CN107166024B - A kind of downshift control method of big-powered tractor perseverance torque power - Google Patents

A kind of downshift control method of big-powered tractor perseverance torque power Download PDF

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CN107166024B
CN107166024B CN201710533948.7A CN201710533948A CN107166024B CN 107166024 B CN107166024 B CN 107166024B CN 201710533948 A CN201710533948 A CN 201710533948A CN 107166024 B CN107166024 B CN 107166024B
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clutch
power
formula
pressure
torque
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CN107166024A (en
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夏光
施信信
滑杨莹
郭东云
郑友
闫瑞琦
邹斌
杜克
谢海
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Hefei University of Technology
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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
    • 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
    • F16H2061/0075—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 characterised by a particular control method
    • F16H2061/009—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 characterised by a particular control method using formulas or mathematic relations for calculating parameters

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

The invention discloses a kind of downshift control methods of big-powered tractor perseverance torque power, it is that tractor dynamic power downshift control process is divided into shift preparation stage, rotating speed synchronous phase, gear stacking stage and gear strain, by controlling the coordination of engagement clutch, separation clutch and engine, to realize that variable ratio drive system during power downshift remains the purpose of permanent torque output so that tractor dynamic power shift smooth-going, without impact.

Description

A kind of downshift control method of big-powered tractor perseverance torque power
Technical field
The invention belongs to tractor dynamic power shift control fields, specifically a kind of to be dragged for Multi-clutch high-power The downshift control method of machine drawing perseverance torque power.
Technical background
Tractor work has following characteristics：(1) by agronomy and machine and tool bearing capacity, general uniform motion；(2) in order to Productivity is improved, accelerator open degree is generally 80% or more；(3) working resistance can fluctuate, and traditional manual transmission is difficult to adapt to The variation of working resistance, need to stop shift；For the operating feature of tractor, foreign countries propose that ' (power changes Power Shift ' Gear) transmission system, the tractor cost for configuring this transmission system is also relatively high.The transmission system effectively expands tractor and holds The working resistance range of continuous work avoids conventional manual transmission frequently parking shift caused by working resistance changes, carries The high production efficiency of tractor.Tractor work is shifted gears generally under very heavy load condition, is shifted gears and is controlled according to non-powered Method, since speed is low, tractor is easy to stop, to influence productivity.How to avoid tractor in fluid drive process Middle stop because of power interruption is to need one of critical issue solved in tractor dynamic power shift control system R&D process.
So-called power shifting, also known as " band carries shift " are to ensure shift under the premise of meeting certain shift quality requirement The unbroken shift of power in the process.Power downshift belongs to a part for power shifting technology, in Multi-clutch power transmission In system, realize that shift process power persistently exports by two or more clutches, when separation clutch is not kept completely separate also When engagement engagement clutch, to ensure that power does not interrupt.But during downshift, if engagement clutch driving plate rotating speed be less than from Moving plate rotating speed then engages clutch back transfer torque and generates parasitic power.Parasitic power is also referred to as circulating power, should Power can also cause transmission system parts very big damage other than causing unnecessary energy loss.Tractor work has Traction, rotary tillage and harvesting diversified forms, when operation, power downshift also needs to ensure tractor work quality and efficiency, if dropping The output torque variation of tractor is excessive during gear, then can not ensure operation quality, is easy to damage equipment, while and With will appear upshift pause and transition in rhythm or melody, the ride comfort that downshifts is influenced, and is controlled only by the shift clutch to big-powered tractor System can not be difficult to realize during power downshift permanent torque output always.
Invention content
The present invention is in place of overcoming the shortcomings of the prior art, to propose a kind of drop of big-powered tractor perseverance torque power Control method is kept off, to by controlling separation, oncoming clutch pressure and diesel engine output power, realize dynamic Variable ratio drive system remains the purpose of permanent torque output during power downshift, so that tractor dynamic power shift smooth-going, Without impact.
