CN105143701A - Method for determining hysteresis of clutch operation - Google Patents
Method for determining hysteresis of clutch operation Download PDFInfo
- Publication number
- CN105143701A CN105143701A CN201480023004.XA CN201480023004A CN105143701A CN 105143701 A CN105143701 A CN 105143701A CN 201480023004 A CN201480023004 A CN 201480023004A CN 105143701 A CN105143701 A CN 105143701A
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- Prior art keywords
- clutch
- actuator
- stroke
- actuator range
- hysteresis block
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- 238000000034 method Methods 0.000 title claims abstract description 19
- 238000002485 combustion reaction Methods 0.000 claims abstract description 21
- 230000000694 effects Effects 0.000 abstract description 3
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 230000001419 dependent effect Effects 0.000 abstract 1
- 230000033001 locomotion Effects 0.000 description 8
- 230000003111 delayed effect Effects 0.000 description 6
- 230000003116 impacting effect Effects 0.000 description 6
- 230000006978 adaptation Effects 0.000 description 5
- 230000003044 adaptive effect Effects 0.000 description 4
- 230000000630 rising effect Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/10—System to be controlled
- F16D2500/104—Clutch
- F16D2500/10406—Clutch position
- F16D2500/10412—Transmission line of a vehicle
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3026—Stroke
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/302—Signal inputs from the actuator
- F16D2500/3027—Torque
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/306—Signal inputs from the engine
- F16D2500/3065—Torque of the engine
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/702—Look-up tables
- F16D2500/70205—Clutch actuator
- F16D2500/70235—Displacement
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/702—Look-up tables
- F16D2500/70252—Clutch torque
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70402—Actuator parameters
- F16D2500/7041—Position
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/70—Details about the implementation of the control system
- F16D2500/706—Strategy of control
- F16D2500/70605—Adaptive correction; Modifying control system parameters, e.g. gains, constants, look-up tables
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A method for controlling the mechanical power transmitted between an internal combustion engine and a transmission by a friction clutch device in a motor vehicle drive train, wherein the occurring hysteresis effects are compensated by means of a hysteresis module, wherein the hysteresis module describes an actuator stroke and an associated engagement stroke, and wherein, in addition to an engagement stroke variation which is dependent on the actuator stroke, an engagement stroke variation which is independent of the actuator stroke can be described.
Description
Technical field
The present invention relates to a kind of method for controlling the mechanical output transmitted between internal-combustion engine and speed changer by the friction clutch device in motor vehicle driveline, wherein compensating the lagging influence of appearance by means of hysteresis block.
Background technique
A kind of known method from DE102011011152A1, for by means of the friction clutch controlling to be arranged between internal-combustion engine and speed changer along the clutch actuator via clutch characteristics curve and the operational stroke that can be associated via the rated moment of the friction clutch transmission axially operating element of actuating friction clutch, wherein to delayedly compensating of occurring along operational stroke between rated moment and the actual moment via friction clutch actual transfer, its mode is: revised by means of correction variable by the rating value determined in order to solenoidoperated cluthes actuator.According to DE102011011152A1, determine to revise variable in by the hysteresis block run with the significant variable of clutch actuator of friction clutch.Correction variable and operational stroke are formed to two-stage relatively.
Summary of the invention
The present invention is based on following object, functionally improve the method starting to mention.Especially, functionally hysteresis block should be improved.Especially, the control of friction clutch device should be accurately described.Especially, the adaptation ability of clutch module should be improved.Especially, the description to the hysteresis characteristic of the reality of friction clutch device in hysteresis block should be improved.Especially, should reduce or avoid module error.Especially, the error adaptation of software friction factor should be reduced.Especially, the steadiness about the jarring effect that can not accurately predict should be obtained or improve.
This object realizes by a kind of method for controlling the mechanical output transmitted between internal-combustion engine and speed changer by the friction clutch device in motor vehicle driveline, the lagging influence of appearance is wherein compensated by means of hysteresis block, wherein hysteresis block describes actuator range and the joint stroke be associated, and wherein except the joint stroke relevant to actuator range change, the joint stroke irrelevant with actuator range can be described and change.
