the measurement between turbine and pump impeller to adjust
Take turns pitch；The state most tightened is reached in response to guide wheel, based on the target skid and the measurement skidding regulation bypass from
The torque capacity of clutch.
According to one embodiment of present invention, target is skidded and also derived from manifold pressure.
According to one embodiment of present invention, target is skidded and also derived from atmospheric pressure.
According to one embodiment of present invention, target is skidded and also derived from road grade.
According to one embodiment of present invention, target is skidded and also derived from vehicle mass.
Brief description of the drawings
Fig. 1 is the schematic diagram of example vehicle power drive system.
Fig. 2 is to be configured to the first torque converter assemblage using two fluid passage control bypass clutches and guide wheel pitch
Schematic cross-section.
Fig. 3 is shown as in two fluid passages of Fig. 2 of the function of single solenoid current torque converter assemblage
The curve map of pressure.
Fig. 4 is to be configured to the second torque converter assemblage using three fluid passage control bypass clutches and guide wheel pitch
Schematic cross-section.
Fig. 5 is shown as in three fluid passages of Fig. 4 of the function of two solenoid currents torque converter assemblage
A pair of curve maps of pressure.
Fig. 6 is to be configured to the 3rd torque converter assemblage using three fluid passage control bypass clutches and guide wheel pitch
Schematic cross-section.
Fig. 7 is the stream of the method for torque-converters of the control with variable pitch guide wheel and bypass clutch during starting event
Cheng Tu.
Fig. 8 is the flow chart for the method that variable pitch guide wheel and bypass clutch are controlled according to target skidding.
Fig. 9 is the stream of the method for torque-converters of the control with variable pitch guide wheel and bypass clutch during shift occurances
Cheng Tu.
Figure 10 is the curve map of the target skidding curve of the function as the time during showing shift occurances.
Figure 11 is the curve map of the target skidding curve of the function as the time during showing the reverse event of moment of torsion.
Embodiment
It is described herein embodiment of the disclosure.However, it should be understood that disclosed embodiment is merely illustrative and other embodiments
Form that is various and substituting can be taken.Accompanying drawing is not drawn necessarily to scale；Some features can be exaggerated or minimized to show spy
Determine the details of part.Therefore, concrete structure and function detail disclosed herein are not necessarily to be construed as limitation, and only as teaching
Lead those skilled in the art and utilize the representative basis of the present invention in a variety of forms.As one of ordinary skill in the art will appreciate
, with reference to the various features that either figure illustrates and describes can with the combinations of features that illustrates in one or more other accompanying drawings,
To produce the embodiment for not being specifically recited or describing.The typical case's application that is combined as of the feature shown provides representative embodiment.
However, the various combinations and modification of the feature consistent with the teaching of the disclosure can be desired to application-specific or embodiment.
Fig. 1 schematically shows vehicle driveline 10.Heavy line indicates the flowing of mechanical output, and dotted line refers to
Show the flowing of information.Explosive motor 12 produces mechanical output by converting the chemical energy of storage in a fuel source.Transmission dress
The rotating speed and moment of torsion of the mechanical output of 14 adjustment engines generation is put to be adapted to being currently needed for for vehicle.From transmission device 14
Mechanical output is transferred to left wheel 16 and right wheel 18 by differential mechanism 20.Roughly equal moment of torsion is supplied to often by differential mechanism 20
Individual wheel, (such as) provides slight speed difference in Ackermann steer angle simultaneously.In rear wheel drive vehicle layout, differential mechanism is also
Rotation axis is changed about 90 degree and rotating speed and moment of torsion are adjusted by fixed base ratio.It is poor in front wheel driving structure
Fast device can be integrated into transmission device, and this is referred to alternatively as transaxle (transaxle).
