WO2013145974A1 - 無段変速機及びその油圧制御方法 - Google Patents
無段変速機及びその油圧制御方法 Download PDFInfo
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- WO2013145974A1 WO2013145974A1 PCT/JP2013/054414 JP2013054414W WO2013145974A1 WO 2013145974 A1 WO2013145974 A1 WO 2013145974A1 JP 2013054414 W JP2013054414 W JP 2013054414W WO 2013145974 A1 WO2013145974 A1 WO 2013145974A1
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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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66231—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 continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed
- F16H61/66236—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 continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed using electrical or electronical sensing or 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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66231—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 continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed
- F16H61/6624—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 continuously variable gearings with endless flexible members controlling shifting exclusively as a function of speed using only hydraulical and mechanical sensing or control means
-
- 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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66254—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 continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
- F16H61/66259—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 continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using electrical or electronical sensing or 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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66272—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 continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
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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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H61/66272—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 continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
- F16H2061/66277—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 continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing by optimising the clamping force exerted on the endless flexible member
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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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
- F16H2061/6629—Detection of slip for determining level of wear
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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
- F16H61/66—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 continuously variable gearings
-
- 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
- F16H61/66—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 continuously variable gearings
- F16H61/662—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 continuously variable gearings with endless flexible members
Definitions
- the present invention relates to hydraulic control of a continuously variable transmission.
- CVT continuously variable transmission
- a gear ratio is changed steplessly by changing a width of a groove of both pulleys.
- a low reverse shift is performed in which the gear ratio is changed toward the lowest level during deceleration, thereby ensuring the re-startability of the vehicle (JP63-74736A).
- One way to improve the fuel efficiency of vehicles equipped with CVT is to reduce the size of the oil pump that is the hydraulic power source of the transmission. If the oil pump is downsized, the engine power consumed to drive the oil pump will be reduced, and the oil pump and transmission internal friction will be reduced by reducing the discharge pressure of the oil pump. Can be improved.
- FIG. 6 shows a state in which the brake pedal is depressed at time ta, the vehicle decelerates, and Low return shift is performed.
- a required secondary pressure that is a secondary pressure required to maintain the gear ratio is calculated according to the gear ratio of the CVT. Then, the required secondary pressure is converted into the primary balance pressure based on the pressure receiving area ratio between the primary pulley and the secondary pulley (X1 in the figure), and the target primary pressure is calculated by subtracting the necessary differential thrust required for shifting from the primary balance pressure. (X2 in the figure).
- the target primary pressure becomes lower than the primary pressure lower limit determined from the belt slip limit (after time tb)
- the target primary pressure is limited to the primary pressure lower limit (X3 in the figure).
- the required secondary pressure is corrected to increase (X4 in the figure).
- the primary pressure lower limit value is based on a theoretical torque capacity formula (described later), and the minimum pressure is limited to a predetermined value regardless of the running conditions.
- An object of the present invention is to further improve fuel efficiency by reducing the size of an oil pump while improving LOW return performance in a continuously variable transmission that performs Low return shift.
- a primary pulley, a secondary pulley, and a belt wound between them are provided, and a pulley pressing force is supplied to the primary pressure supplied to the primary pulley and the secondary pulley. It is a continuously variable transmission determined by the secondary pressure, and it is determined whether or not a low return shift is performed to change the gear ratio of the continuously variable transmission toward the lowest level when the vehicle is decelerated.
- a continuously variable transmission that calculates a primary pressure actual measurement lower limit value at which the belt actually starts to slide based on a gear ratio of the machine, and sets a lower limit value of the primary pressure target value in the Low return shift to the primary pressure actual measurement lower limit value.
- a machine is provided.
- a primary pulley, a secondary pulley, and a belt wound between them are provided, and a pulley pressing force is supplied to the primary pressure and the secondary pulley supplied to the primary pulley.
- a method of controlling the hydraulic pressure of the continuously variable transmission determined by the secondary pressure, and determining whether or not a low reverse shift is performed to change the gear ratio of the continuously variable transmission toward the lowest level when the vehicle is decelerated.
