WO2013073395A1 - 自動変速機の制御装置 - Google Patents
自動変速機の制御装置 Download PDFInfo
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- WO2013073395A1 WO2013073395A1 PCT/JP2012/078571 JP2012078571W WO2013073395A1 WO 2013073395 A1 WO2013073395 A1 WO 2013073395A1 JP 2012078571 W JP2012078571 W JP 2012078571W WO 2013073395 A1 WO2013073395 A1 WO 2013073395A1
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- shift
- automatic transmission
- gear
- shift stage
- piston
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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
- F16H61/02—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 the signals used
- F16H61/0262—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 the signals used the signals being hydraulic
- F16H61/0265—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 the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
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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
- F16H61/08—Timing control
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/02—Selector apparatus
- F16H59/04—Ratio selector apparatus
- F16H59/045—Ratio selector apparatus consisting of fluid valves
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/74—Inputs being a function of engine parameters
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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
- F16H61/06—Smoothing ratio shift by controlling rate of change of fluid pressure
- F16H61/061—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means
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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
- F16H61/68—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 specially adapted for stepped gearings
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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
- F16H61/68—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 specially adapted for stepped gearings
- F16H61/684—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 specially adapted for stepped gearings without interruption of drive
- F16H61/686—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 specially adapted for stepped gearings without interruption of drive with orbital gears
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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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/68—Inputs being a function of gearing status
- F16H2059/6807—Status of gear-change operation, e.g. clutch fully engaged
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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
- F16H2306/00—Shifting
- F16H2306/24—Interruption of shift, e.g. if new shift is initiated during ongoing previous shift
Definitions
- the present invention relates to a control device for an automatic transmission that includes a frictional engagement element that is controlled from an engaged state to a released state by shift control.
- An object of the present invention is to provide a control device for an automatic transmission that can prevent occurrence of a shock or racing when a shift is performed to return the shift stage after the shift control is completed.
- the present invention is a control device for an automatic transmission that includes a first frictional engagement element that is engaged at a first speed and released at a second speed.
- Piston stroke return determination means for detecting a released state of the piston pressing the friction plate of the first friction engagement element; After the shift from the first gear to the second gear is completed, the execution of the shift from the second gear to the first gear is limited until it is determined that the piston is in a predetermined release state.
- Shift start determination means Is provided.
- the first gear after the shift from the first gear to the second gear is completed, the first gear from the second gear until the piston is determined to be in a predetermined release state. Execution of shifting to the shift stage is restricted. That is, in the shift from the first gear to the second gear, the first friction engagement element that is engaged at the first gear and released at the second gear is controlled from the engaged state to the released state. On the other hand, in the shift from the second shift stage to the first shift stage (that is, shift control for returning the shift stage), the first friction engagement element is controlled from the released state to the engaged state.
- the shift from the first gear to the second gear is completed, there is variation in the released state of the piston that presses the friction plate of the first friction engagement element.
- the shift from the second shift stage to the first shift stage (that is, shift control for returning the shift stage) is executed, thereby completing the previous shift. It is possible to execute the next shift after eliminating the unevenness of the piston release state that sometimes occurs.
- the precharge hydraulic pressure for supplying the first friction engagement element is supplied, the supply hydraulic pressure is too large, and a fastening shock is generated. Therefore, it is possible to prevent the occurrence of overshooting.
- 1 is an overall system diagram illustrating a configuration of a power train of a vehicle to which an automatic transmission control device of an embodiment is applied. It is a flowchart which shows the flow of the shift start judgment process performed with the AT controller of an Example. It is a figure which shows an example of the hydraulic pressure-speed map which shows the piston stroke speed with respect to command hydraulic pressure. It is a figure which shows each characteristic of the command oil pressure and actual pressure in a target gear stage, an actual gear stage, throttle opening, an estimated stroke rate, and a 1st friction engagement element when the shift start judgment processing of an Example is performed.
- the configuration of the automatic transmission control device according to the embodiment will be described by dividing it into an “overall system configuration” and a “shift start determination processing configuration”.
- FIG. 1 is an overall system diagram showing a configuration of a power train of a vehicle to which an automatic transmission control device of an embodiment is applied.
