CN106931157B - A kind of double-clutch speed changer shift control method for avoiding dual-clutch gear-shifting power cycle - Google Patents
A kind of double-clutch speed changer shift control method for avoiding dual-clutch gear-shifting power cycle Download PDFInfo
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- CN106931157B CN106931157B CN201710146896.8A CN201710146896A CN106931157B CN 106931157 B CN106931157 B CN 106931157B CN 201710146896 A CN201710146896 A CN 201710146896A CN 106931157 B CN106931157 B CN 106931157B
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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
- F16H61/04—Smoothing ratio shift
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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
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
- F16H63/50—Signals to an engine or motor
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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
- F16D2500/50—Problem to be solved by the control system
- F16D2500/502—Relating the clutch
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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
- F16D2500/70—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
- F16D2500/70406—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
- F16D2500/70—Details about the implementation of the control system
- F16D2500/704—Output parameters from the control unit; Target parameters to be controlled
- F16D2500/70452—Engine parameters
- F16D2500/70454—Engine speed
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
Abstract
The invention discloses a kind of double-clutch speed changer shift control methods for avoiding dual-clutch gear-shifting power cycle, it is characterised in that：When double-clutch automatic gearbox is shifted gears, by the Detaching and Lapping control of double clutch and the adjustment of rotational speed of engine, so as to which double clutch be avoided to generate gearshift power cycle, the gearshift power consumption of double clutch is reduced, reduce shift shock simultaneously, improve the smooth gear shifting of double-clutch speed changer.
Description
Technical field
The present invention relates to a kind of automobile automatic gear shift control method, specifically one kind avoids dual-clutch gear-shifting
The double-clutch speed changer shift control method of power cycle.
Background technology
Double-clutch automatic gearbox (Dual Clutch Transmission, DCT) is the basis based on manual transmission
On a kind of novel automatic transmission for developing, transmitted by using two clutches into action edge, first clutch
Transmit current gear when, second clutch can carry out change gear gear it is preset, when need complete current gear with changing
When entering the switching of gear, first clutch releases current gear, while second clutch engagement change gear, therefore DCT
Not only have the flexibility of manual transmission, but also the comfort with automatic transmission, without bright in entire gearshift procedure
Aobvious power interruption phenomenon, while response of shifting gears is fast, DCT is got the favour of people with its outstanding performance, rapid to promote and apply.
Architectural characteristic special DCT so that power loss reduces during gearshift, but due to there are during power cycle, clutch
Shift time is longer, and impact is smaller, but clutch abrasion is bigger, on the contrary, the shift time of clutch is shorter, conducive to clutch is improved
Device wear condition, impact is bigger, and smooth gear shifting is poorer, thus there are shift time during power cycle and shift shock as power
Irreconcilable conflict during handing-over.Therefore, power cycle phenomenon is also easy to produce in DCT shift processes, causes power loss, changes
Ride comfort is kept off to decline and shift clutch parts damages.
Invention content
The present invention proposes that one kind avoids dual-clutch gear-shifting power to avoid the shortcoming present in the above-mentioned prior art
The double-clutch speed changer shift control method of cycle, to pass through when double-clutch speed changer automatic transmission is shifted gears
The Detaching and Lapping control of double clutch and the adjustment of rotational speed of engine, avoid clutch from generating gearshift power cycle, reduce it is double from
The gearshift power consumption of clutch, while reduce shift shock, improve the smooth gear shifting of double-clutch speed changer.