- a primary pressure actual measurement lower limit value at which the belt actually starts to slip based on a gear ratio of the continuously variable transmission is calculated, and a lower limit value of the primary pressure target value in the low return shift is set as the primary pressure actual measurement lower limit value.
- a hydraulic control method is provided.
- FIG. 1 is a schematic configuration diagram of a continuously variable transmission.
- FIG. 2 is a shift map of the continuously variable transmission.
- FIG. 3 is a flowchart showing the content of the hydraulic pressure drop control during the low return shift.
- FIG. 4 is a table for calculating the required secondary pressure.
- FIG. 5 is a time chart showing a state when the hydraulic pressure lowering control at the time of Low return shifting is performed.
- FIG. 6 is a time chart of the comparative example.
- FIG. 1 shows a schematic configuration of a continuously variable transmission (hereinafter referred to as “CVT”) 1.
- CVT continuously variable transmission
- the primary pulley 2 and the secondary pulley 3 are arranged so that the grooves of both are aligned, and a belt 4 is stretched over the grooves of the pulleys 2 and 3.
- An engine 5 is arranged coaxially with the primary pulley 2, and a torque converter 6 and a forward / reverse switching mechanism 7 are provided between the engine 5 and the primary pulley 2 in order from the engine 5 side.
- the torque converter 6 includes a pump impeller 6a connected to the output shaft of the engine 5, a turbine runner 6b connected to the input shaft of the forward / reverse switching mechanism 7, a stator 6c, and a lock-up clutch 6d.
- the forward / reverse switching mechanism 7 includes a double pinion planetary gear set 7a as a main component, its sun gear is coupled to the turbine runner 6b of the torque converter 6, and the carrier is coupled to the primary pulley 2.
- the forward / reverse switching mechanism 7 further includes a starting clutch 7b that directly connects the sun gear and the carrier of the double pinion planetary gear set 7a, and a reverse brake 7c that fixes the ring gear.
- the starting clutch 7b When the starting clutch 7b is engaged, the input rotation via the torque converter 6 from the engine 5 is directly transmitted to the primary pulley 2, and when the reverse brake 7c is engaged, the input rotation via the torque converter 6 from the engine 5 is reversed. Is transmitted to the primary pulley 2.
- the rotation of the primary pulley 2 is transmitted to the secondary pulley 3 via the belt 4, and the rotation of the secondary pulley 3 is transmitted to the driving wheel (not shown) via the output shaft 8, the gear set 9 and the differential gear device 10.
- one of the conical plates forming the grooves of the primary pulley 2 and the secondary pulley 3 is a fixed conical plate 2a, 3a.
- the other conical plates 2b and 3b are movable conical plates that can be displaced in the axial direction.
- the speed change is performed by changing the groove width of the pulleys 2 and 3 by the differential pressure between the primary pressure Ppri and the secondary pressure Psec, and continuously changing the winding arc diameter of the belt 4 around the pulleys 2 and 3. .
- the primary pressure Ppri and the secondary pressure Psec are controlled by the shift control hydraulic circuit 11 together with the hydraulic pressure supplied to the start clutch 7b that is engaged when the forward travel range is selected and the reverse brake 7c that is engaged when the reverse travel range is selected.
- the shift control hydraulic circuit 11 performs control in response to a signal from the transmission controller 12.
- the transmission controller 12 includes a signal from the input rotation speed sensor 13 that detects the actual input rotation speed Nin of the CVT 1, a signal from the vehicle speed sensor 14 that detects the output rotation speed of the CVT 1, that is, the vehicle speed VSP, and the primary pressure.
- a signal from the primary pressure sensor 15p for detecting Ppri, a signal from the secondary pressure sensor 15s for detecting the secondary pressure Psec, a signal from the accelerator opening sensor 16 for detecting the accelerator opening APO, and a select lever position are detected.