- the vehicle power train in the embodiment has an engine 1, a torque converter 2, and an automatic transmission 3, as shown in FIG.
- the engine 1 is a gasoline engine or a diesel engine, and its output is adjusted by a throttle valve whose opening increases from fully closed to fully open as the accelerator pedal operated by the driver is depressed.
- the engine output shaft 1 a of the engine 1 is connected to the input shaft 4 of the automatic transmission 3 via the torque converter 2.
- the automatic transmission 3 is a stepped automatic transmission.
- the automatic transmission 3 includes a front planetary gear set (not shown) and a rear planetary gear set (not shown) arranged on the input shaft 4 and the output shaft 5 arranged coaxially, a plurality of frictional engagement elements 6, and the like. And a valve body 7.
- the plurality of frictional engagement elements 6 are operated by hydraulic pressure, and a power transmission path is switched by a combination of engagement and release to realize a desired shift stage.
- Each friction engagement element 6 is controlled to be engaged / slip engaged / released by a control hydraulic pressure generated by the valve body 7 based on a control command from the AT controller 9.
- the plurality of frictional engagement elements 6 include a first frictional engagement element that is engaged at least at the first speed and released at the second speed.
- the “first gear” and the “second gear” are arbitrary gears, for example, the first gear and the second gear, the second gear and the fourth gear, or the second gear. And 1st gear.
- a normally open wet multi-plate clutch or wet multi-plate brake capable of continuously controlling the oil flow rate and hydraulic pressure with a proportional solenoid is used.
- An oil passage (not shown) for supplying hydraulic pressure to each friction engagement element 6 is formed in the valve body 7, and a solenoid 8 driven based on a control command input from the AT controller 9 includes: A pressure regulating valve (not shown) provided in each oil passage is operated to control the oil pressure of the command pressure set by the AT controller 9 to be supplied to a predetermined friction engagement element 6. Further, when the vehicle is traveling, the hydraulic pressure is controlled so as to be supplied only to the frictional engagement element 6 necessary for obtaining a desired gear position.
- the AT controller 9 performs a shift to a shift stage that is automatically set based on a shift map (not shown) in accordance with a traveling state obtained from the vehicle speed, the accelerator opening, the throttle opening, and the like. That is, the AT controller 9 supplies the frictional engagement element 6 to be engaged based on outputs from the engine rotation sensor 10, the throttle opening sensor 11, the turbine rotation sensor 12, the output shaft rotation sensor 13, the inhibitor switch 14, and the like. Determine the operating oil pressure command. Then, a command for driving the solenoid 8 is output so that the hydraulic pressure of the determined command pressure is supplied to the frictional engagement element 6 to be engaged, and a discharge command for discharging the hydraulic oil from the frictional engagement element 6 to be released. Is output.
- the engine rotation sensor 10 detects the rotation of the output shaft of the engine 1 and outputs a signal indicating the detected rotation speed of the output shaft (engine rotation speed Ne) to the AT controller 9.
- the throttle opening sensor 11 detects the opening of the throttle valve of the engine 1 and outputs a signal indicating the detected opening of the throttle valve (throttle opening Tvo) to the AT controller 9.
- the turbine rotation sensor 12 outputs the rotation of the input shaft 4 of the automatic transmission 3 and outputs a signal indicating the rotation speed of the input shaft 4 (turbine rotation speed Nt) to the AT controller 9.
- the output shaft rotation sensor 13 outputs the rotation of the output shaft 5 of the automatic transmission 3 and outputs a signal indicating the rotation speed of the output shaft 5 (output shaft rotation speed No) to the AT controller 9.
- the inhibitor switch 14 outputs a signal indicating a selection range of a shift selection mechanism (not shown) to the AT controller 9.
- the AT controller 9 determines whether or not the latter shift control is possible when there is a request for the shift control with the target shift stage as the original shift stage during a certain shift control or after completion of the certain shift control. To do. That is, the AT controller 9 presses the friction plate of the first friction engagement element that is engaged at the first speed and released at the second speed after the shift from the first speed to the second speed. The execution of the shift from the second shift stage to the first shift stage is limited until it is determined that the piston to be released is in the released state. As a result, the shift control for returning the shift stage changed in the previous shift control to the original shift stage is not executed until the piston stroke returns, and the request for the shift control to return to the original shift stage is suspended. The That is, the AT controller 9 delays the start timing of the shift control for returning the gear position until it can be determined that the piston stroke has returned.
