CN103148207A - Method for controlling clutch switch process of dual-clutch transmission - Google Patents

Method for controlling clutch switch process of dual-clutch transmission Download PDF

Info

Publication number
CN103148207A
CN103148207A CN2013100559139A CN201310055913A CN103148207A CN 103148207 A CN103148207 A CN 103148207A CN 2013100559139 A CN2013100559139 A CN 2013100559139A CN 201310055913 A CN201310055913 A CN 201310055913A CN 103148207 A CN103148207 A CN 103148207A
Authority
CN
China
Prior art keywords
clutch
speed
input
gear
speed ratio
Prior art date
Application number
CN2013100559139A
Other languages
Chinese (zh)
Inventor
银联作
胡成帅
朱高华
孙芬
路红芳
Original Assignee
重庆青山工业有限责任公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 重庆青山工业有限责任公司 filed Critical 重庆青山工业有限责任公司
Priority to CN2013100559139A priority Critical patent/CN103148207A/en
Publication of CN103148207A publication Critical patent/CN103148207A/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/006Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control 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
    • F16H61/68Control 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 specially adapted for stepped gearings
    • F16H61/684Control 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 specially adapted for stepped gearings without interruption of drive
    • F16H61/688Control 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 specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches

Abstract

The invention relates to a control method of a transmission, in particular to a method for controlling a clutch switch process of a dual-clutch transmission, and aims to provide a method for controlling a clutch switch process of a dual-clutch transmission, which is allowed to be more simplified and calibrated. The method comprises the following steps: determining a target gear speed ratio; determining an input clutch torque of a preorder clutch; detecting input rotating speed of the preorder clutch; detecting target rotating speed of a subsequent clutch; calculating a current speed ratio by using the detected input rotating speed to divide the detected output rotating speed; determining a target speed ratio according to calibrated data, wherein the calibrated data depends on the gear type, the drive gear, the input rotating speed, the input torque and the current temperature of the clutch; calculating speed ratio error; and using the value of the speed ratio error as a control objective, and continuously and unceasingly revising clutch pressure and engine torque demands according to the level of the error in the closed-loop control, so as to enable an actual speed ratio to follow a target ratio curve.

Description

The clutch method for handover control of double-clutch speed changer

Technical field

The present invention relates to a kind of controlling method of speed changer, particularly relate to a kind of controlling method of the clutch handoff procedure for double-clutch speed changer.

Background technique

Speed changer is a very important part in modern transmission system, in order to improve the efficient of transmission system, in the recent period since, people have carried out considerable R﹠D work.Be accompanied by the development of modern control technology, wherein the development of quite a few all launches round double-clutch speed changer.The engage a gear of double-clutch speed changer is similar to common manual transmission.Gear in each gear train is arranged on separately axle and can rotates freely around axle, and the gear side is provided with synchronizer, and synchronizer can optionally mesh the gear of different gears, double-clutch speed changer.In order to realize automatic speed changing, the gear shift of each gear train is moved synchronizer by certain actuator and is realized.Reverse gearset comprises an input shaft gear, a counter shaft gear and an intermediate gear that arranges between them, thereby realizes counter shaft gear counter-rotating and then realize the counter-rotating of output shaft and reverse gear.Although these double-clutch speed changers have overcome the shortcoming of some conventional transmissions and new type auto speed changer, but control and adjusting to the self-shifting double-clutch speed changer are the things of a complexity, and the desired comfortable target of passenger did not reach yet in the past.at present, in the regulating and controlling field to double clutch, a large amount of patent applications is arranged also, for example U.S. BorgWarner Inc is respectively CN1530570A at the publication number that China proposes, CN1526976A, CN1523253A, the open time is three applications for a patent for invention of 2004, Shanghai Automotive Transmission Co is CN101943228A at the publication number that China proposes, open day is on January 12nd, 2011, denomination of invention is the clutch closed loop control system of two clutch gearboxes and the application for a patent for invention of controlling method thereof, also having in addition the applicant is 201210082148.5 at the application number that proposes before, application publication number is CN102606724A, Shen Qing Publication day is the Chinese invention patent application on July 25th, 2012.In addition, domestic also have the people to deliver relevant paper at the double-clutch speed changer control field, title as Southwestern University Li Jun China is the master thesis of " dual-clutch transmission control system design and research ", this piece paper elaborates the control system of dual-clutch transmission, and this piece paper can retrieve in the Baidu library.It is worth mentioning that, in the approaching prior art of the control technique in double-clutch speed changer, the control system that the AMT automatic transmission adopts and controlling method are all to be worth using for reference.