Friction clutch device can automatically be operated.Friction clutch device can have at least one friction clutch.Friction clutch device can have unique friction clutch.Friction clutch device can have single clutch.Friction clutch device can have clutch input block and clutch output block.Friction clutch device can have two friction clutches.Friction clutch device can have double clutch.Friction clutch device can have a clutch input block and two clutch output blocks.
Friction clutch can realize the power transimission of increase from the operating position opened completely in the operatively controlled mode of foundation towards completely closed operating position, in the described operating position opened completely, substantially power transimission is not carried out between clutch input block and clutch output block, in described completely closed operating position, between clutch input block and clutch output block, substantially carry out power transimission completely, carry out to the power transimission frictional fit wherein between clutch input block and clutch output block.On the contrary, from completely closed operating position towards the operating position opened completely can realize the power transimission reduced according to operatively controlled mode, in described completely closed operating position, substantially power transimission is completely carried out between clutch input block and clutch output block, in the described operating position opened completely, between clutch input block and clutch output block, substantially do not carry out power transimission.Double clutch can be used in, and switches the poower flow from clutch input block in the mode of the conversion of transition between first clutch output block and second clutch output block.
Friction clutch can be single plate clutch.Friction clutch can be multiplate clutch.Friction clutch can be dry clutch.Friction clutch can be wet clutch.Friction clutch can be pressure type clutch.Friction clutch can be pull type clutch.Friction clutch can have rotation axis.Clutch input block can have housing parts, at least one platen and at least one pressure strip.At least one platen and housing parts can be fixed to one another connection.At least one pressure strip and housing parts can distinguish antitorque connection each other.At least one pressure strip can in axial direction move between clutch open position and clutch operating position relative at least one platen limitedly.At least one pressure strip also can be referred to as joint towards the movement in the direction of clutch operating position.At least one pressure strip also can be referred to as separation towards the movement in the direction of clutch open position.Clutch output block can have at least one driven disc.At least one driven disc can clamp between at least one platen and at least one pressure strip in order to frictional fit ground power transimission.
Friction clutch device can have operation equipment.Operation equipment can be used in automatically actuating friction clutch device.Operation equipment can have at least one actuator.At least one actuator can be used at least one pressure strip mobile.At least one actuator can control by means of at least one controller for electric consumption.
Motor vehicle driveline can have internal-combustion engine.Motor vehicle driveline can have torsional oscillation deflate device, especially double mass flywheel.Motor vehicle driveline can have friction clutch device.Motor vehicle driveline can have speed changer.Motor vehicle driveline can have at least one drivable wheel of vehicle.Motor vehicle can have at least one controller for electric consumption.Control gear can be used in controlling combustion engine, friction clutch device and/or speed changer.Control gear can be used in automatically actuating friction clutch device.Control gear can have in multiple structure and/or the control module be functionally separated.Control module can be connected to each other in the mode of conducted signal.
Control mechanical output to be undertaken by control moment.Control mechanical output also to be undertaken by controlling rotating speed.In order to control mechanical output, the viewer of actual friction clutch device runing adjustment technical elements can be parallel to.Viewer can comprise adaptive clutch module.Viewer can comprise the imitation of the friction clutch device to reality.Viewer can comprise regulator.At least one input variable of viewer can based at least one input variable of the friction clutch device of reality.At least one other the input variable of viewer can based at least one measurand of the friction clutch device of reality.
The delayed clutch that can comprise opens component and clutch closes component.Delayedly can be affected by mechanical friction.Delayed can being retracted property impact.Hysteresis block can based on traction indicator model.Traction indicator model can show as the traction indicator in elongated hole.When elongated hole moves, when contacting with bore edges, traction indicator can be driven.When the moving direction change of elongated hole, first traction indicator can keep static, until set up the contact with opposite bore edges.
Changing to describe the joint stroke irrelevant with actuator, joint stroke can be changed when not changing actuator range time controling.Time controling can carry out by means of time parameter.Time parameter can set.