Transmission device 14 includes two power transmission levels：Torque-converters 22 and gearbox 24.Transmission input shaft 26 is fixed
Ground is connected drivably to engine crankshaft.Power and moment of torsion are transferred to turbine wheel shaft by torque-converters from transmission input shaft 26
28.Gearbox 24 provides multiple gearratios, and it includes multiple forward gear gearratios and at least one back gear ratio.Gearbox 24
It may include to engage with multiple combinations to set up the multiple controllable of multiple flow of power paths with different fixed drive ratios
Clutch.Alternatively or in combination, gearbox 24 may include that the variable-speed motor of any gearratio can be set up between fixed limitation
(variator)。
Gearbox, torque-converters and engine respond to the instruction from controller 30.It is sent to speed change box clutch
Instruction with torque-converters can be communicated by adjusting electric current, and then regulating piston applies the pressure of the fluid in chamber.Control
Device 30 determines the expectation state of transmission device and engine based on the signal from various sensors.These sensors may include
Transmission device and engine sensor, turn of their indication driving gear input shafts 26, turbine wheel shaft 28 and transmission output shaft
Speed.The sensor may also include the accelerator pedal 32 for the driver's operation for indicating driver's power demand.Controller 30 can be with
It is nonshared control unit or independent communication controler (such as vehicle system controller, transmission controller and engine control
Device processed) combination.
Fig. 2 schematically shows the first embodiment of torque-converters 22.Hydraulic power flow path includes pump impeller 34 and whirlpool
Wheel 36.Pump impeller 34 is fixedly joined to transmission input shaft 26, and transmission input shaft 26 is suitable for being fixed to engine song
Axle.Turbine 36 is fixedly joined to turbine wheel shaft 28.Guide wheel 38 is attached to gear mechanism housing 40 by passive one-way clutch 42.
Under low turbine rotating speed, pump impeller 34 makes fluid flow to turbine 36 from pump impeller 34 around ring, to guide wheel 38 and return to pump impeller 34.
Guide wheel 38 is kept by one-way clutch 42 not to be rotated so that guide wheel 38 can change flow direction and provide anti-work for multiple torque
Use moment of torsion.When turbine 36 rotating speed close to pump impeller 34 rotating speed when, the fluid in ring is circumferential with pump impeller and turbine around input shaft
Flow on ground.One-way clutch 42 then surmounts (overrun) so that guide wheel 38 can rotate rather than hinder the flowing.
Controlled by the power flow of hydraulic power flow path by the rotating speed of pump impeller 34 and the rotating speed of turbine 36.Rotating speed with
Relation between moment of torsion is the complicated letter of the complicated function and pump impeller of the geometry of ring, the blade angle of turbine and guide wheel
Number.Under constant secondary speed, both impeller torque and turbine torque increase with the increase of pump impeller rotating speed.It is designed to
The torque-converters being applied to higher resistive torque on pump impeller under given pump impeller rotating speed and secondary speed is referred to as more rigid
(stiffer) or relatively tighten the torque-converters of (tighter), and be designed to for identical pump impeller rotating speed and secondary speed application
The torque-converters of relatively low moment of torsion is referred to as relatively loose (looser) torque-converters.The rigidity of torque-converters may be expressed as turning round pump impeller
The square capacity characteristic or k-factor related to pump impeller rotating speed.Low k-factor indicates the torque-converters tightened, and high k-factor indicates pine
The torque-converters speeded.The ratio of turbine torque and impeller torque generally increases with the increase of pump impeller rotating speed and the ratio of secondary speed.
However, based on power conservation, torque ratio will never be more than rotating ratio.The product of rotating ratio and torque ratio is torque converter, should
Torque converter changes between zero and one as the function of pump impeller rotating speed and secondary speed.Torque ratio in turbine static is claimed
For stall torque ratio.Torque-converters design, which is usually directed to, to be reached desired rigidity, maximize efficiency and is maximizing torque ratio
Between balance.For different vehicle working conditions, best combining properties are different.Piston 44 is via mechanical linkage
The blade of guide wheel 38 is connected to so that the pitch of the mobile change guide vane of piston, so as to change k-factor and torque ratio.
