CN106151493B - Automatic catch automobile dynamical system control method - Google Patents
Automatic catch automobile dynamical system control method Download PDFInfo
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- CN106151493B CN106151493B CN201510146429.6A CN201510146429A CN106151493B CN 106151493 B CN106151493 B CN 106151493B CN 201510146429 A CN201510146429 A CN 201510146429A CN 106151493 B CN106151493 B CN 106151493B
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- 238000005183 dynamical system Methods 0.000 title claims abstract description 7
- 238000000034 methods Methods 0.000 claims abstract description 27
- 230000005540 biological transmission Effects 0.000 claims description 20
- 230000001133 acceleration Effects 0.000 claims description 8
- 230000002045 lasting Effects 0.000 claims description 3
- 239000007788 liquids Substances 0.000 claims description 2
- 230000001603 reducing Effects 0.000 abstract description 5
- 239000000295 fuel oils Substances 0.000 abstract description 3
- 230000003993 interaction Effects 0.000 abstract description 2
- 238000010586 diagrams Methods 0.000 description 6
- 230000035939 shock Effects 0.000 description 4
- 239000003921 oils Substances 0.000 description 3
- 238000007634 remodeling Methods 0.000 description 2
- 239000004152 Nitrogen oxides Substances 0.000 description 1
- 280000060737 Systems Control companies 0.000 description 1
- UGFAIRIUMAVXCW-UHFFFAOYSA-N carbon monoxide Chemical compound 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- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitric oxide Chemical class 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O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 1
- 229910052813 nitrogen oxides Inorganic materials 0.000 description 1
Classifications
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- Y02T10/76—
Abstract
Description
Technical field
The present invention relates to technical field of automobile control；Specifically, the present invention relates to a kind of automatic catch automobile dynamical systems Control method.
Background technology
It is well known that not having clutch between the engine and gearbox of automatic catch automobile, the connection between them is logical Fluid torque-converter is crossed to realize.The effect of fluid torque-converter includes transmitting rotating speed and torque and makes engine and fluid drive Connection between case becomes nonrigid to facilitate self shifter.
Fig. 1 is traditional shift process schematic diagram according to prior art.In Fig. 1, reference numeral 1 represents engine speed Curve, 2 represent turbine speed curves, and 3 represent engine torque curve.Automatic catch automobile is during upshift, due to different gears The difference of interdigit gearratio, the secondary speed of fluid torque-converter can decline during upshift, and engine speed can be with fluid power The decline of torque converter turbine rotating speed and decline.In this way, driver can be perceived by the reduction of engine speed on instrument board Occurent gearshift simultaneously because the inertia torque brought of engine speed reduction influences, needs pair during gearshift control Engine carries out drop and turns round control, if drop turns round control and is unable to the decline of perfect cooperation engine speed, is just very easy to open in rotating speed The stage begun to decline and decline end generates shift shock.
In the dynamical system control of traditional automatic catch automobile upshift process, engine speed will not be deliberately controlled, so Engine speed can be reduced with the reduction of transformer turbine rotating speed, in order to overcome engine speed used during reducing Property shift shock caused by torque, Transmission Control Module can ask engine control module by postpone ignition advance angle etc. side Method reduces the influence of the output torque, balancing inertia torque of engine.Burning can be caused not fill however, postponing ignition advance angle Divide, reduce fuel oil service efficiency, while insufficient burning can also bring more carbon monoxide and nitrogen oxides, increase ternary to urge Change device burden and increase exhaust emissions amount.
Invention content
The object of the present invention is to provide a kind of automobile dynamic system control methods that can overcome aforementioned prior art problem.
The foregoing purpose for the present invention that the invention is realized by the following technical scheme, wherein, the present solution provides one Kind of automatic catch automobile dynamical system control method, the automobile dynamic system include engine, fluid torque-converter and gearbox with And engine control module and Transmission Control Module, in shift process：
The engine control module determines that driver it is expected torque according to engine rotational speed signal and accelerator pedal signal, And the engine rotational speed signal when driver it is expected, torque and gearshift start is sent to the Transmission Control Module；
The Transmission Control Module according to the driver it is expected torque, the speed signal of automobile, current shift speed ratio, Target gear speed compares, designs the engine target torque that gearshift opportunity and shift duration calculate satisfaction gearshift requirement in real time It is sent to the engine control module, the engine that the engine control module is sent out according to the Transmission Control Module Target torque request output meets the engine torque of gearshift requirement；
The Transmission Control Module calculates the lock-up clutch control pressure signal of the fluid torque-converter in real time, lock Only clutch pressure control valve exports lock-up clutch pressure according to the lock-up clutch pressure controling signal.