- the selection range signal from the inhibitor switch 17 that performs, the signal from the brake switch 18 that detects whether or not the brake pedal is depressed, and the operating state of the engine 5 from the engine controller 19 that controls the engine 5 (engine speed Ne, engine Torque, fuel injection time, cooling water temperature Signal are inputted regarding MPe etc.).
- the transmission controller 12 sets a target input rotation speed tNin corresponding to the vehicle speed VSP and the accelerator opening APO with reference to the shift map shown in FIG. 2, and the actual input rotation speed Nin follows the target input rotation speed tNin.
- the primary pressure Ppri and the secondary pressure Psec are controlled so that the pulley pressing force necessary for transmitting the input torque of the CVT 1 determined by the engine torque and the torque converter torque ratio is obtained.
- theoretical lower limit value a lower limit value (hereinafter referred to as “theoretical lower limit value”) calculated by the following equation is set for the primary pressure Ppri and the secondary pressure Psec, and the primary pressure Ppri and the secondary pressure Psec are usually theoretical. It is restricted so as not to be lower than the lower limit value.
- Theoretical lower limit (T cos ⁇ ) / (2 ⁇ R) T: Transfer torque ⁇ : Sheave angle of pulley ⁇ : Coefficient of friction between belt and pulley R: Contact radius between belt and pulley
- the primary pressure Ppri can be lowered below the theoretical lower limit value, except immediately before or during a steady shift where the gear ratio does not change.
- the transmission controller 12 performs the hydraulic pressure drop control during the low return shift described below to lower the primary pressure Ppri below the theoretical lower limit value, thereby reducing the LOW return performance of the vehicle on which the CVT 1 is mounted. While improving, it becomes possible to further improve fuel consumption by downsizing the oil pump.
- FIG. 3 is a flowchart showing the contents of the hydraulic pressure drop control during the low return shift performed by the transmission controller 12. The contents of this control and its operation and effects will be described with reference to this.
- the time chart shown in FIG. The time chart shown in FIG. 5 shows a state when the hydraulic pressure drop control is performed at the time of Low return shift.
- the transmission controller 12 determines whether or not a low return shift is being performed. When the accelerator opening is zero and the brake pedal is depressed, or when the accelerator opening is zero and the vehicle deceleration is greater than a predetermined value (when climbing), the transmission controller 12 is in the low return shift. The process proceeds to S2. Otherwise, the process ends.
- the transmission controller 12 determines whether lock-up is in progress.
- the lockup clutch 6d is engaged when the vehicle speed VSP becomes higher than a predetermined lockup start vehicle speed, and is released when the vehicle speed VSP becomes lower than a predetermined lockup release vehicle speed ( ⁇ lockup start vehicle speed). Based on this, it can be determined whether the lockup is in progress.
- the process proceeds to S3 and subsequent steps so as to lower the primary pressure Ppri below the primary pressure theoretical lower limit. If it is determined that the lock-up is not being performed, the process proceeds to S9 in order to return the primary pressure Ppri, which has been lowered below the primary theoretical lower limit value in the processes after S3, to the primary pressure theoretical lower limit value.
- the transmission controller 12 calculates the primary pressure theoretical lower limit value.
- the transmission controller 12 calculates the primary pressure actual measurement lower limit value.
- the primary pressure actual measurement lower limit value is a primary pressure Ppri at which the belt 3 actually starts to slide, and is calculated with reference to a map obtained in advance through experiments based on the deceleration and speed ratio of the vehicle.
- the primary pressure actual measurement lower limit value is set to a lower value as the deceleration of the vehicle is larger and the gear ratio is lower.
- the transmission controller 12 calculates the secondary pressure Psec necessary to maintain the gear ratio at that time with reference to the table shown in FIG. Although the required primary pressure is also shown in FIG. 4, it is not used in the hydraulic pressure drop control during the low return shift.
- the transmission controller 12 adds the difference (Y1 in FIG. 5) between the primary pressure theoretical lower limit value and the primary pressure actual measurement lower limit value to the required secondary pressure (Y2 in FIG. 5), and calculates the corrected required secondary pressure. To do. Then, the transmission controller 12 controls the secondary pressure Psec so that the secondary pressure Psec becomes the necessary secondary pressure after correction. Specifically, a solenoid valve that regulates the secondary pressure Psec is controlled.