The present invention to achieve the above object of the invention, adopts the following technical scheme that：
The present invention it is a kind of avoid dual-clutch gear-shifting power cycle double-clutch speed changer shift control method the characteristics of be
It carries out as follows：
Step 1, the normal pressure for reducing separation clutch make the driving disc spacing pressing of the separation clutch be in driven disc and detach
Critical condition, while increase the normal pressure of engagement clutch, the driving disc spacing pressing of the engagement clutch is made to be in driven disc and is engaged
Critical condition；
Step 2 gradually adjusts the separation clutch and the normal pressure for engaging clutch, while gradually adjusts and start
The rotating speed of machine, make the separation clutch driving disc spacing pressing and driven disc incrementally increase cunning rub, the driving disc spacing pressing for engaging clutch
It incrementally increases and engages with driven disc；
Step 3, when it is described separation clutch normal pressure fall to zero when, it is described separation clutch driving disc spacing pressing with it is driven
Disk is kept completely separate, and driving disc spacing pressing and the driven disc of the separation clutch are in completely sliding state of rubbing, the corresponding engagement clutch
Maintenance pressure of the normal pressure for the engagement clutch, the maintenance pressure for keeping the engagement clutch is constant, until described
The driving disc spacing pressing of engagement clutch is completely combined with driven disc；
Step 4, when it is described engagement clutch active disk rotating speed be equal to it is described engagement clutch driven disk rotating speed when, institute
The driving disc spacing pressing for stating engagement clutch is completely combined with driven disc, while continues to increase the normal pressure for engaging clutch to described
Until the rated value for engaging clutch engagement force.
The characteristics of automatic transmission shift control method for correcting of the present invention, lies also in,
Detached described in the step 2 adjusting of clutch and the normal pressure for engaging clutch in accordance with the following methods into
Row：
According to the requirement of gearshift response time, gradually reduce the normal pressure of the separation clutch, while incrementally increase institute
The normal pressure of engagement clutch is stated, and makes to engage the friction torque T of clutch described in shift processc2Meet formula (1)：
In formula (1)：i1For current gear gearratio；i2To change to gear gearratio；Tcut1Transmission to detach clutch turns
Square；R is tire radius；M is tire quality；jBFor clutch driven plate rear end thereof inertia summation；jRFor vehicle wheel rotation inertia.
The adjusting of engine speed described in the step 2 carries out in accordance with the following methods：
Adjust the engine speed, make the engine speed be more than it is described separation clutch driven plate rotating speed with it is described
Engage the maximum value between clutch driven plate rotating speed.
The rated value of clutch engagement force is engaged described in the step 4 to transmit design during engagement clutch normal work
Normal pressure needed for torque.
Compared with the prior art, the present invention has the beneficial effect that：
1st, the present invention carries out separation and the Engagement Control of double clutch by adjusting the normal pressure of double clutch, effectively reduces
Shift shock improves the smooth gear shifting of double-clutch speed changer.
2nd, the present invention, by the adjustment of rotational speed to engine, avoids clutch in double clutch separation, cohesive process
Gearshift power cycle is generated during gearshift, reduces the gearshift power consumption of double clutch, while avoids double clutch shifting components
Damage extends the service life of double clutch shifting components.
3rd, the present invention is improved double clutch and is changed by the Detaching and Lapping control of double clutch and the adjustment of rotational speed of engine
Performance is kept off, without changing vehicle hardware system, it is only necessary to increase this control method pair in automatic transmission electronic control unit
The software program answered, operability is strong, and is applicable to the vehicle of equipment different type double-clutch automatic gearbox, the scope of application
Extensively.
Description of the drawings
Fig. 1 is the dual clutch transmission structure schematic diagram of the embodiment of the present invention；
Fig. 2 is that two clutch normal pressures adjust schematic diagram in double-clutch speed changer shift process of the invention；
Fig. 3 is that engine speed adjusts schematic diagram in double-clutch speed changer shift process of the invention.