Changing to describe the joint stroke irrelevant with actuator range, can change under the condition considering hysteresis block error when not changing actuator range and engaging stroke.Hysteresis block can be affected by least one module parameter.Module parameter can be internal-combustion engine moment.Module parameter can be clutch torque.Hysteresis block error can be associated with the module parameter be responsible for, and described module parameter can be corrected.Hysteresis block error can be determined under the condition considering equalising torque.Equalising torque can be determined under consideration internal-combustion engine moment and the condition based on the moment of clutch characteristics curve.When determining the moment based on clutch characteristics curve, can consider to engage and/or separated region, friction clutch device not transmitted power in described joint and/or separated region.When determining the moment based on clutch characteristics curve, contact (Tastpunkt) can be considered.Clutch characteristics curve can have slope.Clutch torque can be proportional with impacting force.
Hysteresis block error can according to equation T
k_BKM-T
k_KKL=T
errordetermine.T
k_BKMcan be following clutch torque, described clutch torque be determined based on internal-combustion engine moment.T
k_KKLcan be following clutch torque, described clutch torque be determined based on clutch characteristics curve.T
errorcan be following moment, described moment draws from lag model error.Lag model error can determine by means of traction indicator module and the position of drawing indicator can be amendable module parameter.
In addition, the present invention based on object can realize by a kind of delayed method in friction clutch for determining in motor vehicle, wherein determine delayed by means of lag model, wherein lag model is formed by the traction indicator in the marginate elongated hole of tool, wherein draw indicator when elongated hole move and while move with elongated hole when contacting with the marginal existence of elongated hole, and draw indicator and also can move when the edge of itself and elongated hole is contactless.The motion of traction indicator can be the motion to the time controling in the neutral position of elongated hole when the edge of itself and elongated hole is contactless of traction indicator.The moving direction of traction indicator can work as the edge of itself and elongated hole contactless time drawn by the determined error in equalising torque.
Briefly and in other words, therefore, the clutch hysteresis block be also expanded by the present invention.The clutch hysteresis block of expansion can be structured in hysteresis block, and described hysteresis block shows substantially as the traction indicator in elongated hole.Traction indicator can be driven by the side in the both sides of elongated hole.Described expansion can propose, and traction indicator also can move when it does not contact with the edge of elongated hole.The motion of traction indicator when the EDGE CONTACT not from elongated hole can control with different types: 1. move in the neutral position of elongated hole time controling; 2. the moving direction of drawing indicator is determined by the possible known module error in equalising torque.
By " can " especially represent optional feature of the present invention.Therefore, corresponding exist following embodiment of the present invention, and described embodiment has a corresponding feature or multiple corresponding feature.
By method according to the present invention, functionally improve hysteresis block.The control of accurate explanation friction clutch device.Improve the adaptation ability of clutch module.Improve in lag model the description of the hysteresis characteristic of the reality of friction clutch device.Reduce or avoid module error.Reduce the error adaptation of software friction factor.Obtain or improve the steadiness relative to the jarring effect that can not accurately predict.
Accompanying drawing explanation
Below, embodiments of the invention are described in detail with reference to the attached drawings.Other feature and advantage are obtained from described description.The concrete feature of these embodiments can be general feature of the present invention.These embodiments' also can be each feature of the present invention with the feature of other feature associations.
Accompanying drawing is schematically and exemplarily illustrate:
Fig. 1 illustrates the chart of the conventional structure of adaptive clutch module;
Fig. 2 illustrates the chart of the internal-combustion engine module of physics;
Fig. 3 illustrates the chart of the clutch torque when clutch is opened;
Fig. 4 illustrates the chart of the clutch torque when clutch closes;
Fig. 5 illustrates the chart of the joint stroke change relevant to actuator range;
Fig. 6 illustrates the chart of the joint stroke change relevant to actuator range;
Fig. 7 illustrates the chart of the joint stroke change relevant to actuator range;
Fig. 8 illustrates the chart of the joint stroke change relevant to actuator range, and
Fig. 9 illustrates the chart that the joint stroke had nothing to do with actuator range changes.