The present invention is to solve technical problem to adopt the following technical scheme that：
A kind of the characteristics of downshift control method of big-powered tractor perseverance torque power of the present invention is by tractor perseverance torque The process of power downshift control is divided into：Shift preparation stage, rotating speed synchronous phase, gear stacking stage and engagement strain, And it carries out as follows：
Step 1, in the shift preparation stage, act pressure to the engagement clutch for increasing engagement clutch maintains Pressure pIt is accurate, so that engagement clutch is in torque and transmit critical condition, to eliminate the idle stroke of engagement clutch；
Step 2 is carved at the beginning of the rotating speed synchronous phase, and the output power of diesel engine is increased accelerating power ΔPAdd 1, then incrementally increase the output power of diesel engine and rubbed wasted power Δ P with the cunning for compensating separation clutchDamage；Simultaneously Reduce the act pressure of separation clutch to the load torque pressure p of separation clutchPointAnd it remains unchanged；
Step 3 is carved at the beginning of the gear stacking stage, and the output power of diesel engine is reduced accelerating power ΔPAdd 2, then gradually reduce the output power of diesel engine and rubbed wasted power Δ P with the cunning for compensating separation clutchDamage；Simultaneously The act pressure of engagement clutch is incrementally increased to the load torque pressure p of the engagement clutchIt closesUntil, and gradually reduce institute The act pressure of separation clutch is stated, and the separation clutch meets gear stacking stage with the act pressure for engaging clutch Pressure increment relationship；
Step 4, in the engagement strain, keep the output power of diesel engine constant, at the same increase described in connect Close the upper pressure limit p that the act pressure of clutch is transmitted to engagement clutch moment of torqueEventually。
The characteristics of downshift control method of big-powered tractor perseverance torque power of the present invention, lies also in：
The pressure p that the engagement clutch is maintained in the preparation stage is calculated using formula (1)It is accurate：
In formula (1), FpreFor the pretensioned spring power of the resetting spring of the engagement clutch, FfFor piston friction power, Ah For piston effective active area.
Diesel engine is calculated in rotating speed synchronous phase start time increased accelerating power Δ P using formula (2)Add 1：
ΔPAdd 1=Jeαωe (2)
In formula (2), JeFor input shaft rotary inertia, α is input axle acceleration；ωeFor input shaft rotating speed.
The separation clutch is calculated using formula (3) to rub wasted power Δ P in the cunning of rotating speed synchronous phaseDamage：
ΔPDamage=kpPointΔωPoint (3)
In formula (3), Δ ωPointTo detach the speed discrepancy of clutch principal and subordinate's Moving plate；The separation clutch load torque pressure pPointIt is calculated using formula (4)：
In formula (4), TLFor the torque that the separation clutch transmits, k is frictional behavior coefficient, by friction plate the piece number, is rubbed It wipes contact surface internal-and external diameter and friction plate material determines；
The accelerating power Δ P that diesel engine reduces in gear stacking stage start time is calculated using formula (5)Add 2：
ΔPAdd 2=Jeαωe2 (5)
In formula (5), ωe2For the rotating speed of gear stacking stage start time input shaft.
The load torque pressure p of the engagement clutch is calculated using formula (6)It closes：
In formula (6), q is adjacent two gears transmission ratio ratio.
The pressure increment relationship of gear stacking stage is obtained using formula (7)：
|ΔpPoint|=| q Δs pIt closes| (7)
In formula (7), Δ pPointFor the pressure increment of the separation clutch, Δ pIt closesPressure for the engagement clutch increases Amount；
The upper pressure limit p that the engagement clutch moment of torque transmits is calculated using formula (8)Eventually：
pEventually=η pIt closes (8)
In formula (8), η is the coefficient more than 1.
Compared with the prior art, beneficial effects of the present invention are embodied in：
1, just start after its driving and driven disk rotating speed synchronizes the invention is characterized in that engaging clutch during power downshift The control method of engagement makes clutch is positive always to transmit torque, avoids the generation of parasitic power；
2, the present invention is according to power-balance relationship during downshift, in rotating speed synchronous phase by improving diesel engine The output power of machine improves input shaft rotating speed to compensate the unit friction work loss in gear stacking stage, to realize output Constant torque；
3, the present invention is by establishing the engagement of gear stacking stage, separation clutch act pressure increment relation, in conjunction with right The output power of diesel engine completes the power handing-over of gear stacking stage, ensure that during downshifting without parasitism Power, and output torque is constant.