Specific embodiment
In the present embodiment, a kind of double-clutch speed changer shift control method for avoiding dual-clutch gear-shifting power cycle is
When double-clutch automatic gearbox is shifted gears, by the Detaching and Lapping control of double clutch and the adjustment of rotational speed of engine, keep away
Exempt from double clutch and generate gearshift power cycle, reduce the gearshift power consumption of double clutch, while reduce shift shock, improve double
The smooth gear shifting of clutch speed changer.It is to carry out as follows specifically refering to Fig. 1-Fig. 3：
Step 1, double-clutch speed changer are completed power by two clutches and are transmitted and gearratio variation, definition current gear
Under into the clutch that action edge transmits be separation clutch, need to change to clutch that gear is transmitted into action edge to engage clutch
Device, before transforming gear is carried out, it is necessary first to eliminate idle stroke of the separation clutch with engaging clutch, i.e.,：Reduce separation from
The normal pressure of clutch is in driving disc spacing pressing and the driven disc of the separation clutch and detaches critical condition, at the same increase engage from
The normal pressure of clutch makes the driving disc spacing pressing of the engagement clutch be in driven disc and engages critical condition, eliminates separation clutch
Idle stroke with engaging clutch makes separation clutch reach the critical condition of power handing-over with engaging clutch, to shorten
The shift time of dual-clutch transmission；
Step 2, when carrying out transforming gear, in order to shorten shift time, improve smooth gear shifting, avoid power interruption,
Transmitting the separation clutch of current gear power needs to gradually reduce power transmission, transmits the engagement clutch of change gear power
It needs to incrementally increase power transmission, separation clutch needs to join into action edge, needs gradually to adjust separation with engaging clutch
Clutch and the normal pressure for engaging clutch make the driving disc spacing pressing of separation clutch and driven disc incrementally increase cunning and rub, engage clutch
The driving disc spacing pressing of device is incrementally increased with driven disc to be engaged；Meanwhile in order to avoid separation clutch generates work(between clutch with engaging
Rate recycles, and needs gradually to adjust the rotating speed of engine；
Specifically, the adjusting of normal pressure of the separation clutch with engaging clutch carries out in accordance with the following methods：
The shock extent of evaluation smooth gear shifting during gearshift is illustrated first：
Shock extent in Vehicle Shifting is often represented with the first derivative of vehicle acceleration, since shift process is shorter,
Speed changes unobvious, therefore rolling resistance moment and air drag square in the process can be considered constant, can obtain separation clutch
It is gradually sliding rub, engage clutch gradually under engagement state shock extent expression formula, wherein, j1To adjust under engine speed conditions
Shock extent when the equal inactivity of two clutches recycles, j2For separation clutch, there are shock extents during power cycle.
In formula (1), formula (2)：i1For current gear gearratio；i2To change to gear gearratio；Tc1For separation clutch
Moment of friction；Tc2To engage the moment of friction of clutch；R is tire radius；M is tire quality；jBAfter clutch driven plate
Hold rotary inertia summation；jRFor vehicle wheel rotation inertia.
By above-mentioned shock extent expression formula it is found that the smooth gear shifting of double-clutch speed changer is mainly turned by separation clutch friction
Square change rateEngage clutch friction torque rate of changeAnd it is influenced with the presence or absence of factors such as power cycles.
Detach clutch friction torque rate of change Tc1, engagement clutch friction torque rate of change Tc2Expression formula it is as follows：
In formula (3), formula (4)：For the change rate for detaching clutch, engaging clutch engagement force；Rc、rcRespectively
Big path for clutch disk；μ is the friction coefficient of clutch disk.
By formula (3), formula (4) it is found thatTogetherFor proportional relationship, and due to detaching clutch in shift process
Device engaging force continuously decreases, and engagement clutch engagement force gradually rises, thereforeFor negative value,For positive value.
(1) when all power cycle is not present in two clutches, by (1) first expression formula of formula it is found that by adjusting two clutches
The change rate of device engaging force can realize that shock extent is 0 in theory.
(2) when detaching clutch there are power cycle, when engagement clutch forward direction transmits torque, from formula (2)Two term system numerical symbols are opposite；By gearshift real process it is found that reducing since two clutch normal pressures, one side increases a side,Itself there is opposite positive-negative relationship, therefore can not theoretically be engaged according to formula (1) expression formula by adjusting two clutches
Power size is realized Two are cancelled out each other, and shift shock are made to be reduced to 0 in theory.MeanwhileTwo are derivative term,
The change rate of physical quantity itself is reflected, transformation period is longer, its gentler value of variation is smaller, and transformation period is shorter, changes more
Its fierce value is bigger.Since there are power cycles, it is impossible to which by adjusting clutch engagement force by this two eliminations, therefore there are power
The clutch gear-shift time is longer during cycle, and impact is smaller, but clutch abrasion is bigger；On the contrary, shift time is shorter, impact is got over
Greatly, but be conducive to improve clutch abrasion situation.