- FIG. 2 is a flowchart illustrating a shift start determination process executed by the AT controller according to the embodiment.
- the flow chart shown in FIG. 2 executes the shift from the second shift stage to the first shift stage until it is determined that the piston is in the released state after the shift from the first shift stage to the second shift stage. This corresponds to shift start determination means for limiting the shift.
- shift start determination means for limiting the shift.
- step S1 it is determined whether or not the currently executed shift control from the first shift stage to the second shift stage (hereinafter referred to as “previous shift control”) has been completed. If YES (end of shifting), the process proceeds to step S2. If NO (during shifting), step S1 is repeated.
- the end determination of the previous shift control is determined as the end of the shift if the actual gear stage matches the target gear stage of the shift, and the shift is in progress if the actual gear stage does not match the target gear stage of the shift. Judge.
- step S2 following the determination of the end of the previous shift in step S1, the shift control from the second shift stage to the first shift stage (that is, the target shift stage is changed to the original shift stage in the previous shift control). It is determined whether or not there has been a request for execution of the return shift control (hereinafter referred to as “shift control for returning the shift stage”). If YES (shift request is present), the process proceeds to step S3. If NO (shift request is not requested), the shift start determination routine is terminated.
- step S3 following the determination that there is a shift request in step S2, the stroke rate of the piston that presses the friction plate of the first friction engagement element that is engaged at the first shift stage and released at the second shift stage is calculated.
- the “stroke rate” is a value indicating the ratio of the distance that the piston has moved in the possible stroke distance of the piston, and is expressed as a percentage.
- the fully open state (completely released state) is set to 0%, and the fully closed state (completely connected state) is set to 100%.
- the stroke rate is zero, it is determined that the piston stroke has returned.
- the map hydroaulic-speed map; refer FIG.
- step S4 following the calculation of the stroke rate in step S3, it is determined whether or not the calculated stroke rate is greater than a preset stroke threshold. If YES (stroke rate> stroke threshold), the process proceeds to step S5. If NO (stroke rate ⁇ stroke threshold), the process proceeds to step S10.
- the “stroke threshold” is a stroke rate at which it can be determined that the piston is in a released state, and is a value that the piston stroke has returned. Although an arbitrary value is set in advance, it is set to zero here.
- This step S3 corresponds to piston stroke return determination means for detecting the released state of the piston that presses the friction plate of the first friction engagement element.
- step S5 following the determination that stroke rate> stroke threshold in step S4, the throttle valve opening (throttle opening Tvo) of engine 1 is detected, and the process proceeds to step S6.
- the throttle opening degree Tvo is detected by the throttle opening degree sensor 11 as described above.
- step S6 following the detection of the throttle opening Tvo in step S5, it is determined whether or not the detected throttle opening Tvo is less than the throttle threshold. If YES (throttle opening ⁇ throttle threshold), the process proceeds to step S7. If NO (throttle opening ⁇ throttle threshold), the process proceeds to step S10.
- the “throttle threshold value” is a value that can be determined that the driver's required driving force is relatively high, and is set to an arbitrary value in advance.
- step S7 following the determination that throttle opening ⁇ throttle threshold in step S6, the input torque input to the automatic transmission 3 is estimated, and the process proceeds to step S8.
- the “input torque” is estimated based on, for example, the accelerator opening, engine speed, engine output possible torque, and the like.
- This step S7 corresponds to input torque estimating means for estimating the input torque to the automatic transmission 3.
- step S8 following the estimation of the input torque in step S7, it is determined whether or not the estimated input torque is less than the torque threshold. If YES (input torque ⁇ torque threshold), the process proceeds to step S9. If NO (input torque ⁇ torque threshold), the process proceeds to step S10.
- the “torque threshold value” is a value with which it can be determined that the required driving force of the driver is relatively high, and is set to an arbitrary value in advance.