Description of the drawings
Fig. 1 is the power transmission line schematic diagram of power-shift transmission of the present invention；
Fig. 2 is diesel engine output power change curve of the present invention；
Fig. 3 is Detaching and Lapping clutch act pressure change curve of the present invention；
Fig. 4 is output torque change curve in shift process of the present invention；
Fig. 5 is input and output rotation speed change curve graph in shift process of the present invention.
Specific implementation mode
In the present embodiment, a kind of downshift control method of big-powered tractor perseverance torque power is by tractor perseverance torque The process of power upshift control is divided into：Shift preparation stage, rotating speed synchronous phase, gear stacking stage and engagement strain, Permanent torque upshift is realized by controlling the coordination of engagement clutch, separation clutch and engine, refering to fig. 1-Fig. 5, specifically Say, be to carry out as follows：
Step 1, shift the preparation stage, i.e. t1~t2Stage increases the act pressure of engagement clutch to engaging clutch The pressure p of maintenanceIt is accurate, so that engagement clutch is in torque and transmit critical condition, to eliminate the idle stroke of engagement clutch；
The pressure p that engagement clutch is maintained in the preparation stageIt is accurateIt is calculated using formula (1)：
In formula (1), FpreFor the pretensioned spring power of the resetting spring of the engagement clutch；FfFor piston friction power；Ah For piston effective active area.
Step 2, in rotating speed synchronous phase, i.e. t2~t3Stage, at this stage t2Moment, the driven disc for engaging clutch turn Speed is more than active disk rotating speed, and in order to avoid generating parasitic power, engagement clutch is failure to actuate at this stage until its principal and subordinate's Moving plate Rotating speed synchronizes；In order to make the driven disk rotating speed Fast synchronization of engagement clutch winner, the output power increase of diesel engine is added Fast power Δ PAdd 1, i.e., it is accelerating power Δ P by the output power increase of diesel engineAdd 1, to improve input shaft input torque And input shaft rotating speed；Then it incrementally increases the output power of diesel engine and is rubbed wasted power Δ with the cunning for compensating separation clutch PDamage；Reduce the act pressure of separation clutch simultaneously to the load torque pressure p of separation clutchPointAnd it remains unchanged；In rotating speed Synchronous phase finish time, separation clutch becomes sliding state of rubbing from engagement state, and output torque is constant；
Diesel engine is in rotating speed synchronous phase t2Moment increased accelerating power Δ PAdd 1It is calculated using formula (2)：
ΔPAdd 1=Jeαωe (2)
In formula (2), JeFor input shaft rotary inertia, α is input axle acceleration；ωeFor input shaft rotating speed；
The cunning of separation clutch is rubbed wasted power Δ PDamageIt is calculated using formula (3)：
ΔPDamage=kpPointΔωPoint (3)
In formula (3), Δ ωPointTo detach clutch principal and subordinate's Moving plate speed discrepancy；
Load torque pressure p of the separation clutch in rotating speed synchronous phasePointIt is calculated using formula (4)：
In formula (4), TLFor the torque that separation clutch transmits, k is frictional behavior coefficient, is connect by friction plate the piece number, friction Contacting surface internal-and external diameter and friction plate material determine；Wherein, the calculating of frictional behavior coefficient k carries out in accordance with the following methods：
1, when clutch is dry clutch, frictional behavior coefficient k is calculated using formula (5)：
In formula (5), μ, S, Z, R0、R1Respectively clutch friction coefficient, contact area, friction plate the piece number, friction plate outer diameter And internal diameter.