Accordingly, there exist shift shock degree during power cycle and shift time (clutch abrasion) as contradiction amount, it is
The contradiction reconciled between shift time and shift shock need to establish the system optimization Controlling model based on principle of minimum, but control
Process processed is extremely complex.And during inactivity cycle gearshift, due toTwo can mutually offset and remove, therefore there is no shift times
Contradiction between shift shock, shifting gears under arbitrary shift time can realize that shock extent is 0, therefore double-clutch speed changer is shifted gears
When should avoid the generation of power cycle.
According to gearshift the response time requirement, gradually reduce separation clutch normal pressure, while incrementally increase engagement from
The normal pressure of clutch, and make to engage the friction torque T of clutch in shift processc2Meet formula (5), you can ensure that two clutches change
Shock extent is 0 during gear power joins sliding rub.
Wherein, the transmission torque T of clutch is detachedcut1Expression formula it is as follows：
In formula (6)：For motor torque change rate；jAFor clutch driving plate and its anterior member rotary inertia summation；
TrTo include the running resistance square including rolling resistance moment and air drag square.
By analyze above it is found that double-clutch speed changer in shift process there are during power cycle, it is difficult to which it is flat to solve gearshift
Therefore pliable problem, gearshift power cycle must be eliminated in double-clutch speed changer in shift process, turned by adjusting engine
Inactivity recycles during achievable two clutch gear-shifts of speed.
When clutch forward direction transmits moment of friction, clutch driving plate rotating speed has to be larger than driven disk rotating speed；If clutch
Driven disk rotating speed is higher than active disk rotating speed, then moment of friction direction of transfer becomes as by driven disc to driving disc spacing pressing.Moment of friction it is anti-
Power cycle can be caused to generate to transmitting.In shift process, if clutch driving plate rotating speed is less than separation clutch or engagement
The driven disk rotating speed of clutch, then double clutch is in the presence of gearshift power cycle, consumption of engine power, the stress evil for component of shifting gears
Change, and smooth gear shifting is difficult to solve, and in order to avoid the gearshift power cycle of double-clutch speed changer, needs to make clutch driving plate
Rotating speed is more than separation clutch or engages the driven disk rotating speed of clutch, since clutch driving plate is straight with engine output shaft
Even, then clutch driving plate rotating speed is identical with engine speed, and therefore, the adjusting of engine speed carries out in accordance with the following methods：
Engine speed is adjusted, engine speed is made to be more than separation clutch driven plate rotating speed with engaging clutch driven plate
Maximum value between rotating speed.
Step 3, when the normal pressure for detaching clutch falls to zero, detach the handed down from the older generations of the family of the driving disc spacing pressing of clutch and driven disc
The moment of friction passed is zero, and the driving disc spacing pressing and driven disc for detaching clutch are kept completely separate, detach the driving disc spacing pressing of clutch with it is driven
Disk is in completely sliding state of rubbing, and the normal pressure of corresponding engagement clutch is to engage the maintenance pressure of clutch, engages clutch at this time
The driving disc spacing pressing of device is not fully engaged also with driven disc, in order to reduce shift shock, is improved smooth gear shifting, is remained engaged with clutch
Maintenance pressure it is constant, until engagement clutch driving disc spacing pressing be completely combined with driven disc；
Step 4, when engage clutch active disk rotating speed be equal to engagement clutch driven disk rotating speed when, engage clutch
Driving disc spacing pressing be completely combined with driven disc, at this point, engagement clutch maintenance pressure be only ensure transmit changed to gear torque
Minimum normal pressure, if engine output torque fluctuation, vehicle meet running resistance torque variation, engage clutch and will appear
Slipping phenomenon can not adapt to transmit the variation of torque, the adaptability changed to improve engagement clutch to transmitting torque, simultaneously
Until needing to continue the normal pressure to the rated value of engagement clutch engagement force that increase engages clutch.