- step S9 following the determination of input torque ⁇ torque threshold value in step S8, it is determined whether a predetermined time has elapsed since the timing at which the previous shift control determined in step S1 was completed. If YES (predetermined time has elapsed), the process proceeds to step S10. If NO (predetermined time has not elapsed), the process returns to step S3.
- the “predetermined time” is a time during which it can be determined that the piston in the first frictional engagement element is in the released state, and is set to an arbitrary value in advance.
- step S10 it is determined whether stroke rate ⁇ stroke threshold in step S4, or throttle opening ⁇ throttle threshold in step S6, or input torque ⁇ torque threshold in step S8, or Based on one of the determinations that the predetermined time has elapsed in step S9, a shift control for returning the requested gear in step S2, that is, a gear shift control from the second gear to the first gear is executed. Then, the routine ends.
- FIG. 4 shows the target gear stage, actual gear stage, throttle opening, stroke rate in the first friction engagement element, command oil pressure and actual pressure in the first friction engagement element when the shift start determination process of the embodiment is executed. It is a figure which shows each characteristic.
- the target gear stage is changed from the first gear stage (for example, second gear) to the second gear stage (for example, first gear), and a downshift request is output.
- the first frictional engagement element that is engaged at the first speed and released at the second speed is changed from the engagement control to the release control.
- step S1 is repeated, the upshift request is limited, and the upshift is not executed.
- step S1 the first shift stage (for example, the second speed stage) to the second shift stage (for example, the first speed stage), and when the previous shift control (downshift shift) is completed.
- step S2 the process proceeds from step S2 to step S3, and the stroke rate in the first friction engagement element is calculated.
- step S4 the stroke rate in the first friction engagement element exceeds the stroke threshold (here, zero). Therefore, the process proceeds from step S4 to step S5, and the throttle opening is detected.
- the throttle opening is below the throttle threshold. Therefore, the process proceeds from step S6 to step S7, and the input torque to the automatic transmission 3 is estimated. And if the input torque estimated from the accelerator opening etc. is less than a torque threshold value at the time t7, it will progress to step S8-> step S9.
- the stroke rate in the first frictional engagement element is not zero. For this reason, as shown by a two-dot chain line in FIG. 4, the stroke rate immediately increases and the piston stroke returns too much. For this reason, there is a risk that a fastening shock may occur due to sudden fastening when the precharge hydraulic pressure is supplied. Also, if the precharge time is shortened in anticipation that the stroke rate at the first frictional engagement element is not zero, or if the precharge hydraulic pressure is set to a low value, the rate of increase of the stroke rate becomes slow and the engagement is It is possible that the engine will blow up due to a delay.
- the stroke rate in the first friction engagement element has reached the stroke threshold (here, zero) at time t8, so that step S3 is performed.
- the stroke threshold here, zero
- the first frictional engagement element that is engaged at the first speed and released at the second speed among the plurality of frictional engagement elements 6 is changed from the release control to the engagement control. Control changed.
- a command hydraulic pressure for supplying a precharge hydraulic pressure for filling the first friction engagement element is output, and the actual pressure starts to increase in accordance with the command hydraulic pressure.
- the stroke rate in the first frictional engagement element is zero at time t8, and the piston in the first frictional engagement element is completely released. Therefore, the engagement control of the first friction engagement element can be started from a state where the piston stroke is completely returned. That is, it is possible to prevent variations in the released state of the pistons and prevent the supply hydraulic pressure from being too large and causing a fastening shock, or being too small and causing a blow-up.
- step S1 if the throttle opening Tvo exceeds the throttle threshold before the stroke rate exceeds the stroke threshold, step S1 ⁇ step S2 ⁇ It progresses to step S3-> step S4-> step S5-> step S6-> step S10.
- step S3-> step S4-> step S5-> step S6-> step S10 if the throttle opening Tvo exceeds the throttle threshold before the stroke rate exceeds the stroke threshold, step S1 ⁇ step S2 ⁇ It progresses to step S3-> step S4-> step S5-> step S6-> step S10.