Transmission input shaft 26 selectively bonds to turbine wheel shaft 28 by bypassing clutch, so as to provide the second power
Flow path.Bypassing clutch includes piston 46, and piston 46 is fixedly joined to turbine wheel shaft 28 and had towards input shaft 26
The friction material 48 of a part.Bypass clutch torque capacity with by friction material extrude be against input shaft power into than
Example.When vehicle is cruised with medium speed, it is necessary to power be typically low and fuel efficiency is important.Generally, bypass
Clutch can be engaged during cruising, so as to be transmitted engine torque to turbine wheel shaft with very high efficiency.However, at some
Under situation, particularly under the relatively low velocity with high transmission ratio, due to needing to be carried by hydraulic power flow path
Isolate (torsional vibration isolation) for twisting vibration, therefore bypass clutch can be separated.In these feelings
Under condition, torque converter is very important.Excessively loose torque-converters will allow excessive between engine and turbine wheel shaft
Speed discrepancy, so as to reduce efficiency.In addition, the larger speed discrepancy between engine and turbine wheel shaft to engage bypass clutch more
Plus be difficult to smoothly perform.
In Fig. 2 torque-converters, guide wheel pitch and bypass clutch torque capacity are all used only two fluid passages to control
System.Arrow in Fig. 2 indicates the direction of flow of fluid during bypass clutch separation.Fluid flows out from valve body, passes through turbine wheel shaft 28
In axial passage, reach release chamber 50.Fluid is flowed to using in chamber 52 by friction material 48 therefrom.Friction material
Gap between 48 and input shaft 26 is sufficiently small to be declined with causing release chamber 50 and applying the pressure between chamber 52.From administration
Chamber 52, fluid is flow between pump impeller 34 and turbine 36 in fluid power chamber.Fluid is between guide wheel 38 and pump impeller 34 from liquid
Power chamber flows out.Therefrom, fluid flows through the hole in guide wheel shaft 40 and valve body is returned between guide wheel shaft and turbine wheel shaft.Tighten
Chamber 54 is fluidly connected to the passage between guide wheel shaft and turbine wheel shaft.If the flow resistance between two chambers is sufficiently small
So that they can be considered to have the pressure being substantially the same, then the two chambers are fluidly connected.Even if on the contrary, fluid
It can be flowed between the chamber connected by aperture or by pump, the chamber is nor fluidly connect.Piston 46 passes through release
Chamber 50 and apply chamber 52 between pressure differential and separation point position is also maintained at by return spring 58.
Relaxation chamber 56 is fluidly connected to release chamber 50 by the hole in turbine wheel shaft 28.Rotated with different rotating speeds
Axle between interface, release chamber 50 and relaxation chamber 56 between passage by seal 60 and 62 (by the passage and its
Its chamber isolation) limit.When bypass clutch is kept completely separate, the pressure ratio in relaxation chamber 56 tightens the pressure in chamber 54
It is high.The power that this pressure differential combination spring 64 applies promotes to the right piston 44, and it corresponds to most loose torque-converters characteristic.
Fig. 3 shows how controller orders the guide wheel pitch and clutch capacity of the torque-converters for Fig. 2.Controller is ordered
Make solenoid current.In response to the solenoid current, the fluid pressure in two circuits of one or more valve regulation in valve body
Power.Via turbine wheel shaft 28 central fluid be connected to release chamber 50 first line in pressure follow curve 70.Via
The pressure being connected in the second circuit for tightening chamber 54 follows curve space fluid between turbine wheel shaft 28 and guide wheel shaft 40
72。
When electric current is zero, the pressure in first line forces piston 46 to be moved to off-position and forces piston 44 to move
To loose pitch location.The pressure in the fluid resistance by piston, the second circuit is attributed to less than the pressure in first line
Power.With the increase of solenoid current, two pressure are untill identical speed decreases up to and reaches threshold value.More than the threshold
Value, valve body starts to make the pressure in the second circuit with the increase of solenoid current increase.Pressure balance on piston 44 makes
Obtain for some engine torques and rotating ratio, fluid power active force can make guide wheel pitch move away from most loose position.This claims
For load relevant range.As solenoid current further increases, certain point is reached, at this point, is turned round for all engines
Pressure balance on square and rotating ratio, piston 44 forces guide wheel pitch to be moved to the position most tightened.Select return spring 64
Spring rate so that these transformation threshold values be suitable.When solenoid current further increases, a little 74 are reached, at this
Pressure of the pressure in release chamber 50 in chamber 52 is applied at point, it is sufficient to overcome return spring 58 and shift piston 46 onto
Bonding station.Solenoid current increases above the point so that clutch torque capacity increase.