When transmission for vehicles designs, need to carry out speed changer according to engine parameter, transmission ratio, whole-car parameters
Each gear transmits torque calculation, and according to needed for each gear transmits torque calculation speed changer different drive ratios clutch positive pressure
Power on this basis designs the normal pressure of clutch certain redundancy, it is ensured that in vehicle parameter, driving cycle, drives behaviour
Clutch energy reliable delivery motor torque, therefore the positive pressure of clutch needed for speed changer different drive ratios during vertical operating mode variation
The calculated value of power adds pressure design redundancy value, and normal pressure needed for design torque is transmitted when as clutch works normally, therefore,
The rated value of clutch engagement force is engaged to transmit normal pressure needed for design torque during engagement clutch normal work.
Embodiment：The present embodiment changes the fast double-clutch automatic gearbox of certain model 7 using the control method of the present invention
Gear control, it is specific to control process as follows：
Fig. 1 is the fast dual clutch transmission structure schematic diagram of certain model 7, chooses a gear and two grades carry out gearshift control, to other
Gear does not do detailed expression.C1, C2 represent clutch 1 and clutch 2 respectively in Fig. 1, then during one grade of two grades of change,
Clutch 1 is separation clutch, and clutch 2 is engagement clutch；G1~G7 represents gears at different levels, and provides gearratio iabFor tooth
Take turns gearratio (a=1~7 between Ga, Gb；B=1~7), then one keep off gearratio i1For i12×i37, two gear gearratio i2For i45
×i67。
If the original state of double-clutch speed changer is combined for clutch C1, clutch C2 separation, and with a gear job.Now by
One gear change, two gear, then two gear synchronizers combine in advance (does not represent synchronizer, shown state is one or two gear synchronizers in Fig. 1
The state combined), clutch C2 is still detached at this time；Shift process continues, and clutch C2 pressing forces gradually increase, clutch C1
Pressing force is gradually reduced, and when clutch C1 is kept completely separate, clutch C2 detaches a gear synchronizer after being completely combined, shifted gears
Into.
In the shift process of double-clutch speed changer, each shift clutch is there are three kinds of states, i.e.,：Separation, cunning are rubbed
(conjunction) and engagement.Separation and the sliding two states that rub can describe its torque with same expression formula from the point of view of mathematical notation, difference
Place is only that under discrete state that clutch engagement force is 0, can be considered that the cunning for being not loaded with engaging force is rubbed state.It is it can be considered that every
There is only two states for a shift clutch：Cunning rubs, detaches, therefore there are following four shapes for the shift process of double-clutch speed changer
State, i.e.,：
(a) C1 engages C2 cunnings and rubs；(b) C1 slides C2 cunnings of rubbing and rubs；(c) C1 slides the C2 engagements that rub；(d) C1 engages C2 engagements obviously,
(d) state is untenable, therefore there is only (a), (b), (c) three kinds of states in the shift process of double-clutch speed changer.
Referring to Fig.2, curve ordinate is the normal pressure F of clutch, wherein solid line is C1 normal pressures, and dotted line is C2 positive pressures
Power, then the adjustment of two clutch normal pressures is divided into following several stages in double-clutch speed changer shift process：
1st, 0~t0 stages
Double-clutch speed changer is in (a) state, due to i1More than i2, then the driven disk rotating speeds of clutch C1 are more than clutch C2
Driven disk rotating speed, therefore power cycle phenomenon is not present in C2.If there are power cycle, the transmission torque T of clutch C2 by C1cut1For
Negative value, but its initial equilibrium state is just, during which necessary 0 point of mistake, the condition lance always remained engaged with C1 under this state if it is by 0 point
Shield, therefore power cycle phenomenon is not present in C1, C2 under current state.