In the control field of double-clutch speed changer, be a very important field to the control of clutch handoff procedure, for speed changer is controlled and operation in good time, make each gear shift level and smooth and effectively, still also have a large amount of things to do.In the clutch switch step, guarantee that it is very crucial that output torque is tried one's best smooth-going, because it is from a gear switch to another gear.In present existing controlling method, some control engine speed is followed a linear goal, the target of the control rate that also has migration curve to an approximately linear.These two kinds of methods can produce shift quality preferably, and two kinds of methods are all very sensitive to the variation of moment of torsion, but they need to do more staking-out work.As application number be 200410005885.0, notice of authorization number is a kind of disclosed method of controlling double clutch transmission device of Chinese invention patent on November 19th, 2008 for CN100434768C, notice of authorization day, the method comprises a linear goal curve, the major defect of this method is, in the identification that relies on from the transfer process state that enters out state, and can allow speed become linearity before closed loop control activates.Application number is 200380109880.6 in addition, notice of authorization number is the Chinese invention patent on July 9th, 2008 for CN100400937C, notice of authorization day, a kind of gear-shifting control method of automatic double clutch gearbox is disclosed, the method has comprised based on the calculating to the multimode target of the physical property of controlled system, even now should obtain a result preferably to the definite of target, but is difficult to revise and optimize in the practice of vehicle calibration.

Summary of the invention

The technical problem to be solved in the present invention is to provide a kind of clutch method for handover control that allows the double-clutch speed changer of the demarcation more simplified.

The clutch method for handover control of double-clutch speed changer of the present invention, in described double-clutch speed changer, the clutch of clutch switching front transfer moment of torsion is front sequence clutch, and another is follow-up clutch, and it comprises the following steps:

(1) determine the target gear ratios;

(2) determine the input torque of front sequence clutch;

(3) detect the input speed of front sequence clutch;

(4) detect the rotating speed of target of follow-up clutch;

(5) calculate current speed ratio with the input speed that detects divided by the output speed that detects;

(6) determine goals ratio according to nominal data, nominal data depends on shift type, drives gear, input speed, input torque and current clutch temp;

(7) deduct current speed ratio with goals ratio and calculate current speed ratio error;

(8) take the value of speed ratio error as controlling target, adopt the PID closed loop control successively to revise clutch moment of torque and Engine torque request, make actual speed ratio follow the goals ratio curve, the parameter of PID controller depends on shift type, speed ratio error, drives gear, input torque and current clutch temp, accelerator open degree, output speed, braking pedal situation.

The clutch method for handover control of double-clutch speed changer of the present invention, it further comprises following steps:

(1) determine goals ratio with the target deadline of completing gear shift;

(2) time division section within the object time, three time phase T1, T2 in control and T3.

The clutch method for handover control of double-clutch speed changer of the present invention, it further comprises following steps:

(1) the goals ratio increment of regulation T1;

(2) the low closed loop gain in regulation T1.

The clutch method for handover control of double-clutch speed changer of the present invention, it further comprises following steps:

(1) the goals ratio incremental raio T1 of regulation T3 and T2's is lower.

The clutch method for handover control difference from prior art of double-clutch speed changer of the present invention is that the target of the clutch method for handover control of double-clutch speed changer of the present invention calculates and the variation of input speed independence mutually, also independent mutually with the rotating speed difference size of the input and output of clutch, so the clutch method for handover control of double-clutch speed changer of the present invention allows the demarcation more simplified.

To be divided into three time phases the object time in the clutch method for handover control of double-clutch speed changer of the present invention, and be all in order to strengthen the stability of control in T1 stage and T3 stage respective specified target slope.

Be described further below in conjunction with the clutch method for handover control of accompanying drawing to double-clutch speed changer of the present invention.

Description of drawings

Fig. 1 is the structural representation of the double-clutch speed changer can the clutch method for handover control by double-clutch speed changer of the present invention controlled;

Fig. 2 is the structural representation of double-clutch speed changer hydraulic system;

Fig. 3 is the flow chart of the clutch method for handover control of double-clutch speed changer of the present invention;

Fig. 4 is the speed ratio plotted curve that upgrades;

Fig. 5 is the speed ratio plotted curve that lowers category.