Fig. 4 shows the torque-converters with variable pitch guide wheel and bypass clutch, and the torque-converters can be by total of three
Fluid passage independent control.Extra passage formation is in guide wheel shaft 40, and this needs guide wheel shaft 40 to have than the guide wheel shaft in Fig. 2
The wide cross section in cross section.Although Fig. 4 shows there is identical thickness in the whole length upper block axle 40 of guide wheel shaft 40,
The cross section for being variable thickness in some cases is probably preferred.The fluid returned in clutch separation from fluid power chamber
Or the fluid when clutch is employed into fluid power chamber is conducted through this new passage.Fluid is via guide wheel shaft 40
Fluid passage between turbine wheel shaft 28 is simultaneously then directed into deflation chamber 54 by the hole in guide wheel shaft 40.Seal 78 will
The two passages are separated.
Fig. 5 shows how controller orders the guide wheel pitch and clutch capacity of the torque-converters for Fig. 4.Controller is ordered
Make two solenoid currents.In response to these solenoid currents, the Fluid pressure in three circuits of valve regulation in valve body.Via
The pressure being connected in the first line of release chamber 50 follows curve 80 central fluid of turbine wheel shaft 28.Via guide wheel shaft stream
The pressure being connected in the second circuit of fluid power chamber follows curve 82 body.Any by pump impeller 34 influences, using chamber 52
In pressure follow pressure in the second circuit.In order that clutch solenoid current is set to by clutch separation, controller
Zero.In order to apply clutch, controller makes the increase of clutch solenoid current.When pressure 82 exceedes pressure 80, flow of fluid
Direction it is reverse.Online 84 right side, clutch torque capacity increases with the increase of clutch solenoid current.Line 84
Position can be by selecting suitable spring rate to be conditioned for spring 58, and in this construction, spring 58 is optional.
It is connected in the tertiary circuit for tightening chamber 54 interstitial fluid between guide wheel shaft 40 and turbine wheel shaft 28
Pressure follows curve 86.Controller adjusts pitch solenoid current, to adjust the pitch of guide vane.No matter the state of clutch
How, controller all can adjust guide vane pitch.However, the related scope of the scope of relaxation, load and the scope of deflation it
Between the pressure that depends in first line of border, therefore controller must compensate accordingly for.
Fig. 6 shows the torque-converters with variable pitch guide wheel and bypass clutch, and the torque-converters can be by total of three
Fluid passage independent control.Relaxation chamber 56 in Fig. 2 and Fig. 4, which is fluidly connected to, discharges chamber 50, and the relaxation in Fig. 6
Chamber 56' is fluidly connected to the passage that fluid is returned through it from fluid power chamber in clutch separation.Fig. 6 torque-converters
Operating is similar with the operating of Fig. 4 torque-converters.However, between the scope of the scope of relaxation, the scope of load correlation and deflation
Border non-pressure 80 depending on pressure 82.Because pressure 82 tends to for many situations that controller adjusts guide wheel pitch
Close to zero, it is therefore desirable to less compensation.
Fig. 7 and Fig. 8 show the mistake that guide wheel pitch and bypass clutch torque capacity are controlled during vehicle start is operated
Journey.When the vehicle is still, it is necessary to be skidded on apparatus for starting so that engine can operate to produce torsion with enough speed
Square.During driveaway operation, vehicle no longer needs beating on apparatus for starting from static be converted to for appropriate power operation
Sliding speed (although because other reasons may still need to skid).At 80, pattern variable is initialized as 1.