- the transmission controller 12 detects the actual secondary pressure Psec obtained as a result of controlling the secondary pressure Psec in S ⁇ b> 6 by the secondary pressure sensor 15 s, and compares this with the pressure receiving area ratio of the primary pulley 2 and the secondary pulley 3. Based on this, the primary balance pressure is converted (Y3 in FIG. 5).
- the transmission controller 12 calculates a target primary pressure by subtracting a difference thrust necessary for downshifting (a value obtained by dividing the necessary difference thrust by the pressure receiving area of the primary pulley 2) from the primary balance pressure (FIG. 5). Middle Y4).
- the target primary pressure is lower than the primary pressure theoretical lower limit value, but is higher than the primary pressure actual measurement lower limit value, and thus is not limited by the primary pressure actual measurement lower limit value.
- the transmission controller 12 controls the primary pressure Ppri so that the primary pressure Ppri becomes the target primary pressure. Specifically, a solenoid valve that regulates the primary pressure Ppri is controlled.
- the actual secondary pressure is increased to the necessary secondary pressure after correction. It is possible to reduce the target primary pressure to the primary pressure actual measurement lower limit by changing the primary pressure theoretical lower limit to the primary pressure actual measurement lower limit.
- the primary pressure Ppri for obtaining the required differential thrust from the actual secondary pressure Psec is calculated by increasing the actual secondary pressure until the oil amount balance is actually insufficient. The purpose is to do.
- the actual secondary pressure Psec does not increase to the required secondary pressure after correction due to an actual shortage of the oil balance, but the target primary pressure obtained by subtracting the necessary differential thrust from here is the primary pressure. Since it is higher than the actual measurement lower limit value, the primary pressure Ppri can be lowered to the target primary pressure.
- the secondary pressure at the time of low return shifting can be lowered relatively by lowering the lower limit value of the primary pressure (or a sufficient secondary pressure cannot be secured). This also makes it possible to obtain the differential thrust necessary for gear shifting), thereby reducing the size of the oil pump and improving fuel consumption.
- the necessary differential thrust can be obtained without reducing the primary pressure.
- the primary pressure is reduced to the lower limit even when the oil balance is actually insufficient and the actual secondary pressure Psec does not increase to the required secondary pressure after correction (time t2 to t3 in FIG. 5). By doing so, the necessary differential thrust can be ensured, and the gear ratio of CVT1 can be quickly returned to the lowest level.
- the transmission controller 12 brings the target primary pressure closer to the primary pressure theoretical lower limit value with a predetermined ramp gradient and after correction.
- the required secondary pressure is brought close to the required secondary pressure with a predetermined ramp gradient, thereby controlling the primary pressure theoretical lower limit value and the required secondary pressure, respectively.
- the relative slip between the belt and the pulley is affected by the dynamic friction coefficient between the belt and the pulley even when the lower limit of the primary pressure is lowered during a shift transition where the gear ratio fluctuates.
- the friction coefficient between the belt and the pulley shifts from the dynamic friction coefficient to the static friction coefficient. Since there is a possibility that relative slip occurs between the pulley and the belt, LOW returnability is prevented while preventing the belt 3 from slipping which may be caused by lowering the primary pressure lower limit value below the theoretical value in this region. Can be improved.
- times t3 to t4 correspond.