Embodiment

Understand the present invention in order to be more convenient for, this first to the machinery of double-clutch speed changer of the prior art consist of, the Hydraulic system and control system explains.

Consist of except can be referring to the description in the file of pointing out in background technique about the machinery of double-clutch speed changer, can also be 200910260370.8 at the application number that proposes before referring to the applicant, application publication number is CN101737462A, Shen Qing Publication day to be the Chinese invention patent application on June 16th, 2010, also can be referring to Fig. 1.Double-clutch speed changer as shown in Figure 1, comprise two clutches, be first clutch 11 and second clutch 12, the even number shelves countershaft 14, jack shaft 15 and the reversing auxiliary shaft 16 that also comprise input shaft 110, odd number shelves countershaft 13, be arranged in parallel with odd number shelves countershaft 13, also comprise a plurality of synchronizers, i.e. the first synchronizer 17, the second synchronizer 18 and the 3rd synchronizer 19.Double-clutch speed changer by selectable speed ratio transmission from the moment of torsion of motor to output shaft, until on wheel.Double-clutch speed changer transmits moment of torsion from motor on odd number shelves countershaft 13 or even number shelves countershaft 14 by first clutch 11 or second clutch 12.Gear on odd number shelves countershaft 13 and even number shelves countershaft 14 all with jack shaft 15 on the gear constant engagement.Odd number shelves countershaft 13 and even number shelves countershaft 14 1 straight through the gear transmission on jack shaft 15 to wheel.Odd number shelves countershaft 13 can be in transmission connection with jack shaft 15 by overrunning clutch 20 and the 3rd synchronizer 19, even number shelves countershaft 14 when the first synchronizer 17 or the second synchronizer 18 hang up shifting gear and jack shaft 15 be in transmission connection.If one of odd number shelves countershaft 13 and even number shelves countershaft 14 are transmitting moment of torsion to jack shaft 15, and there is gear to be hung up on them, so can be by reducing the moment of torsion on front sequence clutch until sliding generations that rub, the moment of torsion that also increases simultaneously on follow-up clutch realize gear switch, before the preorder clutch finger clutch here switches, just at that clutch of transmitting torque, it also can be called as the active service clutch, and another is follow-up clutch.

When odd number shelves countershaft 13 just provides moment of torsion to jack shaft 15 by first clutch 11, and second clutch 12 is not when engaging, and the target gear is on the gear of even number shelves countershaft 14, and gear need to be selected.This generic operation is called as gear to be selected, and also can be called pre-engage a gear, because it is not in the situation that affect vehicle operating and in advance gear had been hung up before switch clutch.

Therefore, an important link is exactly to realize pre-hung or the excision of gear by the first synchronizer 17, the second synchronizer 18 or the 3rd synchronizer 19 in handoff procedure.In double-clutch speed changer as shown in fig. 1,5 synchronizers are arranged in fact, be respectively the second synchronizer 18 and the 3rd synchronizer 19 of paired setting, and first an independent synchronizer 17 that switches between forward gears and reverse gear.The second synchronizer 18 and the 3rd synchronizer 19 are synchronizers of bi-directional drive, namely when from the centre left or can hang up the gear on the left side or the right when moving right.As for the first synchronizer 17 as shown in Fig. 1 optimal way, moving to right can engage a gear, and when moving to left invalid (namely hanging neutral).