Embodiment
Fig. 1 illustrates the chart 100 of the conventional structure of adaptive clutch module.Actual friction clutch 102 is arranged between internal-combustion engine and speed changer in motor vehicle driveline.Friction clutch 102 for controllably open and close Power Train, can realize starting and the conversion of speed change level of speed changer.Friction clutch 102 is automatically operated by means of actuator.Actuator controls by means of controller for electric consumption.By means of control gear, perform regulation technology method.In order to control actuator and then in order to actuating friction clutch 102, use adaptive clutch module.The clutch module of this adaptation illustrates by means of the viewer 104 of regulation technology.
Viewer 104 and friction clutch 102 are arranged in parallel.Viewer 104 by observed friction clutch 102 known also referred to as the clutch input torque for internal-combustion engine moment 106 with rebuild also referred to as the clutch output torque for clutch torque 108 clutch torque calculated.To this, viewer 104 imitates observed friction clutch 102 as module 110 and comprises regulator, and actual clutch torque 108 followed the trail of by described regulator.In addition, viewer 104 comprises hysteresis block 112, with revise clutch module 110 by the error of delayed decision.Error moment 116 flows to the clutch torque 108 of hysteresis block 112 as reality and the difference of the precalculated clutch torque 114 of head.Therefrom determine to revise variable 118 by means of hysteresis block 112.Except internal-combustion engine moment 106, correction variable 118 is flowed to clutch module 110, make to consider the lagging influence to the clutch torque calculated adaptedly.
Fig. 2 illustrates the chart 200 of the internal-combustion engine module of physics.By means of internal-combustion engine module, based on internal-combustion engine moment T
bKM, internal-combustion engine rotational speed n
bKMwith internal-combustion engine acting J
bKMdetermine clutch torque T
k.Described clutch torque is also referred to as being T
k_BKM.
Fig. 3 illustrates the chart 300 of the clutch torque 302 when clutch is opened.Clutch characteristics curve 304 shown in chart 300.At this, x-axis describes actuator range and describe clutch torque in y-axis.Clutch torque and friction clutch, such as proportional according to the impacting force of the friction clutch 102 of Fig. 1.Clutch characteristics curve 304 from the clutch opened completely along with actuator range increase until contact 306 is flatly stretched.Contact 306 is following points, at described some place, starts clutch torque rising along with actuator range increases.In the described region 308 existing for current actuator position 310, along with actuator range increases, clutch torque does not also rise.
Fig. 4 illustrates the chart 400 of the clutch torque 402 when clutch closes.Clutch characteristics curve 404 is shown in graph 400.At this, x-axis describes actuator range and describe clutch torque in y-axis.Clutch torque and friction clutch, impacting force as the friction clutch 102 according to Fig. 1 is proportional.Clutch characteristics curve 404 linearly stretches with slope a along with actuator range increases from contact 406 with rising.In the described region 408 existing for current actuator position 410, along with actuator range increases, there is the rising of clutch torque.Actuator loads friction clutch 414 in the mode shown in modelling when inserting Compress Spring 412.Along with actuator range increases, the impacting force of friction clutch 414 increases and transmits the clutch torque increased.
Fig. 5-8 illustrates clutch module, the chart of the view relevant to actuator range as the joint stroke change in clutch module 110 respectively.In these charts, in x-axis, describe actuator range respectively and describe clutch torque in y-axis.Clutch torque and friction clutch, such as proportional according to the impacting force of the friction clutch 102 of Fig. 1.At actuator and friction clutch, as according to illustrating by means of the traction indicator 500 guided in elongated hole 502 respectively with being coupled modelling between the friction clutch 102 of Fig. 1.At this, elongated hole 502 arranges to actuator and draws indicator 500 and arranges to the pressure strip loaded by actuator of friction clutch.In chart 504, traction indicator 500 abuts on the edge on the right of elongated hole 502.Actuator is arranged in actuator position 506.When b's elongated hole moves in the direction of the arrow, as shown in chart 508, until first actuator position 510 does not drive traction indicator 500, until traction indicator 500 abuts on the edge on the left side of elongated hole 502.Described actuator range is corresponding to the length of elongated hole 502 and lagging width 512.Friction clutch is loaded under the condition of the Compress Spring 514,516 that actuator modelization is illustratively arranged in series insertion two.Along with actuator range increases, at this, Compress Spring 514 is pressed together, and Compress Spring 516 and then friction clutch are not also loaded owing to rubbing.When elongated hole 502 continues c motion in the direction of the arrow, as shown in chart 518, until actuator position 520, drive traction indicator 500.Along with actuator range increases, also Compress Spring 516 is pressed together at this, wherein overcomes friction, and then load friction clutch.Elongated hole 502 in the direction of the arrow d reverse motions time, as shown in chart 522, until actuator position 524, first do not drive traction indicator 500, until traction indicator 500 again abut on the edge on the right of elongated hole 502.Described actuator range is again corresponding to length and the lagging width 512 of elongated hole 502.Along with actuator range increase, at this, Compress Spring 514 by off-load, wherein Compress Spring 516 due to friction also not by off-load and friction clutch be also loaded.When d continues motion to elongated hole 502 in the direction of the arrow, just drive traction indicator 500 and the state be back to shown in chart 504.