At 82, the target that controller is calculated on torque-converters is skidded.It can be the function of multiple parameters that target, which is skidded, described
Parameter includes car speed, accelerator pedal position, manifold pressure, atmospheric pressure, road grade and the vehicle mass of estimation.Typically
For, target is skidded to be reduced with the increase of car speed, because needing gradually to subtract for given engine speed
Few skidding.(for example transmission output shaft turns other speed proportional to car speed during whole driveaway operation
Speed or secondary speed) it may be used as the replacement of car speed.Accelerator pedal position combination car speed indicates that driver's power is needed
Ask.Typically, target is skidded increase as accelerator pedal position increases because the higher engine speed of needs with
Produce more power.Engine torque output is closely related with Manifold Air Pressure.For turbocharged engine, manifold pressure
Power only may gradually increase during driveaway operation.In order to compensate this point, when manifold pressure is relatively low, target, which is skidded, to be increased
Plus, cause higher engine speed.Higher engine speed causes more instant moment of torsion and also increases manifold pressure
Advance the speed.Controller is also conceivable to environment atmospheric pressure.When atmospheric pressure is low (such as at High aititude), manifold pressure
Set up slower.Therefore, target, which is skidded, to increase as atmospheric pressure is reduced.Finally, road grade and vehicle mass be all
Influence the relation between transmission output torque and vehicle acceleration.Abrupt slope and/or it is high-quality when, controller can increase
Target is skidded preferably to be accelerated with being provided at given pedal position.
Controller, which has, is used for the several mechanisms for adjusting and skidding of being skidded towards the target.Make change by adjusting guide wheel pitch
The torque capacity of the deflation of square device and increase bypass clutch both increases the load on engine, is skidded so as to tend to reduce.Root
According to process being shown in Fig. 8 and being discussed in more detail below, these parameters are adjusted at 84.Increase engine torque output to tend to
In increasing skidding.Engine torque output is adjusted at 86.At 88, controller is determined based on whether driveaway operation completes
Whether repeat step 82,84 and 86.For example, when target is skidded and is reduced to below threshold value, controller can determine that starting is completed.
Fig. 8 shows the process of the regulation guide wheel pitch used at 84 and bypass clutch torque capacity.Surveyed at 90
Amount is actual to skid, and calculates skidding error using the skidding at 92.Direct measurement pump impeller rotating speed and secondary speed can be passed through
And subtract secondary speed to measure skidding from pump impeller rotating speed.Or, pump impeller rotating speed can be inferred to from the speed of some other measurements
And/or secondary speed.At 94, which pattern (as indicated by pattern variable), the process are active depending on
Carry out branch.In the first mode, at 96, bypass clutch is set at the position being kept completely separate, and is missed based on skidding
Difference adjusts guide wheel pitch.Specifically, if skidding error is just (more than desired skidding), regulation guide wheel pitch is so as to become
Square device tightens.On the contrary, if skidding error is negative (fewer than desired skidding), regulation guide wheel pitch is so that torque-converters relaxes.
If guide wheel pitch is in its position most tightened at 98 after adjustment, pattern variable is set to 2 at 100, with
Change the following execution of Fig. 8 subprocess.In a second mode, at 102, guide wheel pitch is maintained at the state most tightened, together
When based on skidding regulating error bypass clutch torque capacity.If bypassing clutch at 104 after adjustment to release completely
Put, then pattern variable is set to 1 at 106, performed with the following of subprocess for changing Fig. 8.
Fig. 9 and Figure 10 are shown controls guide wheel pitch and bypass clutch torque capacity during transmission device shift occurances
Process.Wish to skid during shifting gears and may feel the hair of the torque disturbances at the output shaft of dislike to reduce automotive occupant
It is raw.Transmission efficiency is reduced due to skidding, so excessive or prolonged skidding should be avoided.It is at 110, pattern variable is initial
Turn to 2.At 112, initial time is recorded as t0.At 114, controller the target on torque-converters is skidded as the time and
The function of other specification (such as engine torque) is calculated.Generally, target is skidded and increased with the increase of engine torque
Plus, because the size increase of potential torque disturbances.Engine torque can directly or be equally used, can also be used
The some other moments of torsion proportional to engine torque in whole shift occurances.As shown in Figure 10, target is skidded and is used as the time
Function gradually increase.At 116, adjust guide wheel pitch and bypass clutch torque capacity to realize according to Fig. 8 subprocess
Target is skidded.In t1After second, the process enters the maintenance stage of skidding at 118.