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Abstract
Description
T:伝達トルク
α:プーリのシーブ角
μ:ベルトとプーリとの間の摩擦係数
R:ベルトとプーリとの接触半径
Claims (6)
- プライマリプーリと、セカンダリプーリと、これらの間に巻き掛けられるベルトとを備え、プーリ押し付け力が前記プライマリプーリに供給されるプライマリ圧及び前記セカンダリプーリに供給されるセカンダリ圧によって決まる無段変速機であって、
車両減速時に前記無段変速機の変速比を最Lowに向けて変更するLow戻し変速を行っているか判断するLow戻し変速判断手段と、
車両の減速度及び前記無段変速機の変速比に基づき前記ベルトが実際に滑り始めるプライマリ圧実測下限値を算出する実測下限値演算手段と、
を備え、
前記Low戻し変速における前記プライマリ圧の目標値の下限値を前記プライマリ圧実測下限値に設定する、
無段変速機。 - 請求項1に記載の無段変速機であって、
前記Low戻し変速を行っていると判断された場合に、
前記無段変速機の変速比を維持するのに必要な必要セカンダリ圧を演算し、
プライマリ圧理論目標値と前記プライマリ圧実測下限値との差分を演算し、
前記必要セカンダリ圧に前記差分を加算することで補正後必要セカンダリ圧を演算し、
実セカンダリ圧が前記補正後必要セカンダリ圧になるように前記実セカンダリ圧を制御し、
前記実セカンダリ圧から目標プライマリ圧を演算する、
無段変速機。 - 請求項2に記載の無段変速機であって、
車速が下がって停車直前若しくは変速比が最ローである状態が検知された後は、前記プライマリ圧を前記プライマリ圧理論下限値に制御する、
無段変速機。 - プライマリプーリと、セカンダリプーリと、これらの間に巻き掛けられるベルトとを備え、プーリ押し付け力が前記プライマリプーリに供給されるプライマリ圧及び前記セカンダリプーリに供給されるセカンダリ圧によって決まる無段変速機の油圧制御方法であって、
車両減速時に前記無段変速機の変速比を最Lowに向けて変更するLow戻し変速を行っているか判断し、
車両の減速度及び前記無段変速機の変速比に基づき前記ベルトが実際に滑り始めるプライマリ圧実測下限値を算出し、
前記Low戻し変速における前記プライマリ圧の目標値の下限値を前記プライマリ圧実測下限値に設定する、
油圧制御方法。 - 請求項4に記載の油圧制御方法であって、
前記Low戻し変速を行っていると判断された場合に、
前記無段変速機の変速比を維持するのに必要な必要セカンダリ圧を演算し、
プライマリ圧理論目標値と前記プライマリ圧実測下限値との差分を演算し、
前記必要セカンダリ圧に前記差分を加算することで補正後必要セカンダリ圧を演算し、
実セカンダリ圧が前記補正後必要セカンダリ圧になるように前記実セカンダリ圧を制御し、
前記実セカンダリ圧から目標プライマリ圧を演算する、
油圧制御方法。 - 請求項5に記載の油圧制御方法であって、
車速が下がって停車直前若しくは変速比が最ローである状態が検知された後は、前記プライマリ圧を前記プライマリ圧理論下限値に制御する、
油圧制御方法。
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KR1020147026548A KR101585368B1 (ko) | 2012-03-28 | 2013-02-21 | 무단 변속기 및 그 유압 제어 방법 |
JP2014507528A JP5903487B2 (ja) | 2012-03-28 | 2013-02-21 | 無段変速機及びその油圧制御方法 |
CN201380013863.6A CN104185752B (zh) | 2012-03-28 | 2013-02-21 | 无级变速器及其液压控制方法 |
US14/387,414 US9133930B2 (en) | 2012-03-28 | 2013-02-21 | Continuously variable transmission and its hydraulic pressure control method |
EP13768782.8A EP2833025A4 (en) | 2012-03-28 | 2013-02-21 | STAGE-FREE TRANSMISSION AND LINE PRESSURE CONTROL PROCEDURE THEREFOR |
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EP (1) | EP2833025A4 (ja) |
JP (1) | JP5903487B2 (ja) |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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KR20190013912A (ko) | 2016-07-01 | 2019-02-11 | 쟈트코 가부시키가이샤 | 하이브리드 차량의 제어 장치 |
WO2020059339A1 (ja) * | 2018-09-21 | 2020-03-26 | ジヤトコ株式会社 | ベルト式無段変速機 |
Families Citing this family (9)
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KR101936535B1 (ko) * | 2015-03-23 | 2019-01-08 | 쟈트코 가부시키가이샤 | 차량 제어 장치 및 차량의 제어 방법 |
JP6547010B2 (ja) * | 2016-01-19 | 2019-07-17 | ジヤトコ株式会社 | 車両の制御装置、及び車両の制御方法 |