2nd, t0~t3 stages
This stage is the critical stage of double-clutch speed changer gearshift control, and can be divided into following several stages：
(1) t0~t1 stages
Double-clutch speed changer is in (a) state, and clutch C1 normal pressures rapidly drop to critical value, and clutch C1, which is in, to be divided
From critical condition, the friction torque that C1 is transmitted at this time is equal to Tcut1, clutch C2 normal pressures are climbed to critical value, clutch
Device C2 is in engagement critical condition.
(2) t1~t2 stages
Double-clutch speed changer is in (b) state, and C1 actives disk rotating speed, C2 active disk rotating speeds are all equal to when current state is initial
Driven disk rotating speeds of C1 and more than the driven disk rotating speeds of C2.There are C1 actives disk rotating speed, C2 actives disk rotating speed at the end of current state all etc.
In the driven disk rotating speeds of C2 and less than the driven disk rotating speeds of C1.
Clutch driven plate rotating speed becomes if higher than moment of friction direction of transfer if clutch driving plate rotating speed as by driven end
To drive end, then power cycle can occur, since the driven disk rotating speeds of C2 are consistently less than the driven disk rotating speeds of C1, therefore there is no C1 is idle
Rate recycles the operating mode of C2 power cycles；If all there are the operating modes of power cycle by C1, C2, being equivalent to adjusting engine speed makes in real time
Speed is counter to drag engine rotation, it is clear that is unreasonable；Therefore at t1~t2 sections, if the adjustment of rotational speed without engine controls,
Therefore C1, must take the method that engine speed adjusts to carry out the gearshift control of clutch C1 and C2 there are power cycle operating mode,
It can effectively avoid C1 and generate power cycle, concrete measure refers to Fig. 3, and curve ordinate is rotating speed n, and wherein solid line is C1 driven discs
Rotating speed, long dotted line are the driven disk rotating speeds of C2, and short dash line is engine speed, and specific adjusting method is as follows：
Clutch C1 normal pressures can need to be according to C1 normal pressures regulation and control side according to set sliding friction time linear decline, clutch C2
Formula is acted, i.e. the friction torque T in t2 time point clutches C2c2Meeting formula (5) constraint, remaining linearly increases, and
Ensure to be all higher than the maximum value between the driven disk rotating speed of clutch C1 and C2 in t1~t2 sections of intrinsic motivation rotating speeds.
(3) t2~t3 stages
Double-clutch speed changer is in (b) state, and clutch C1 normal pressures have fallen to 0, control clutch C2 normal pressure dimensions
It holds constant, maintains clutch C2 normal pressures constant until C2 is fully engaged, in t2~t3 sections, shock extent connects during can making this
0 is bordering on, almost without shift shock.
3rd, t3~t4 stages
Double-clutch speed changer is in (c) state, and clutch C2 is fully engaged, and increases its normal pressure to clutch rapidly and engages
The rated value of power.
So far, 7 fast double-clutch speed changers are completed to be controlled by the gearshift of the double clutch of one grade of two grades of change, are avoided
Double clutch generates power cycle in shift process, improves smooth gear shifting, reduces the damage of gearshift component.
Therefore, dual-clutch gear-shifting control method using the present invention carries out separation and the Engagement Control of double clutch, can
Shift shock is effectively reduced, improves the smooth gear shifting of double-clutch speed changer, generation gearshift power during clutch gear-shift is avoided to follow
Ring, reduces the gearshift power consumption of double clutch, while avoids the damage of double clutch shifting components, extends double clutch shifting components
Service life.