The control of speaking of within the present invention, general idea refers to electronic control component.Electronic control component itself has surpassed outside scope described in the invention.In any case, it need to manage control logic, provides needed voltage, signal, hydraulic pressure that double-clutch speed changer is operated.No matter be that clutch switches, or the gear selection, all need each clutch and each synchronizer are controlled.In order to realize controlling, change control signal into the control result, need hydraulic system to carry out, hydraulic system can be that 200910249994.X, application publication number are CN101709777A, Shen Qing Publication day to be the Chinese invention patent application on May 19th, 2010 at the application number that proposes before referring to the applicant, also can be referring to hydraulic system as shown in Figure 2.As shown in Figure 2, the first gear is selected control solenoid valve 22 and the second gear to select to control solenoid valve 23 and is preferably PWM-type (PWM).The PWM-type solenoid valve can provide a variable pressure by send pulse signal to solenoid valve.This solenoid valve is a kind of low-cost mode that can realize that variable pressure is controlled.The first gear select to be controlled the oil pressure that solenoid valve 22 and the second gear select to control solenoid valve 23 and is provided by main pressure regulator valve 28, main pressure regulator valve 28 outputs be main oil pressure, and the oil of main pressure regulator valve 28 is provided by pump 29.By the variable pressure solenoid valve, the main oil pressure of main pressure regulator valve 28 outputs can be in minimum to output changeably between maximum.Two variable pressure solenoid valves are arranged in Fig. 2, i.e. the first variable pressure solenoid valve 210 and the second variable pressure solenoid valve 211, they are used for respectively controlling by first clutch actuator 213 and second clutch actuator 212 moment of torsion that each clutches transmit.The purpose that main oil pressure is controlled is exactly to make main oil pressure all the time higher than the request pressure of the first variable pressure solenoid valve 210 and the second variable pressure solenoid valve 211.Similarly, main oil pressure will select control solenoid valve 22 and the second gear to select the request pressure of control solenoid valve 23 also very important higher than the first gear.The first gear select to control solenoid valve 22 and the second gear select to control solenoid valve 23 according to the relative pressure state selectivity of the first variable pressure solenoid valve 210 and the second variable pressure solenoid valve 211 provide hydraulic pressure to gear selecting sequence valve 24, gear selecting sequence valve 24 provides a hydraulic coupling to select piston 25, third gear to select piston 26, the first gears to select pistons 27, the second gear to select piston 25, third gear to select the first synchronizer 17, the second synchronizer 18 in the mobile corresponding diagram 1 respectively of piston 26, the movement of the 3rd synchronizer 19 to the second gear.

The clutch method for handover control of double-clutch speed changer of the present invention mainly embodies from flow chart shown in Figure 3, from initial entry block 31, having determined a target gear when the logic of transmission control unit and hardware changes when having occured, speed changer is necessary for the clutch switching and prepares, so enter entry block 32, determine the type of gear shift request in entry block 32, (speed ratio of target gear is determined by speed changer hardware to obtain the speed ratio of target gear, such as 1 grade of speed ratio, 2 grades of speed ratios, 3 grades of speed ratios, 4 grades of speed ratios, 5 grades of speed ratios etc.It is 1 grade as the target gear, the target gear ratios is exactly the speed ratio of 1 grade so), then enter entry block 33, (input torque of front sequence clutch namely motor is delivered to the moment of torsion of front sequence clutch to the input torque that entry block 33 is determined from motor for the moment of torsion of clutch switches.The value of this moment of torsion is to send to control system of speed variator by engine control system by the CAN communication, the value that then obtains through calculating).In entry block 34, the input speed of sequence clutch before determining (input speed of front sequence clutch is the rotating speed of motor namely, the value of this rotating speed be exactly this moment engine control system send to the engine speed of control system of speed variator by the CAN communication).In entry block 35, target velocity determines that according to the input speed of the follow-up clutch that detects (then rotating speed of target can calculate by the speed probe collection on speed changer and obtain, if the target gear is 1,3,5 grade, the rotating speed of target of so follow-up clutch can be converted to input shaft by the rotating speed that gathers odd number shelves countershaft and obtain, if the target gear is 2,4 grades, the rotating speed of target of so follow-up clutch can be converted to input shaft by the rotating speed that gathers even number shelves countershaft and obtain).In entry block 36, actual current speed ratio in other words based on the input speed of speed changer divided by the output speed of speed changer calculate (input speed is exactly current engine speed, the value of this rotating speed be exactly this moment engine control system send to the engine speed of control system of speed variator by the CAN communication; Output speed is exactly to be converted to the differential mechanism rear end and the value that obtains by the rotating speed that current jack shaft speed probe collects).This signal is exactly the control signal 31 shown in Fig. 4 and Fig. 5.In entry block 37, target is calculated based on input speed, input torque and the shift type of each clutch switching time.Then this time be divided out the ratio of regulation, and such as T1 accounts for 10% of cumulative time, T2 accounts for 80% of cumulative time, and T3 accounts for 10% of cumulative time.These ratios are not fixed for every kind of shift type.Shift type is defined as follows, and power on upgrades, and power off upgrades, and power on lowers category, and power off lowers category.Similarly, also having defined the speed ratio percentage change for every kind of shift type, for example, is 5% of overall ratio variable quantity in T1, is 90% of overall ratio variable quantity in T2, is 5% of overall ratio variable quantity in T3.In entry block 38, the goals ratio corresponding with the time (reasoning speed ratio) will produce target error with the deviation of actual speed ratio.This error is passed to the variation that a PID controller decides input torque.Then proceed to entry block 40, this will determine new moment of torsion target, thereby proceed to entry block 41.Then continue to calculate actual speed ratio by entry block 39, form closed loop control, until target is reached.