During the maintenance stage of skidding, the function that target is skidded only as engine torque at 120 is calculated.
The skidding is realized at 122 using Fig. 8 subprocess.During the stage, controller adjusts the torsion of shift clutch at 124
Square capacity is to realize gearshift.When controller determines that gearshift is completed, the stage terminates at 126.This can be for example by becoming
Fast case gearratio reaches new value to determine.At 128, the time for being converted to the ramp down stage is registered as t2.At 130,
Target is calculated as indicated in fig. 10 to skid with t3It will be skidded in the period of second and be smoothly reduced to zero.Used at 132
Fig. 8 subprocess realizes that target is skidded.The termination of determination process at 134.
Although Fig. 9 and Figure 10 are related to shift occurances, the process can be used for benefiting from its of controlled torque converter slip
The bend the throttle event of the quick increase power of the small amendment of his types of events, such as driver request.Figure 11 is shown
The target skidding function in each stage how should be corrected and mitigate impact cross noise to handle the reverse event of moment of torsion.In
Between in the stage, as engine torque (or some other representative moments of torsion) changes direction, target is skidded from positive transition to negative
To.In addition to the skidding control related to discrete event, Fig. 8 process can be used for controlling the skidding in the case of the long period,
NVH for example during low engine speed (overload) is operated with cylinder deactivation operation mitigates.
Although described above is exemplary embodiment, being included it is not intended that these embodiments describe claim
All possible form.The word used in specification non-limiting word for descriptive words, and it will be understood that not
Various changes can be made in the case of departing from spirit and scope of the present disclosure.As it was previously stated, the spy of each embodiment can be combined
Levy to form the further embodiment that the possibility of the present invention is not explicitly described or illustrated.Although expecting on one or more
Characteristic, multiple embodiments may be described as providing advantage or better than other embodiments or the embodiment of prior art, but
It is one or more feature or characteristic it will be appreciated by one of ordinary skill in the art that according to concrete application and embodiment
It can be compromised to realize desired total system attribute.Therefore, it is described as be in one or more characteristics and is not so good as other realities
The desirable embodiment of embodiment of example or prior art is applied not outside the scope of the present disclosure, and expect to be used for it is specific should
With.
Claims (11)
1. a kind of transmission device, including：
Torque-converters, with pump impeller, turbine, variable pitch guide wheel and bypass clutch；With
Controller, is configured as：
In the first mode, while the corresponding pitch of the torque-converters characteristic that is maintained at guide wheel with most tightens is set by regulation
Logical clutch torque capacity is with the holding target skidding between turbine and pump impeller；
It is reduced to zero in response to the bypass clutch torque capacity and is converted to second mode；
In a second mode, guide wheel pitch is adjusted to keep while the bypass clutch torque capacity is remained into zero
State target skidding；
Reach that the pitch is set and returns to first mode in response to guide wheel pitch.
2. transmission device as claimed in claim 1, wherein, the controller is further configured to：In vehicle start event
Period, the target is calculated based on pedal position and car speed and skidded.
3. transmission device as claimed in claim 2, wherein, the target, which is skidded, is also based on manifold pressure.
4. transmission device as claimed in claim 2, wherein, the target, which is skidded, is also based on atmospheric pressure.
5. transmission device as claimed in claim 2, wherein, the target, which is skidded, is also based on road grade.
6. transmission device as claimed in claim 2, wherein, the target, which is skidded, is also based on vehicle mass.
7. transmission device as claimed in claim 1, wherein, the controller is further configured to：During shift occurances,
The target is calculated based on engine torque to skid.
8. transmission device as claimed in claim 7, wherein, the target, which is skidded, is also based on elapsed time.