- step S1 in the flowchart shown in FIG. Step S2 ⁇ Step S3 ⁇ Step S4 ⁇ Step S5 ⁇ Step S6 ⁇ Step S7 ⁇ Step S8 ⁇ Step S10
- An automatic transmission control device including a first frictional engagement element that is engaged at a first speed and released at a second speed, Piston stroke return determination means (step S4) for detecting a released state of the piston pressing the friction plate of the first friction engagement element; After the shift from the first gear to the second gear is completed, the execution of the shift from the second gear to the first gear is limited until it is determined that the piston is in a predetermined release state. Shift start determining means (FIG. 4); It was set as the structure provided with. For this reason, it is possible to prevent the occurrence of shock and racing when executing a shift to return the shift stage after the shift control is completed.
- step S8 for estimating the input torque to the automatic transmission 3;
- the shift start determining means (FIG. 4) responds to a shift request from the second shift stage to the first shift stage in response to the first shift stage.
- the shift from the second gear to the first gear is executed before determining that the piston is in the released state. For this reason, when it can be determined that the driver's required driving force is large, even if it is before it is determined that the first frictional engagement element is released, the shift control for returning the gear position is executed, thereby satisfying the driver's request. Shift control responding with good response can be performed.
- the calculated stroke rate is used as a determination criterion, but the present invention is not limited to this.
- a map of a stroke rate with respect to a time when a predetermined command oil pressure is supplied in advance may be provided, and the time and the command oil pressure may be used as determination criteria.
- the automatic transmission 3 is mounted on the engine vehicle that uses the engine 1 as a travel drive source.
- the present invention can also be applied to an electric vehicle that is a traveling drive source.
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Abstract
Description