In entry block 37, goals ratio is definite according to nominal data, and nominal data depends on shift type, drives gear, input speed, input torque (being the moment of torsion that motor passes to speed changer) and current clutch temp.Goals ratio=previous goals ratio+goals ratio increment.Specifically being calculated as follows of goals ratio increment:

At first be to calculate the object time (this time represents with T) of completing gear shift, this time is determined by following two-part factor: the value of first portion's factor (representing with a) is to obtain by two parameter interpolation tables, two input quantities of this two parameter interpolations table are respectively: shift type, driving gear, the value in two parameter interpolation tables is the numerical value that can demarcate.The value of second portion factor (representing with b) is to obtain by three parameter interpolation tables, and three input quantities of this three parameter interpolations table are respectively input speed (engine speed), input torque (being the moment of torsion that motor passes to speed changer), when the temperature of front clutch.So complete the object time T=a+b of gear shift.

Next is to calculate the value of T1, T2, T3 and variation total amount, variation total amount, the variation total amount of speed ratio in the T3 time of speed ratio in the T2 time of speed ratio in the T1 time, and concrete calculation method is as follows: T1=T*T1 accounts for the percentage in T.The percentage (representing with e) that T1 accounts for time T is determined by two-part factor: the value of first portion's factor (representing with c) is to obtain by two parameter interpolation tables, two input quantities of this two parameter interpolations table are respectively: shift type, driving gear, the value in two parameter interpolation tables is the numerical value that can demarcate.The value of second portion factor (representing with b) is to obtain by three parameter interpolation tables, and three input quantities of this three parameter interpolations table are respectively input speed (engine speed), input torque (being the moment of torsion that motor passes to speed changer), when the temperature of front clutch.So T1 accounts for the percentage e=c+b of time T.T3=T*T3 accounts for the percentage in T.The percentage (representing with f) that T3 accounts for time T is determined by two-part factor: the value of first portion's factor (representing with h) is to obtain by two parameter interpolation tables, two input quantities of this two parameter interpolations table are respectively: shift type, driving gear, the value in two parameter interpolation tables is the numerical value that can demarcate.The value of second portion factor (representing with i) is to obtain by three parameter interpolation tables, and three input quantities of this three parameter interpolations table are respectively input speed (engine speed), input torque, when the temperature of front clutch.So T3 accounts for the percentage f=h+i of time T.T2=T*T2 accounts for the percentage in T.The percentage that T2 accounts in T represents with j, j=100%-e-f, and in whole shift time, the total amount that speed ratio changes is k=target gear ratios-driving gear ratios.The percentage that interior speed ratio variation of T1 time total amount accounts for k is m, and in the T1 time, speed ratio changes total amount n=k*m, and the value of m is to obtain by a two-dimensional interpolation table, and two input quantities of this two-dimensional interpolation table are respectively shift type, driving gear.The percentage that interior speed ratio variation of T3 time total amount accounts for k is p, and in the T3 time, speed ratio changes total amount q=k*p, and the value of p is to obtain by a two-dimensional interpolation table, and two input quantities of this two-dimensional interpolation table are respectively shift type, driving gear.In the T2 time, speed ratio changes total amount r=k-n-q.Calculate at last the goals ratio increment, the goals ratio increment=n/T1 in the T1 time; Goals ratio increment=r/T2 in the T2 time; Goals ratio increment=q/T3 in the T3 time; So, at the goals ratio of T1 in the time be: goals ratio=previous goals ratio+n/T1.At the goals ratio of T2 in the time be: goals ratio=previous goals ratio+r/T2.At the goals ratio of T3 in the time be: goals ratio=previous goals ratio+q/T3.