9. transmission device as claimed in claim 1, wherein, the controller is further configured to：In the reverse event of moment of torsion
Period, the target is calculated based on engine torque and skidded.
10. a kind of method for controlling transmission device, including：
Repeatedly measure the slip speed between turbine and pump impeller；
When guide wheel pitch is in complete deflated state, the torque capacity of bypass clutch is adjusted based on the slip speed；
When bypass clutch is kept completely separate, the guide wheel pitch is adjusted based on the slip speed.
11. a kind of method for accelerating vehicle, including：
When bypassing clutch and discharging completely, skidded based on the target derived from pedal position and car speed and be based on turbine
The skidding of measurement between pump impeller adjusts guide wheel pitch；
The state most tightened is reached in response to guide wheel, bypass clutch is adjusted based on the skidding of target skidding and the measurement
The torque capacity of device.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US15/044,136 | 2016-02-16 | ||
| US15/044,136 US10118624B2 (en) | 2014-08-12 | 2016-02-16 | Torque converter having variable pitch stator and bypass clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107084241A true CN107084241A (en) | 2017-08-22 |
| CN107084241B CN107084241B (en) | 2020-07-07 |
Family
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710083751.8A Expired - Fee Related CN107084241B (en) | 2016-02-16 | 2017-02-16 | Torque converter with variable pitch stator and bypass clutch |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN107084241B (en) |
| DE (1) | DE102017103136A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111425578A (en) * | 2019-01-09 | 2020-07-17 | 通用汽车环球科技运作有限责任公司 | Torque converter assembly and method of operating the same |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102022123430A1 (en) | 2022-09-14 | 2024-03-14 | Voith Patent Gmbh | Synchronous point detection for converter clutch |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101118017A (en) * | 2006-08-01 | 2008-02-06 | 通用汽车环球科技运作公司 | Torque converter clutch lock on method and low slip regulation |
| US20080254941A1 (en) * | 2007-04-11 | 2008-10-16 | Jeffery Scott | Controlling the operating states of a torque converter clutch in an automatic transmission |
| US20090065319A1 (en) * | 2007-08-29 | 2009-03-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque converter with stator shaft one-way clutch |
| EP2048415A2 (en) * | 2007-10-11 | 2009-04-15 | GM Global Technology Operations, Inc. | Torque converter control method and apparatus |
| DE102009010127A1 (en) * | 2008-03-14 | 2009-09-17 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque converter reverse clutch system and method of operating a reverse clutch system |
| CN103386972A (en) * | 2012-05-07 | 2013-11-13 | 福特全球技术公司 | Method for controlling hybrid vehicle |
-
2017
- 2017-02-16 CN CN201710083751.8A patent/CN107084241B/en not_active Expired - Fee Related
- 2017-02-16 DE DE102017103136.7A patent/DE102017103136A1/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101118017A (en) * | 2006-08-01 | 2008-02-06 | 通用汽车环球科技运作公司 | Torque converter clutch lock on method and low slip regulation |
| US20080254941A1 (en) * | 2007-04-11 | 2008-10-16 | Jeffery Scott | Controlling the operating states of a torque converter clutch in an automatic transmission |
| US20090065319A1 (en) * | 2007-08-29 | 2009-03-12 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque converter with stator shaft one-way clutch |
| EP2048415A2 (en) * | 2007-10-11 | 2009-04-15 | GM Global Technology Operations, Inc. | Torque converter control method and apparatus |
| DE102009010127A1 (en) * | 2008-03-14 | 2009-09-17 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque converter reverse clutch system and method of operating a reverse clutch system |
| CN103386972A (en) * | 2012-05-07 | 2013-11-13 | 福特全球技术公司 | Method for controlling hybrid vehicle |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111425578A (en) * | 2019-01-09 | 2020-07-17 | 通用汽车环球科技运作有限责任公司 | Torque converter assembly and method of operating the same |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107084241B (en) | 2020-07-07 |
| DE102017103136A1 (en) | 2017-08-17 |
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