このような変速中に目標変速段の変更要求があった場合の制御に関する従来技術として、変速判断から実変速の開始、つまりイナーシャフェーズ開始までに走行条件(例えば、スロットル開度等)の変化によって目標変速段の変更要求があった場合には目標変速段の変更を許可するが、イナーシャフェーズ開始後は目標変速段の変更を禁止して、変速中の変速を完了するようにした自動変速機の制御装置が知られている(例えば、特許文献1参照)。
すなわち、先の変速制御で解放された摩擦締結要素は、変速段を戻す変速制御を実行すると締結制御される。ここで、先の変速制御で解放された摩擦締結要素では、変速終了時のピストンの解放状態にばらつきある。そのため、変速制御終了と同時に変速段を戻す変速制御を実行すると、推定したピストン解放状態よりも実際の解放量が小さいとき(ピストンストロークが想定よりも戻っていないとき)には、がた詰めのためのプリチャージ油圧の供給時に急締結となって締結ショックが生じてしまう。また、推定したピストン解放状態よりも実際の解放量が大きいとき(ピストンストロークが想定以上に戻りすぎているとき)には、プリチャージ油圧が小さすぎて締結遅れになりエンジンの吹け上がりが発生してしまう。
前記第1摩擦締結要素の摩擦板を押圧するピストンの解放状態を検出するピストンストローク戻り判定手段と、
前記第1変速段から前記第2変速段への変速終了後、前記ピストンが所定の解放状態であると判定するまで、前記第2変速段から前記第1変速段への変速の実行を制限する変速開始判断手段と、
を備える。
すなわち、第1変速段から第2変速段への変速において、第1変速段で締結され、第2変速段で解放される第1摩擦締結要素は、締結状態から解放状態へと制御される。一方、第2変速段から第1変速段への変速(つまり、変速段を元に戻す変速制御)では、第1摩擦締結要素は解放状態から締結状態へと制御される。
しかしながら、第1変速段から第2変速段への変速終了時、第1摩擦締結要素の摩擦板を押圧するピストンの解放状態にはバラツキが生じている。そのため、ピストンが所定の解放状態であると判定してから、第2変速段から第1変速段への変速(つまり、変速段を元に戻す変速制御)を実行することで、先の変速終了時に生じているピストン解放状態のバラツキを解消してから次の変速を実行することができる。
これにより、変速制御終了後に変速段を戻す変速を実行する際、第1摩擦締結要素のがた詰めのためのプリチャージ油圧の供給時に、供給油圧が大きすぎて締結ショックが発生したり、小さすぎて吹け上がりが発生したりする等を防止することができる。
図1は、実施例の自動変速機の制御装置が適用された車両のパワートレインの構成を示す全体システム図である。
前記複数の摩擦締結要素6は、少なくとも第1変速段で締結され、第2変速段で解放される第1摩擦締結要素を備える。なお、「第1変速段」及び「第2変速段」とは任意の変速段であり、例えば1速段と2速段であったり、2速段と4速段であったり、2速段と1速段であったりする。
そして、各摩擦締結要素6としては、例えば、比例ソレノイドで油流量および油圧を連続的に制御できるノーマルオープンの湿式多板クラッチや湿式多板ブレーキが用いられる。
前記スロットル開度センサ11は、エンジン1のスロットルバルブの開度を検出し、検出したスロットルバルブの開度(スロットル開度Tvo)を示す信号を、ATコントローラ9に出力する。
前記タービン回転センサ12は、自動変速機3の入力軸4の回転を出力し、入力軸4の回転数(タービン回転数Nt)を示す信号を、ATコントローラ9に出力する。
前記出力軸回転センサ13は、自動変速機3の出力軸5の回転を出力し、出力軸5の回転数(出力軸回転数No)を示す信号を、ATコントローラ9に出力する。
前記インヒビタスイッチ14は、図示しないシフト選択機構の選択レンジを示す信号を、ATコントローラ9に出力する。
つまり、このATコントローラ9は、第1変速段から前記第2変速段への変速終了後、第1変速段で締結され、第2変速段で解放される第1摩擦締結要素の摩擦板を押圧するピストンが解放状態であると判定するまで、第2変速段から第1変速段への変速の実行を制限する。これにより、ピストンストロークが戻った状態になるまで、先の変速制御で変更した変速段を、元の変速段に戻す変速制御は実行されず、元の変速段とする変速制御の要求は保留される。
すなわち、このATコントローラ9では、ピストンストロークが戻ったと判断できるまでは、変速段を元に戻す変速制御の開始タイミングを遅らせる。
図2は、実施例のATコントローラにて実行される変速開始判断処理の流れを示すフローチャートである。なお、この図2に示すフローチャートが、第1変速段から第2変速段への変速終了後、ピストンが解放状態であると判定するまで、第2変速段から第1変速段への変速の実行を制限する変速開始判断手段に相当する。以下、図2に示す各ステップについて説明する。
ここで、先の変速制御の終了判断は、実ギヤ段が変速の目標ギヤ段と一致していれば変速終了と判断し、実ギヤ段が変速の目標ギヤ段と一致していなかったら変速中と判断する。
ここで、「ストローク率」は、ピストンのストローク可能距離において、ピストンが移動した距離の割合を示す値であり、百分率で示す。全開状態(完全解放状態)をゼロ%とし、全閉状態(完全締結状態)を100%とする。本実施例では、このストローク率がゼロのとき、ピストンのストロークが戻った状態であると判断する。