The clutch that drives gear place axle is front sequence clutch, and the clutch of target gear place axle is follow-up clutch.Remarks: in Clutch Control, the moment of torsion of calculating all has been converted to input shaft end.The increment of the torque request value of front sequence clutch is affected by two factors: first portion's factor is that a PID controller calculates gain, and this value can represent with s; The second portion factor is a dynamic adjustments value, and this dynamic adjustments value can represent with w.At T1 in the time: preorder clutch moment of torque value request=previous preorder clutch moment of torque value request+s+w.Three parameters of this PID controller can be with P1, I1, D1, represent.The current speed ratio error of the current speed ratio error+D1*(of the current speed ratio error+I1* of s=P1*-previous speed ratio error), P1 is determined by two-part factor, the value of first portion's factor (representing with P11) is to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: shift type, driving gear and input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.The second portion factor be (representing with P12) to be to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: current speed ratio error, input torque increment (current input torque-previous input torque) and current clutch temp, the value of three parameter interpolation tables is the numerical value that can demarcate.P1=P11+P12。I1 is determined by two-part factor: the value of first portion's factor (representing with I11) is to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: shift type, driving gear and input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.The second portion factor be (representing with I12) to be to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: current speed ratio error, input torque increment (current input torque-previous input torque) and current clutch temp, the value of three parameter interpolation tables is the numerical value that can demarcate.I1=I11+I12。D1 is determined by two-part factor: the value of first portion's factor (representing with D11) is to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: shift type, driving gear and input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.The second portion factor be (representing with D12) to be to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: current speed ratio error, input torque increment (current input torque-previous input torque) and current clutch temp, the value of three parameter interpolation tables is the numerical value that can demarcate.Dynamic adjustments value w obtains by three parameter interpolation tables, and three input quantities of this three parameter interpolations table are respectively: accelerator open degree, braking pedal state, output speed error (current output speed-previous output speed).So torque request value+s+w of the torque request value of front sequence clutch=previous front sequence clutch.The increment of the torque request value of follow-up clutch is affected by two factors, and first portion's factor is that a PID controller calculates gain, and this value can represent with v; The second portion factor is a dynamic adjustments value, and this dynamic adjustments value can represent with y.At T1 in the time: follow-up clutch moment of torque value request=previous follow-up clutch moment of torque value request+v+y, three parameters of this PID controller can be with P2, I2, D2, represent.The current speed ratio error of the current speed ratio error+D2*(of the current speed ratio error+I2* of v=P2*-previous speed ratio error) P2 is determined by two-part factor: the value of first portion's factor (representing with P21) is to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: shift type, driving gear and input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.The second portion factor be (representing with P22) to be to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: current speed ratio error, input torque increment (current input torque-previous input torque) and current clutch temp, the value of three parameter interpolation tables is the numerical value that can demarcate.P2=P21+P22。I2 is determined by two-part factor: the value of first portion's factor (representing with I21) is to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: shift type, driving gear and input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.The second portion factor be (representing with I22) to be to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: current speed ratio error, input torque increment (current input torque-previous input torque) and current clutch temp, the value of three parameter interpolation tables is the numerical value that can demarcate.I2=I21+I22。D2 is determined by two-part factor: the value of first portion's factor (representing with D21) is to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: shift type, driving gear and input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.The second portion factor be (representing with D22) to be to obtain by three parameter interpolation tables, three input quantities of this three parameter interpolations table are respectively: current speed ratio error, input torque increment (current input torque-previous input torque) and current clutch temp, the value of three parameter interpolation tables is the numerical value that can demarcate.Dynamic adjustments value y obtains by three parameter interpolation tables, and three input quantities of this three parameter interpolations table are respectively: accelerator open degree, braking pedal state, output speed error (current output speed-previous output speed).So torque request value+v+y of the torque request value of follow-up clutch=previous front sequence clutch.The increment of Engine torque value request is to be calculated by a PID controller, and this value can represent with z; At T1 in the time: Engine torque value request=previous Engine torque value request+z.Three parameters of this PID controller can be with P3, I3, D3, represent.The current speed ratio error of the current speed ratio error+D3*(of the current speed ratio error+I3* of z=P3*-previous speed ratio error).P3 is fixed by three parameter interpolation votings, three input variables of this interpolation table are respectively: current speed ratio error, shift type, (driver's requested torque is to issue control system of speed variator by engine control system by the CAN communication to driver's requested torque, this value is affected by accelerator open degree mainly) with the difference of current input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.I3 is fixed by three parameter interpolation votings, and three input variables of this interpolation table are respectively: current speed ratio error, and shift type, the difference of driver's requested torque and current input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.D3 is fixed by three parameter interpolation votings, and three input variables of this interpolation table are respectively: current speed ratio error, and shift type, the difference of driver's requested torque and current input torque, the value in three parameter interpolation tables is the numerical value that can demarcate.Torque request value+the z of the torque request value of motor=previous motor.T2, T3 are in the stage, and computational methods and the computational methods in T1 of preorder clutch moment of torque value request, follow-up clutch moment of torque value request, Engine torque value request are similar, and just the size of the demarcation numerical value in each interpolation table is not identical.