2, when clutch is wet clutch, frictional behavior coefficient k can be obtained by platform experiment, specifically according to following Experimental method carries out：
Wet clutch is accessed into clutch test stand, the output end access load of testing stand, the act pressure of clutch FsendWith load torque TloadIt is provided by electric hydraulic oil pump, it is Δ F that defining clutch act pressure, which adjusts step pitch,send, load It is Δ T that torque, which adjusts step pitch,load。
(1) apply clutch act pressure Fsend=Δ Fsend, and remain unchanged, while it is Δ T to apply load torqueload, And constantly adjustment load torque size until clutch starts, rub and the driven end uniform motion of clutch, record apply instantly by cunning Load torque size delta Tload1, preserve clutch act pressure Fsend=Δ FsendWith load torque Tload=Δ Tload1；
(2) step pitch Δ F is adjusted with clutch act pressuresendIncrease the act pressure F for adding clutchsend=2 Δ Fsend, And remain unchanged, while it is Δ T to apply load torqueload, and constantly adjustment load torque size is until clutch starts cunning and rubs And the driven end uniform motion of clutch, record the load torque size delta T applied instantlyload2, preserve clutch act pressure Fsend=2 Δ FsendWith load torque Tload=Δ Tload1。
Step 3, in gear stacking stage, i.e. t3~t4Stage, at this stage t3Moment obtains to remain engaged with clutch The output power of diesel engine is reduced accelerating power Δ P by principal and subordinate's Moving plate rotating speedAdd 2, i.e., by the output power of diesel engine Reduction amount is accelerating power Δ PAdd 2, to reduce input shaft input torque and input shaft rotating speed；Then diesel engine is gradually reduced Output power rubbed wasted power Δ P with the cunning for compensating separation clutchDamage；The act pressure of engagement clutch is incrementally increased simultaneously To the load torque pressure p of the engagement clutchIt closesUntil, and the act pressure of the separation clutch is gradually reduced, and point Luxuriant clutch meets the pressure increment relationship of gear stacking stage with the act pressure for engaging clutch, so that in gear weight Folded stage output torque remains unchanged；
The accelerating power Δ P that diesel engine reduces in gear stacking stage start timeAdd 2It is calculated using formula (6)：
ΔPAdd 2=Jeαωe2 (6)
In formula (6), ωe2For the rotating speed of gear stacking stage start time input shaft；
Engage the load torque pressure p of clutchIt closesIt is calculated using formula (7)：
In formula (7), q is adjacent two gears transmission ratio ratio；
The pressure increment relationship of gear stacking stage meets formula (8)：
|ΔpPoint|=| q Δs pIt closes| (8)
Formula (8), Δ pPointTo detach the pressure increment of clutch, Δ pIt closesTo engage the pressure increment of clutch；
Step 4 is engaging strain, i.e. t4~t5Stage keeps the output power of diesel engine constant, increases simultaneously The upper pressure limit p that the act pressure of big engagement clutch is transmitted to engagement clutch moment of torqueEventually。
Engage the upper pressure limit p that clutch moment of torque transmitsEventuallyIt is calculated using formula (8)：
pEventually=η pIt closes (9)
In formula (9), η is the coefficient more than 1；The value of η depending on the fluctuation range of clutch transmission torque size, Value range is that [1.1,1.5] be easy to cause hydraulic pipeline leakage if the value of η is excessive；Conversely, then easily causing engagement Slipping of clutch.
By above step to the output power of the pressure control and diesel engine of shift clutch, high-power is realized The permanent torque power downshift of tractor controls, and to realize, output torque is constant, shifts gears without impact.
Embodiment：The present embodiment downshifts control method to certain model big-powered tractor power using the tractor of the present invention Gear shift transmission carries out 4 grades of drops, 3 grades of controls.