Fig. 9 illustrates clutch module, chart 600 as the view had nothing to do with actuator range of the joint stroke change in clutch module 110.From shown in Figure 7, wherein until actuator position 520 drives traction indicator 500, to be pressed together by Compress Spring 516 under the condition overcoming friction and under the state loading friction clutch, with actuator range, joint stroke can be independently shown in clutch module, its mode is: when the actuator range do not continued when actuator position 602 remains unchanged, and Compress Spring 516 continues to be pressed together and clutch torque 604 e raising in the direction of the arrow.Whereby, describe such as because the impacting force shaken and be accompanied by this when actuator position is constant improves the lagging influence caused.In addition, addedly, especially with reference to figure 5-8 and relevant description.
Reference numerals list:
100 charts
102 friction clutches
104 viewers
106 internal-combustion engine moments
108 clutch torque
110 clutch modules
112 hysteresis block
114 clutch torque
116 error moments
118 revise variable
200 charts
300 charts
302 clutch torque
304 clutch characteristics curves
306 contacts
308 regions
310 actuator positions
400 charts
402 clutch torque
404 clutch characteristics curves
406 contacts
408 regions
410 actuator positions
412 Compress Springs
414 friction clutches
500 traction indicators
502 elongated holes
504 charts
506 actuator positions
508 charts
510 actuator positions
512 lagging widths
514 Compress Springs
516 Compress Springs
518 charts
520 actuator positions
522 charts
524 actuator positions
600 charts
602 actuator positions
604 clutch torque
Claims (8)
1. one kind for controlling the method for the mechanical output (108) transmitted between internal-combustion engine and speed changer by the friction clutch device (102) in motor vehicle driveline, the lagging influence of appearance is wherein compensated by means of hysteresis block (112)
It is characterized in that, the joint stroke that described hysteresis block (112) is described actuator range and is associated, wherein except the joint stroke relevant to actuator range change (500,508,518,522), outside, the joint stroke irrelevant with actuator range can be described and change (600).
2. method according to claim 1, is characterized in that, changing, changing joint stroke when not changing actuator range time controling to describe the joint stroke irrelevant with actuator range.
3. method according to claim 1, is characterized in that, changing (600), can change engage stroke when not changing actuator range and consider hysteresis block error to describe the joint stroke irrelevant with actuator range.
4. method according to claim 3, is characterized in that, described hysteresis block error is associated with the module parameter be responsible for and described module parameter is corrected.
5. the method according to item at least one in claim 3 to 4, is characterized in that, under the condition considering equalising torque, determine described hysteresis block error.
6. method according to claim 5, is characterized in that, under consideration internal-combustion engine moment and the condition based on the moment of clutch characteristics curve, determine described equalising torque.
7. the method according to item at least one in claim 3 to 6, is characterized in that, according to equation T
k_BKM-T
k_KKL=T
errordetermine described hysteresis block error.