そして、このストローク率を求めるには、予め、指令油圧ごとに決まるピストンストローク速度を示すマップ(油圧-速度マップ;図3参照)を作成する。この油圧-速度マップを作成するには、まず、ピストンのストローク可能距離を把握する。次に、第1摩擦締結要素への指令油圧ごとの完全解放時間を測定する。そして、ストローク可能距離と指令油圧ごとの完全解放時間とから解放方向へのピストンストローク速度を算出し、油圧-速度マップを作成する。
そして、この油圧-速度マップと、指令油圧値と、指令時間とから、解放方向へピストンが移動した距離を算出する。最後に、ピストンのストローク可能距離に対する移動距離を百分率で算出し、ストローク率とする。
ここで、「ストローク閾値」とは、ピストンが解放状態であると判定できるストローク率であり、ピストンストロークが戻ったとする値である。予め任意の値に設定するが、ここではゼロとする。なお、このステップS3が、第1摩擦締結要素の摩擦板を押圧するピストンの解放状態を検出するピストンストローク戻り判定手段に相当する。
スロットル開度Tvoは、前述したように、スロットル開度センサ11により検出する。
ここで、「スロットル閾値」は、運転者の要求駆動力が比較的高いと判断できる値であり、予め任意の値に設定する。
ここで、「入力トルク」は、例えばアクセル開度やエンジン回転数、エンジン出力可能トルク等に基づいて推定する。なお、このステップS7が、自動変速機3への入力トルクを推定する入力トルク推定手段に相当する。
ここで、「トルク閾値」は、運転者の要求駆動力が比較的高いと判断できる値であり、予め任意の値に設定する。
ここで、「所定時間」とは、第1摩擦締結要素におけるピストンが確実に解放状態であると判定できる時間であり、予め任意の値に設定する。
図4は、実施例の変速開始判断処理を実行したときの、目標ギヤ段・実ギヤ段・スロットル開度・第1摩擦締結要素におけるストローク率・第1摩擦締結要素における指令油圧と実圧の各特性を示す図である。
また、第1摩擦締結要素におけるストローク率がゼロではないことを見込んでプリチャージ時間を短くしたり、又は、プリチャージ油圧を低い値に設定した場合では、ストローク率の上昇速度が遅くなって締結遅れになりエンジンの吹け上がりが発生してしまうことが考えられる。
このとき、時刻t8時点で第1摩擦締結要素におけるストローク率はゼロであり、第1摩擦締結要素におけるピストンが完全に解放した状態である。そのため、第1摩擦締結要素の締結制御は、ピストンストロークが完全に戻った状態から始めることができる。すなわち、ピストンの解放状態のバラツキがなくなり、供給油圧が大きすぎて締結ショックが発生したり、小さすぎて吹け上がりが発生したりする等を防止することができる。
このため、スロットル開度Tvoが大きく、運転者の要求駆動力が高いと判断される場合には、レスポンスよく運転者の要求に応えることができる。
このため、自動変速機3への入力トルクが大きく、運転者の要求駆動力が高いと判断される場合には、レスポンスよく運転者の要求に応えることができる。
実施例の自動変速機の制御装置にあっては、下記に列挙する効果を得ることができる。
前記第1摩擦締結要素の摩擦板を押圧するピストンの解放状態を検出するピストンストローク戻り判定手段(ステップS4)と、
前記第1変速段から前記第2変速段への変速終了後、前記ピストンが所定の解放状態であると判定するまで、前記第2変速段から前記第1変速段への変速の実行を制限する変速開始判断手段(図4)と、
を備える構成とした。
このため、変速制御終了後に変速段を戻す変速を実行する際、ショックや吹け上がりの発生を防止することができる。
前記ピストンが所定の解放状態であると判定したときに、前記第2変速段から前記第1変速段への変速を実行する構成とした。
このため、変速制御終了後に変速段を戻す変速を実行する際、ショックや吹け上がりの発生を防止することができる。
前記変速開始判断手段(図4)は、前記入力トルクが所定値(入力閾値)以上のときには、前記第2変速段から前記第1変速段への変速要求に応答して、前記第1変速段から前記第2変速段への変速終了後、前記ピストンが解放状態であると判定する前に、前記第2変速段から前記第1変速段への変速を実行する構成とした。
このため、運転者の要求駆動力が大きいと判断できるときには、第1摩擦締結要素が解放したと判定される前であっても変速段を戻す変速制御を実行することで、運転者の要求にレスポンスよく応える変速制御を行うことができる。
Claims (6)
- 第1変速段で締結され、第2変速段で解放される第1摩擦締結要素を備えた自動変速機の制御装置であって、
前記第1摩擦締結要素の摩擦板を押圧するピストンの解放状態を検出するピストンストローク戻り判定手段と、
前記第1変速段から前記第2変速段への変速終了後、前記ピストンが所定の解放状態であると判定するまで、前記第2変速段から前記第1変速段への変速の実行を制限する変速開始判断手段と、
を備える自動変速機の制御手段。 - 請求項1に記載された自動変速機の制御手段において、
前記変速開始判断手段は、前記ピストンが所定の解放状態であると判定する前に、前記第2変速段から前記第1変速段への変速要求があったときには、
前記ピストンが所定の解放状態であると判定したときに、前記第2変速段から前記第1変速段への変速を実行する自動変速機の制御装置。 - 請求項1又は請求項2に記載された自動変速機の制御装置において、
自動変速機への入力トルクを推定する入力トルク推定手段を備え、