Refering to fig. 1, C1、C2、C3And C4Respectively shift clutch, as clutch C1、C2Separation, clutch C3、C4Engagement When, power-shift transmission gear is 4 grades；As clutch C1、C4Engagement, clutch C2、C3When separation, power-shift transmission Gear is 3 grades；When transmission gear from 4 grades drop 3 grades when, clutch C1Become engagement state, clutch C from discrete state3From connecing Conjunction state becomes discrete state, and power flow is gradually from clutch C3It is transitioned into clutch C1；
Certain model big-powered tractor power system parameter is as follows：Detach the load torque T that clutch transmitsLFor 380N.m；Piston cylinder pretensioned spring power FpreFor 20N；Piston friction power FfFor 10N；Piston effective active area AhFor 0.01m2；K is 0.098N.m/pa；Q is 1.2；η is 1.3；Input shaft rotary inertia JeFor 0.5kg.m2, rotating speed synchronous phase opens Begin moment input shaft rotating speed ωe1For 180rad/s, gear stacking stage start time input shaft rotating speed ωe2It is defeated for 216rad/s It is 90rad/s to enter shaft angle acceleration2, gear overlapping time tIt closesFor 0.4s；Output shaft rotational speed omegavFor 150rad/s；
The pressure p that engagement clutch is maintained in the preparation stage is calculated according to formula (1)It is accurate=300pa；It is calculated and is turned according to formula (2) The fast increased accelerating power Δ P of synchronous phaseAdd 1=8.1kW；Rotating speed synchronous phase is calculated according to formula (3) to rub compensating for loss and damage power ΔPDamage=kpPointΔωPoint=TLα t=13.7kW；Separation clutch load torque pressure is calculated according to formula (4)Rotating speed synchronous phase input shaft rotating speed ωe=180+ α t=216rad/s；It is calculated and is engaged according to formula (7) Clutch load torque pressureSince gear overlapping time is 0.4s, detach under clutch pressure Reduction of speed rateFor 11600pa/s, oncoming clutch pressure climbing speedFor 9717pa/s；Gear is calculated according to formula (6) The accelerating power Δ P that stacking stage start time reducesAdd 2=9.72kW；The cunning abrasion of gear stacking stage is calculated according to formula (3) Lose compensation power Δ PDamage=kpPointΔωPoint=-34.2t=-13.7kW；The pressure that engagement clutch moment of torque transmits is calculated according to formula (9) Power upper limit pEventually=η pIt closes=5053pa；
Referring to Fig.2, peFor the output power of diesel engine, in t2~t3In the stage, diesel engine is in rotating speed synchronous phase t2When Carve increased accelerating power Δ PAdd 1=8.1kW, to improve input shaft input torque and input shaft rotating speed；Then bavin is incrementally increased The output power of oil turbine is rubbed wasted power Δ P with the cunning for compensating separation clutchDamage=13.7kW, to compensate engagement clutch Unit friction work loss；In t3~t4Stage, at this stage t3Moment, in order to remain engaged with the driven disk rotating speed of clutch winner, diesel oil The output power of engine reduces accelerating power Δ PAdd 2=9.72kW, to reduce input shaft input torque and input shaft rotating speed；So The output power of diesel engine is gradually reduced afterwards to be rubbed wasted power Δ P with the cunning for compensating separation clutchDamage=-13.7kW；? t4~t5Stage keeps the output power 57kW of diesel engine constant.
Refering to Fig. 3, Pc1To engage the act pressure of clutch, Pc3To detach the act pressure of clutch, in t1~t2Rank Section increases the act pressure P of engagement clutchc1The pressure p maintained to engagement clutchIt is accurate=300pa makes engagement clutch be in Torque transmits critical condition, to eliminate the idle stroke of engagement clutch；In t2~t3In the stage, reduce separation clutch makees dynamic pressure Power Pc3To separation clutch load torque pressureAnd it remains unchanged；That is t3~t4Stage, when gear is overlapped Between tIt closes=0.4s, Pc1With Pc3Meet the pressure increment relationship of formula (8), and engages clutch act pressure Pc1Climbing speed For 9717pa/s, separation clutch act pressure Pc3Fall off rateFor 11600pa/s；In t4~t5Stage increases engagement The act pressure P of clutchc1The upper pressure limit p transmitted to engagement clutch moment of torqueEventually=η pIt closes=5053pa.
Refering to Fig. 4, wherein Tc1For clutch C1The torque of transmission, Tc3For clutch C3The torque of transmission, ToutIt is turned round for output Square；According to the process that big-powered tractor perseverance torque power downshift controls, by engaging clutch, separation clutch and starting The coordination of machine controls, and t is overlapped in gear2~t3Stage, Tc3It gradually reduces, Tc1It incrementally increases, ToutIt is constant, realize the model Power drive system remains that permanent torque power is defeated during big-powered tractor power-shift transmission drops 3 grades at 4 grades Go out；
Refering to Fig. 5, wherein ωeFor input shaft rotating speed, ωvTo export rotating speed, ωeT is synchronized in rotating speed2~t3Stage rotating speed Rise, and ωvIt all remains unchanged in entire shift process, realizes smooth shift, ensure that tractor continuous operation.