JP6414151B2 (ja) * | 2016-07-07 | 2018-10-31 | トヨタ自動車株式会社 | ベルト式無段変速機の制御装置 |
JP6859631B2 (ja) * | 2016-08-29 | 2021-04-14 | 日産自動車株式会社 | 無段変速機の制御方法及び制御装置 |
JP6911711B2 (ja) * | 2017-10-31 | 2021-07-28 | トヨタ自動車株式会社 | 車両用動力伝達装置の制御装置 |
JP7003653B2 (ja) * | 2017-12-27 | 2022-02-10 | トヨタ自動車株式会社 | 車両用動力伝達装置の制御装置 |
JP6879196B2 (ja) * | 2017-12-27 | 2021-06-02 | トヨタ自動車株式会社 | 車両用動力伝達装置の制御装置 |
US10900563B2 (en) * | 2018-06-14 | 2021-01-26 | Kawasaki Jukogyo Kabushiki Kaisha | Utility vehicle |
JP7241124B2 (ja) * | 2021-04-21 | 2023-03-16 | 本田技研工業株式会社 | 車両用無段変速機の制御装置及び制御方法 |
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JP4344380B2 (ja) * | 2006-12-26 | 2009-10-14 | ジヤトコ株式会社 | 無段変速機の制御装置 |
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EP2833028B1 (en) * | 2012-03-28 | 2017-08-23 | Jatco Ltd | Continuously variable transmission and hydraulic pressure control method therefor |
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- 2013-02-21 CN CN201380013863.6A patent/CN104185752B/zh active Active
- 2013-02-21 KR KR1020147026548A patent/KR101585368B1/ko active IP Right Grant
- 2013-02-21 EP EP13768782.8A patent/EP2833025A4/en not_active Withdrawn
- 2013-02-21 WO PCT/JP2013/054414 patent/WO2013145974A1/ja active Application Filing
- 2013-02-21 US US14/387,414 patent/US9133930B2/en active Active
- 2013-02-21 JP JP2014507528A patent/JP5903487B2/ja active Active
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JP2008128370A (ja) * | 2006-11-21 | 2008-06-05 | Jatco Ltd | 無段変速機の制御装置 |
WO2012017536A1 (ja) * | 2010-08-05 | 2012-02-09 | トヨタ自動車株式会社 | 車両用無段変速機の制御装置 |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20190013912A (ko) | 2016-07-01 | 2019-02-11 | 쟈트코 가부시키가이샤 | 하이브리드 차량의 제어 장치 |
US11193584B2 (en) | 2016-07-01 | 2021-12-07 | Jatco Ltd | Hybrid vehicle control device |
WO2020059339A1 (ja) * | 2018-09-21 | 2020-03-26 | ジヤトコ株式会社 | ベルト式無段変速機 |
CN112955681A (zh) * | 2018-09-21 | 2021-06-11 | 加特可株式会社 | 带式无级变速器 |
CN112955681B (zh) * | 2018-09-21 | 2022-01-25 | 加特可株式会社 | 带式无级变速器 |
US11326691B2 (en) | 2018-09-21 | 2022-05-10 | Jatco Ltd | Belt-type continuously variable transmission |
Also Published As
Publication number | Publication date |
---|---|
EP2833025A4 (en) | 2016-07-20 |
EP2833025A1 (en) | 2015-02-04 |
KR101585368B1 (ko) | 2016-01-13 |
US20150081181A1 (en) | 2015-03-19 |
CN104185752B (zh) | 2016-05-11 |
KR20140137382A (ko) | 2014-12-02 |
US9133930B2 (en) | 2015-09-15 |
CN104185752A (zh) | 2014-12-03 |
JP5903487B2 (ja) | 2016-04-13 |
JPWO2013145974A1 (ja) | 2015-12-10 |
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