Optionally, it in foregoing control method, when speed reaches upshift shifting points, is controlled by the engine Module records engine rotational speed signal when gearshift starts by engine speed sensor, is remembered by the Transmission Control Module The current shift speed ratio, the target gear speed ratio and the design gearshift opportunity under record.
Optionally, it in foregoing control method, calculates the engine target torquing step and includes：
Speed ratio is respectively kept off according to speed, gearbox, shift time determines target turbine rotating speed in shift process；
Respectively kept off according to gearbox speed ratio, shift time and driver expectation engine output torque determine that gearbox target is defeated Go out torque；
Vehicle target acceleration is calculated according to gearbox target output torque, according to vehicle target acceleration calculation engine Rotating speed of target；
Target slippage is determined according to engine target rotating speed and target turbine rotating speed；
Fluid torque-converter rotating speed of target ratio and target torque ratio are determined according to target slippage；And
Target engine torque is determined according to fluid torque-converter target torque ratio and gearbox target output torque.
Optionally, in foregoing control method, the calculation formula of the target turbine rotating speed is：
WhereinIt represents target turbine rotating speed, representsSpeed,Represent that vehicle travels one kilometer of wheel The number of turns turned over,It represents when front speed ratio,Represent targeted gear speed ratio,Represent lasting shift time,Represent design shift time.
Optionally, in foregoing control method, the calculation formula of the gearbox target output torque is：
WhereinIt represents gearbox target output torque, representsThe desired engine output of driver Torque.
Optionally, in foregoing control method, the calculation formula of the engine target rotating speed is：
WhereinRepresent engine target rotating speed,Represent engine speed when gearshift starts, Represent vehicle target acceleration.
Optionally, in foregoing control method, the calculation formula of the target slippage is：
WhereinRepresent target slippage.
Optionally, in foregoing control method, the rotating speed of target than calculation formula be：
WhereinRepresent fluid torque-converter rotating speed of target ratio, fluid torque-converter target torque ratio It is determined by fluid torque-converter rotating speed of target ratio and fluid torque-converter indicatrix.
Optionally, in foregoing control method, the calculation formula of the target engine torque is：
WhereinTo meet the target engine torque of gearshift needs.
By will be seen that above, automobile dynamic system control method according to the present invention can keep sending out during upshift Motivation rotating speed does not decline, by the pressure for controlling engine output torque and lockup clutch of converter in shift process Power makes engine speed be maintained in a constant range, so as to which driver will not be discovered by the variation of engine speed To shift process；Simultaneously because engine speed does not reduce in shift process, inertia torque can be effectively reduced to gearshift Influence, reduce the drop in shift process and turn round demand, farthest reduce shift shock, at the same will not cause to burn it is insufficient, Reduce the negative interactions such as fuel oil service efficiency.
Description of the drawings
With reference to attached drawing, the disclosure will become more obviously.It is to be appreciated that these attached drawings are merely illustrative Purpose, and be not intended to limit protection scope of the present invention.In figure：
Fig. 1 is traditional shift process schematic diagram according to prior art；
Fig. 2 is the schematic diagram of automobile dynamic system control process according to embodiment of the present invention；And
Fig. 3 is the shift process schematic diagram of aforementioned embodiments control automobile dynamic system according to the present invention.
Specific embodiment
The specific embodiment that the invention will now be described in detail with reference to the accompanying drawings.
Fig. 2 is the schematic diagram of automobile dynamic system control process according to embodiment of the present invention.It can from Fig. 2 To find out, automobile dynamic system control method is by controlling engine output torque and fluid power in shift process in the present invention The pressure of torque converter lock-up clutch controls engine speed during upshift.Specifically, in illustrated embodiment Method may comprise steps of：
1) engine speed for start time of shifting gears and accelerator pedal signal are inputted into engine control module, engine control It is desired to export driver according to the relationship between the engine speed of design, accelerator pedal signal and engine torque for molding root tuber Engine output torque.
2) speed ratio is respectively kept off according to speed, gearbox, shift time determines target turbine rotating speed in shift process, turbine turns Speed calculation formula be：
WhereinIt represents secondary speed, representsSpeed,Represent that vehicle travels one kilometer of wheel and turns over The number of turns,It represents when front speed ratio,Represent targeted gear speed ratio,Represent lasting shift time,Represent design shift time.
3) speed ratio, shift time and driver are respectively kept off according to gearbox and it is expected that engine output torque determines gearbox target Output torque, the calculation formula of gearbox target output torque are：
WhereinIt represents gearbox target output torque, representsThe desired engine output of driver Torque.