In entry block 46, accelerator open degree and braking pedal state are always monitored, thereby determine the object variations that therefore input brings.In entry block 45, the determining of object variations amount is based on and calculates from the input of entry block 43 and entry block 44.According to moment of torsion and load calculation acceleration responsive, calculate the acceleration responsive of speed changer in entry block 44 according to moment of torsion input in entry block 43.

Can stipulate that in T1, the value of closed loop gain is lower (namely in the clutch method for handover control of double-clutch speed changer of the present invention, in the T1 stage, the increment of preorder clutch moment of torque value request, the increment of follow-up clutch moment of torque value request, the increment of Engine torque value request is all lower).Can stipulate in the clutch method for handover control of double-clutch speed changer of the present invention that the goals ratio increment (q/T3) of T3 is than T1(n/T1) and T2(r/T2) lower.

In order to be more convenient for understanding intuitively the application, Fig. 4 and Fig. 5 have provided respectively upgrade speed ratio curve and the speed ratio curve that lowers category, and in Fig. 4,51 represent old gear ratios, and 52 represent the target gear ratios, and 53 represent the actual-gear speed ratio, and 54 represent target gear ratios curve; In Fig. 5,61 represent the target gear ratios, and 62 represent old gear ratios, and 63 represent the actual-gear speed ratio, and 64 represent target gear ratios curve.

Above-described embodiment is described the preferred embodiment of the present invention; be not that scope of the present invention is limited; design under the prerequisite of spirit not breaking away from the present invention; various distortion and improvement that those of ordinary skills make technological scheme of the present invention all should fall in the definite protection domain of claims of the present invention.

Claims (4)

1. the clutch method for handover control of a double-clutch speed changer, in described double-clutch speed changer, to switch the clutch of front transfer moment of torsion be front sequence clutch to clutch, another is follow-up clutch, it is characterized in that, comprises the following steps:
(1) determine the target gear ratios;
(2) determine the input torque of front sequence clutch;
(3) detect the input speed of front sequence clutch;
(4) detect the rotating speed of target of follow-up clutch;
(5) calculate current speed ratio with the input speed that detects divided by the output speed that detects;
(6) determine goals ratio according to nominal data, nominal data depends on shift type, drives gear, input speed, input torque and current clutch temp;
(7) deduct current speed ratio with goals ratio and calculate current speed ratio error;
(8) take the value of speed ratio error as controlling target, adopt the PID closed loop control successively to revise clutch moment of torque and Engine torque request, make actual speed ratio follow the goals ratio curve, the parameter of PID controller depends on shift type, speed ratio error, drives gear, input torque and current clutch temp, accelerator open degree, output speed, braking pedal situation.
2. the clutch method for handover control of double-clutch speed changer according to claim 1 is characterized in that: further comprise following steps:
(1) determine goals ratio with the target deadline of completing gear shift;
(2) time division section within the object time, three time phase T1, T2 in control and T3.
3. the clutch method for handover control of double-clutch speed changer according to claim 2 is characterized in that: further comprise following steps:
(1) the goals ratio increment of regulation T1;
(2) the low closed loop gain in regulation T1.
4. the clutch method for handover control of double-clutch speed changer according to claim 3 is characterized in that: further comprise following steps:
(1) the goals ratio incremental raio T1 of regulation T3 and T2's is lower.
CN2013100559139A 2013-02-21 2013-02-21 Method for controlling clutch switch process of dual-clutch transmission CN103148207A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2013100559139A CN103148207A (en) 2013-02-21 2013-02-21 Method for controlling clutch switch process of dual-clutch transmission

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN2013100559139A CN103148207A (en) 2013-02-21 2013-02-21 Method for controlling clutch switch process of dual-clutch transmission
CN201310263447.3A CN103322185B (en) 2013-02-21 2013-06-27 The clutch method for handover control of double-clutch speed changer

Publications (1)