So far, by controlling the coordination of engagement clutch, separation clutch and engine, the model high-power is realized Power drive system remains permanent torque power output during tractor dynamic power shift speed changer drops 3 grades at 4 grades, realizes Smooth-going downshift, ensure that tractor continuous operation, and clutch C3 gradually becomes discrete state from engagement state, clutch C1 from Discrete state gradually becomes engagement state, and entire perseverance torque power downshift process is completed.

Claims (1)

1. a kind of downshift control method of big-powered tractor perseverance torque power, it is characterized in that by tractor perseverance torque power downshift The process of control is divided into：Shift preparation stage, rotating speed synchronous phase, gear stacking stage and engagement strain, and by as follows Step carries out：
Step 1, in the shift preparation stage, increase the pressure that the act pressure of engagement clutch is maintained to the engagement clutch Power pIt is accurate, so that engagement clutch is in torque and transmit critical condition, to eliminate the idle stroke of engagement clutch；
The pressure p that the engagement clutch is maintained in the preparation stage is calculated using formula (1)It is accurate：
In formula (1), FpreFor the pretensioned spring power of the resetting spring of the engagement clutch, FfFor piston friction power, AhFor work Fill in effective active area；
Step 2 is carved at the beginning of the rotating speed synchronous phase, and the output power of diesel engine is increased accelerating power Δ PAdd 1, then incrementally increase the output power of diesel engine and rubbed wasted power Δ P with the cunning for compensating separation clutchDamage；Subtract simultaneously The act pressure of small separation clutch extremely detaches the load torque pressure p of clutchPointAnd it remains unchanged；
Diesel engine is calculated in rotating speed synchronous phase start time increased accelerating power Δ P using formula (2)Add 1：
ΔPAdd 1=Jeαωe (2)
In formula (2), JeFor input shaft rotary inertia, α is input axle acceleration；ωeFor input shaft rotating speed；
The separation clutch is calculated using formula (3) to rub wasted power Δ P in the cunning of rotating speed synchronous phaseDamage：
ΔPDamage=kpPointΔωPoint (3)
In formula (3), Δ ωPointTo detach the speed discrepancy of clutch principal and subordinate's Moving plate；The separation clutch load torque pressure pPointProfit It is calculated with formula (4)：
In formula (4), TLFor the torque that the separation clutch transmits, k is frictional behavior coefficient, by friction plate the piece number, CONTACT WITH FRICTION Face internal-and external diameter and friction plate material determine；
Step 3 is carved at the beginning of the gear stacking stage, and the output power of diesel engine is reduced accelerating power Δ PAdd 2, then gradually reduce the output power of diesel engine and rubbed wasted power Δ P with the cunning for compensating separation clutchDamage；While by Step increases the act pressure of engagement clutch to the load torque pressure p of the engagement clutchIt closesUntil, and gradually reduce described The act pressure of clutch is detached, and the separation clutch meets gear stacking stage with the act pressure for engaging clutch Pressure increment relationship；
The accelerating power Δ P that diesel engine reduces in gear stacking stage start time is calculated using formula (5)Add 2：
ΔPAdd 2=Jeαωe2 (5)
In formula (5), ωe2For the rotating speed of gear stacking stage start time input shaft；
The load torque pressure p of the engagement clutch is calculated using formula (6)It closes：
In formula (6), q is adjacent two gears transmission ratio ratio；
The pressure increment relationship of gear stacking stage is obtained using formula (7)：
|ΔpPoint|=| q Δs pIt closes| (7)
In formula (7), Δ pPointFor the pressure increment of the separation clutch, Δ pIt closesFor the pressure increment of the engagement clutch；
Step 4, in the engagement strain, keep the output power of diesel engine constant, at the same increase it is described engage from The upper pressure limit p that the act pressure of clutch is transmitted to engagement clutch moment of torqueEventually；
The upper pressure limit p that the engagement clutch moment of torque transmits is calculated using formula (8)Eventually：
pEventually=η pIt closes (8)
In formula (8), η is the coefficient more than 1.
CN201710533948.7A 2017-07-03 2017-07-03 A kind of downshift control method of big-powered tractor perseverance torque power Active CN107166024B (en)

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CN111221367B (en) * 2020-03-12 2021-08-17 合肥工业大学 Control method of multifunctional actuator combining motor and controllable clutch
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

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