4) vehicle target acceleration is calculated according to gearbox target output torque
5) according to vehicle target acceleration calculation engine target rotating speed, the calculation formula of engine target rotating speed is：
WhereinRepresent engine target rotating speed,Represent engine speed when gearshift starts.
6) target slippage is determined according to engine target rotating speed and target turbine rotating speed, the calculation formula of target slippage is：
WhereinRepresent target slippage.
7) fluid torque-converter rotating speed of target ratio and target torque ratio are determined according to target slippage, rotating speed of target than calculating it is public Formula is：
Represent fluid torque-converter rotating speed of target ratio, fluid torque-converter target torque ratioBy liquid Power torque-converters rotating speed of target ratio and fluid torque-converter indicatrix determine.
8) target engine torque, target are determined according to fluid torque-converter target torque ratio and gearbox target output torque The calculation formula of engine torque is：
WhereinTo meet the target engine torque of gearshift needs.
9) Transmission Control Module sends out torque according to target engine torque obtained above to engine control module Control data, the torque that engine control module asks to need in output shift process according to the moment of torsion control of speed change tank module.
10) Transmission Control Module controls solenoid valve according to target slip control lockup clutch of converter, passes through Oil pressure on lockup clutch of converter solenoid valve control lock-up clutch, in speed than transfer process, secondary speed declines, Target slippage increases, and reduces the oil pressure on lock-up clutch；After speed is than converting, secondary speed rises, and target slippage subtracts Oil pressure on small increase lock-up clutch makes the speed discrepancy between turbine and engine meet target slippage requirement, so as to make hair Motivation rotating speed meets the requirement of target engine speed.
It will be seen that according to above, when speed reaches upshift shifting points, engine control module passes through engine speed Engine speed when sensor signal record gearshift starts, Transmission Control Module record current shift speed ratio and targeted gear Position speed ratio and design gearshift opportunity.In shift process, engine control module is stepped on according to engine rotational speed signal and throttle Partitioned signal determines that driver it is expected torque, and engine rotational speed signal when driver it is expected, torque and gearshift start is sent to change Fast case control module, Transmission Control Module it is expected torque, speed signal, current shift speed ratio, target gear according to driver Speed ratio, design gearshift opportunity and shift duration, the engine target torque for calculating satisfaction gearshift requirement in real time are sent to Engine control module, engine control module are full according to the engine target torque request output that Transmission Control Module is sent out The engine torque of foot gearshift requirement；Transmission Control Module calculates target engine speed in real time simultaneously, target turbine turns Speed, target slippage and lock-up clutch control pressure signal, lock-up clutch pressure-control valve is according to lock-up clutch pressure Control signal output lock-up clutch pressure.
Fig. 3 is the shift process schematic diagram of aforementioned embodiments control automobile dynamic system according to the present invention.In Fig. 3 In, reference numeral 1' represents engine speed graph, and 2' represents turbine speed curves, and 3' represents engine torque curve.From figure In it will be seen that, under automobile dynamic system control method of the invention can effectively keep during upshift engine speed not Drop by controlling the pressure of engine output torque and lockup clutch of converter in shift process, turns engine Speed is maintained in a constant range, so as to which driver will not perceive shift process by the variation of engine speed；Together When due in shift process engine speed do not reduce, so influence of the inertia torque to gearshift can be effectively reduced, reduce Drop in shift process turns round demand, farthest reduces shift shock.
If the preceding description carried out with reference to the accompanying drawings to the preferred embodiment of the present invention is only exemplary and illustrative；It is affiliated The technical staff in field can also carry out the preferred embodiment of the present invention equivalent or similar type under the teaching of this paper Flexible or remodeling, these flexible or remodeling will be also fallen into the protection domain covered by claims of the present invention.
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| JP4461997B2 (en) * | 2004-10-12 | 2010-05-12 | 日産自動車株式会社 | Engine control device |
| JP4251182B2 (en) * | 2006-01-13 | 2009-04-08 | トヨタ自動車株式会社 | Vehicle control device |
| US8060286B2 (en) * | 2008-08-06 | 2011-11-15 | GM Global Technology Operations LLC | Torque converter clutch control |
| US8308611B2 (en) * | 2010-01-22 | 2012-11-13 | GM Global Technology Operations LLC | Shift control systems and methods for an automatic transmission |
| US8821344B2 (en) * | 2011-06-08 | 2014-09-02 | Ford Global Technologies, Llc | Controlling a transmission skip change upshift |
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