Publication Number Publication Date
CN103148207A true CN103148207A (en) 2013-06-12

Family

ID=48546449

Family Applications (2)

Application Number Title Priority Date Filing Date
CN2013100559139A CN103148207A (en) 2013-02-21 2013-02-21 Method for controlling clutch switch process of dual-clutch transmission
CN201310263447.3A CN103322185B (en) 2013-02-21 2013-06-27 The clutch method for handover control of double-clutch speed changer

Family Applications After (1)

Application Number Title Priority Date Filing Date
CN201310263447.3A CN103322185B (en) 2013-02-21 2013-06-27 The clutch method for handover control of double-clutch speed changer

Country Status (1)

Country Link
CN (2) CN103148207A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106574674A (en) * 2014-06-19 2017-04-19 法雷奥离合器公司 Torque estimator for double clutch
WO2019228484A1 (en) * 2018-05-31 2019-12-05 长城汽车股份有限公司 Shift control method and device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104976243B (en) * 2015-07-17 2017-03-29 上海汽车变速器有限公司 The pre-oiling pressure adaptive method and system of wet dual-clutch automatic transmission

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3900049B2 (en) * 2002-09-12 2007-04-04 トヨタ自動車株式会社 Hydraulic control device for automatic transmission for vehicle
JP4446911B2 (en) * 2005-03-17 2010-04-07 ジヤトコ株式会社 Gear ratio control device for CVT
CN101130364B (en) * 2006-08-21 2011-12-28 五十铃自动车株式会社 Device for controlling running vehicle
JP4300233B2 (en) * 2006-10-24 2009-07-22 ジヤトコ株式会社 Control device and method for automatic transmission
US8682545B2 (en) * 2010-06-15 2014-03-25 Ford Global Technologies, Llc Damping oscillations during a gear ratio change of a dual clutch powershift transmission
CN102275585B (en) * 2011-05-18 2013-07-24 上海理工大学 Power system efficiency control method of input distribution type hybrid vehicle

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106574674A (en) * 2014-06-19 2017-04-19 法雷奥离合器公司 Torque estimator for double clutch
CN106574674B (en) * 2014-06-19 2019-10-15 法雷奥离合器公司 Torque estimator for double clutch
WO2019228484A1 (en) * 2018-05-31 2019-12-05 长城汽车股份有限公司 Shift control method and device

Also Published As

Publication number Publication date
CN103322185B (en) 2015-10-28
CN103322185A (en) 2013-09-25

Similar Documents

Publication Publication Date Title
EP1596087B1 (en) Clutch torque point learning method and clutch control method
US7354368B2 (en) Method and means for shifting a hydromechanical transmission
CN102072268B (en) For the method for adapting engagement point
EP1921350B1 (en) Method and control system for improving shift feeling in automated transmissions
US7507182B2 (en) Controller, control method and control system for controlling a motor vehicle gear-type transmission
US7962267B2 (en) Control apparatus and method for automatic transmission
US6909955B2 (en) Method of controlling a dual clutch transmission
US6510931B2 (en) Method of operating a torque transfer system
CN100535482C (en) Gear shifting controlling device and method for automatic double clutch type speed variator
CN100532173C (en) Method and apparatus for controlling gear shift of automobile parallel speed changer
US9470309B2 (en) Vehicle transmission controller
CN101844557B (en) Control device for automatic transmission
EP1977944B1 (en) Transmission control method and apparatus for a vehicle
US8788163B2 (en) Method for operating a vehicle drive train
JP5374726B2 (en) Clutch control device and μ correction coefficient calculation method
CN103299104B (en) Speed changer and change control system
CN100513831C (en) Shift control apparatus and method for automatic transmission
CN103807321B (en) The method for searching for the contact point of clutch
US9002603B2 (en) Method for the operation of a transmission device in a vehicle drive train when a request is made to change gears
JP5790672B2 (en) Vehicle shift control device
WO2013130416A1 (en) Multi-range hydro-mechanical transmission
CN102797841B (en) Control equipment for double clutch type automatic transmission
CN101825170B (en) Control apparatus and control method for automatic transmission
CN105620460B (en) Control system and method for hybrid vehicle transmission
US20100113217A1 (en) Synchronous state determination method for automatic dual clutch transmission

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
WW01 Invention patent application withdrawn after publication

Application publication date: 20130612

C04 Withdrawal of patent application after publication (patent law 2001)