前記変速開始判断手段は、前記入力トルクが所定値以上のときには、前記第2変速段から前記第1変速段への変速要求に応答して、前記第1変速段から前記第2変速段への変速終了後、前記ピストンが解放状態であると判定する前に、前記第2変速段から前記第1変速段への変速を実行する自動変速機の制御装置。 - 請求項1又は請求項2に記載された自動変速機の制御装置において、
エンジンのスロットル開度を検出するスロットル開度検出手段を備え、
前記変速開始判断手段は、前記スロットル開度が所定値以上のときには、前記第2変速段から前記第1変速段への変速要求に応答して、前記第1変速段から前記第2変速段への変速終了後、前記ピストンが解放状態であると判定する前に、前記第2変速段から前記第1変速段への変速を実行する自動変速機の制御装置。 - 請求項1又は請求項2に記載された自動変速機の制御装置において、
前記ピストンストローク戻り判定手段は、前記第1摩擦締結要素の解放制御における指令油圧値と指令時間とから前記ピストンのストローク率を求め、このストローク率に基づいて所定の解放状態であるか否かを判定する自動変速機の制御装置。 - 請求項5に記載された自動変速機の制御装置において、
前記ピストンストローク戻り判定手段は、指令油圧とピストンストローク速度との関係を定めた油圧-速度マップを有し、この油圧-速度マップを用いて前記ストローク率を求める自動変速機の制御装置。
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EP12849227.9A EP2781799B1 (en) | 2011-11-18 | 2012-11-05 | Device for controlling automatic transmission |
KR1020147016168A KR101602590B1 (ko) | 2011-11-18 | 2012-11-05 | 자동 변속기의 제어 장치 |
CN201280056112.8A CN103946599B (zh) | 2011-11-18 | 2012-11-05 | 自动变速器的控制装置 |
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JP2924711B2 (ja) * | 1995-05-12 | 1999-07-26 | アイシン・エィ・ダブリュ株式会社 | 自動変速機の制御装置 |
JP3476278B2 (ja) | 1995-07-07 | 2003-12-10 | 三菱自動車工業株式会社 | 自動変速機の変速制御方法 |
DE19714852C1 (de) * | 1997-04-10 | 1998-08-13 | Zahnradfabrik Friedrichshafen | Verfahren zur Erhöhung der Spontanität eines elektrohydraulisch gesteuerten Automatikgetriebes |
DE19722954C1 (de) * | 1997-05-31 | 1998-06-10 | Zahnradfabrik Friedrichshafen | Erhöhung der Spontanität eines Automatgetriebes |
JP3938839B2 (ja) * | 2000-09-18 | 2007-06-27 | ジヤトコ株式会社 | 自動変速機のピストンストローク終了判断装置 |
KR100391435B1 (ko) * | 2000-12-27 | 2003-07-12 | 현대자동차주식회사 | 자동 변속기의 마찰요소 필 타임 검출 방법 및 시스템 |
JP4522465B2 (ja) * | 2008-06-11 | 2010-08-11 | ジヤトコ株式会社 | 自動変速機の油圧制御装置 |
JP4787293B2 (ja) * | 2008-06-19 | 2011-10-05 | ジヤトコ株式会社 | 自動変速機の変速制御装置 |
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JP2007170638A (ja) * | 2005-12-26 | 2007-07-05 | Jatco Ltd | 自動変速機の制御装置 |
JP2008064240A (ja) * | 2006-09-08 | 2008-03-21 | Toyota Motor Corp | 自動変速機の制御装置、制御方法およびその方法をコンピュータに実現させるプログラムならびにそのプログラムを記録した記録媒体 |
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US20150006044A1 (en) | 2015-01-01 |
EP2781799A1 (en) | 2014-09-24 |
EP2781799B1 (en) | 2018-01-10 |
EP2781799A4 (en) | 2016-12-14 |
US9347551B2 (en) | 2016-05-24 |
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KR101602590B1 (ko) | 2016-03-10 |
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