8. the method according to item at least one in claim 3 to 4, is characterized in that, determine hysteresis block error, and the position of drawing indicator (500) is the module parameter that can revise by means of traction indicator module.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013207506.5 | 2013-04-25 | ||
| DE102013207506 | 2013-04-25 | ||
| DE102013211586.5 | 2013-06-20 | ||
| DE102013211586 | 2013-06-20 | ||
| PCT/DE2014/200154 WO2014173407A2 (en) | 2013-04-25 | 2014-04-04 | Method for controlling a mechanical output transmitted by a friction clutch device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105143701A true CN105143701A (en) | 2015-12-09 |
| CN105143701B CN105143701B (en) | 2017-10-03 |
Family
ID=50639246
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480023004.XA Active CN105143701B (en) | 2013-04-25 | 2014-04-04 | Method for determining hysteresis of clutch operation |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN105143701B (en) |
| DE (2) | DE102014206477A1 (en) |
| WO (1) | WO2014173407A2 (en) |
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| CN108700139A (en) * | 2016-02-19 | 2018-10-23 | 舍弗勒技术股份两合公司 | Method for calculating slip power of a hybrid disconnect clutch |
| CN109058323A (en) * | 2017-05-31 | 2018-12-21 | 舍弗勒技术股份两合公司 | Method for calculating a setpoint position of a clutch actuator |
| CN109416089A (en) * | 2016-07-21 | 2019-03-01 | 舍弗勒技术股份两合公司 | Method for maintaining a pressure level of a hydraulic fluid in a hydraulic actuator device |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102015200981B4 (en) | 2015-01-22 | 2016-11-17 | Schaeffler Technologies AG & Co. KG | Method for controlling a mechanical power transmitted by a friction clutch device |
| DE102016203370A1 (en) | 2015-03-17 | 2016-09-22 | Schaeffler Technologies AG & Co. KG | Method for adapting a touch point of a clutch which is closed in the unactuated state |
| DE102018200745B3 (en) | 2018-01-17 | 2019-04-18 | Magna powertrain gmbh & co kg | METHOD FOR REGULATING THE RESETTING OF A POSITION-CONTROLLED CLUTCH UNIT, AND FOR THE PREPARATION OF THE TORQUE TRANSMISSION ARRANGEMENT |
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| DE102010012756A1 (en) * | 2009-04-17 | 2010-10-21 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | coupling parameters |
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| EP2542796B1 (en) | 2010-03-04 | 2014-04-09 | Schaeffler Technologies GmbH & Co. KG | Method for controlling a friction clutch and device therefor |
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- 2014-04-04 DE DE102014206477.5A patent/DE102014206477A1/en not_active Withdrawn
- 2014-04-04 CN CN201480023004.XA patent/CN105143701B/en active Active
- 2014-04-04 DE DE112014002172.5T patent/DE112014002172B4/en active Active
- 2014-04-04 WO PCT/DE2014/200154 patent/WO2014173407A2/en active Application Filing
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108700139A (en) * | 2016-02-19 | 2018-10-23 | 舍弗勒技术股份两合公司 | Method for calculating slip power of a hybrid disconnect clutch |
| CN108700139B (en) * | 2016-02-19 | 2020-12-01 | 舍弗勒技术股份两合公司 | Method for calculating slip power of a hybrid disconnect clutch |
| CN109416089A (en) * | 2016-07-21 | 2019-03-01 | 舍弗勒技术股份两合公司 | Method for maintaining a pressure level of a hydraulic fluid in a hydraulic actuator device |
| CN109416089B (en) * | 2016-07-21 | 2020-10-27 | 舍弗勒技术股份两合公司 | Method for maintaining a pressure level of a hydraulic fluid in a hydraulic actuator device |
| CN109058323A (en) * | 2017-05-31 | 2018-12-21 | 舍弗勒技术股份两合公司 | Method for calculating a setpoint position of a clutch actuator |
| CN109058323B (en) * | 2017-05-31 | 2022-01-07 | 舍弗勒技术股份两合公司 | Method for calculating a setpoint position of a clutch actuator |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112014002172A5 (en) | 2016-01-07 |
| CN105143701B (en) | 2017-10-03 |
| DE112014002172B4 (en) | 2022-11-03 |
| WO2014173407A2 (en) | 2014-10-30 |
| DE102014206477A1 (en) | 2014-10-30 |
| WO2014173407A3 (en) | 2015-08-20 |
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