Claims (1)
1. a kind of double-clutch speed changer shift control method for avoiding dual-clutch gear-shifting power cycle, it is characterized in that by following step
It is rapid to carry out：
Step 1, the normal pressure for reducing separation clutch, the driving disc spacing pressing for making the separation clutch are critical in detaching with driven disc
State, while increase the normal pressure of engagement clutch, the driving disc spacing pressing for making the engagement clutch is critical in engaging with driven disc
State；
Step 2 gradually adjusts the separation clutch and the normal pressure for engaging clutch, while gradually adjusts engine
Rotating speed, make the separation clutch driving disc spacing pressing and driven disc incrementally increase it is sliding rub, the driving disc spacing pressing for engaging clutch and from
Moving plate incrementally increases engagement：
The separation clutch carries out in accordance with the following methods with the adjusting of the normal pressure for engaging clutch：
According to the requirement of gearshift response time, gradually reduce the normal pressure of the separation clutch, while incrementally increase described connect
The normal pressure of clutch is closed, and makes to engage the friction torque T of clutch described in shift processc2Meet formula (1)：
In formula (1)：i1For current gear gearratio；i2To change to gear gearratio；Tcut1To detach the transmission torque of clutch；R
For tire radius；M is tire quality；jBFor clutch driven plate rear end thereof inertia summation；jRFor vehicle wheel rotation inertia；
The adjusting of the engine speed carries out in accordance with the following methods：
The engine speed is adjusted, the engine speed is made to be more than the separation clutch driven plate rotating speed and the engagement
Maximum value between clutch driven plate rotating speed；
Step 3, when it is described separation clutch normal pressure fall to zero when, it is described separation clutch driving disc spacing pressing and driven disc it is complete
Fully separating, driving disc spacing pressing and the driven disc of the separation clutch are in completely sliding state of rubbing, and the corresponding engagement clutch is just
Maintenance pressure of the pressure for the engagement clutch, the maintenance pressure for keeping the engagement clutch is constant, until the engagement
The driving disc spacing pressing of clutch is completely combined with driven disc；
Step 4, when it is described engagement clutch active disk rotating speed be equal to it is described engagement clutch driven disk rotating speed when, it is described to connect
The driving disc spacing pressing for closing clutch is completely combined with driven disc, while continues to increase the normal pressure for engaging clutch to the engagement
Until the rated value of clutch engagement force；Wherein, the rated value of the engagement clutch engagement force is the engagement normal work of clutch
Normal pressure needed for design torque is transmitted when making.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710146896.8A CN106931157B (en) | 2017-03-13 | 2017-03-13 | A kind of double-clutch speed changer shift control method for avoiding dual-clutch gear-shifting power cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710146896.8A CN106931157B (en) | 2017-03-13 | 2017-03-13 | A kind of double-clutch speed changer shift control method for avoiding dual-clutch gear-shifting power cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106931157A CN106931157A (en) | 2017-07-07 |
| CN106931157B true CN106931157B (en) | 2018-07-03 |
Family
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| CN111572525B (en) * | 2020-05-28 | 2021-05-04 | 合肥工业大学 | Gear-shifting quality optimization-based power gear-shifting transmission downshift control method |
| CN114198430B (en) * | 2021-12-20 | 2024-02-20 | 潍柴动力股份有限公司 | Clutch engagement method, device, equipment and medium |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104049650A (en) * | 2014-05-27 | 2014-09-17 | 合肥工业大学 | Wet-type DCT clutch temperature control system based on fuzzy control and control method thereof |
| CN105840808A (en) * | 2016-04-26 | 2016-08-10 | 中国第汽车股份有限公司 | Gear-shifting coordination control method for wet double-clutch automatic speed changer |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104049650A (en) * | 2014-05-27 | 2014-09-17 | 合肥工业大学 | Wet-type DCT clutch temperature control system based on fuzzy control and control method thereof |
| CN105840808A (en) * | 2016-04-26 | 2016-08-10 | 中国第汽车股份有限公司 | Gear-shifting coordination control method for wet double-clutch automatic speed changer |
Non-Patent Citations (3)
| Title |
|---|
| 双湿式离合变速箱升挡过程循环功率抑制方法探究;曲思宇等;《机械传动》;20161031;第40卷(第10期);第54-69页、图2 * |
| 双离合自动变速器顺序换挡控制过程研究;陈伟等;《合肥工业大学学报(自然科学版)》;20091130;第32卷;全文 * |
| 联合油压控制的DCT升挡控制策略研究;马彪等;《重庆大学学报》;20150831;第38卷(第4期);全文 * |
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