WO2014156309A1 - 無段変速機の制御装置及び制御方法 - Google Patents
無段変速機の制御装置及び制御方法 Download PDFInfo
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- WO2014156309A1 WO2014156309A1 PCT/JP2014/052552 JP2014052552W WO2014156309A1 WO 2014156309 A1 WO2014156309 A1 WO 2014156309A1 JP 2014052552 W JP2014052552 W JP 2014052552W WO 2014156309 A1 WO2014156309 A1 WO 2014156309A1
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- flow rate
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- hydraulic pressure
- continuously variable
- variable transmission
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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
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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
- F16H61/66254—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
- F16H61/02—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
- 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
- F16H2059/683—Sensing pressure in control systems or in fluid controlled devices, e.g. by pressure sensors
Definitions
- the present invention relates to a control device for a continuously variable transmission that is configured by a belt or chain being wound around a set of pulleys.
- a continuously variable transmission that shifts a belt or chain over a set of pulleys and changes the groove width of the primary pulley and the secondary pulley is generally used.
- These pulleys are composed of a fixed pulley and a movable pulley.
- the movable pulley is provided with a hydraulic cylinder, and the groove width between the fixed pulley and the movable pulley is changed by changing the hydraulic pressure in the hydraulic cylinder.
- the hydraulic pressures regulated by the hydraulic control device are supplied to the hydraulic cylinders of the primary pulley and the secondary pulley, respectively.
- the hydraulic control device controls the hydraulic pressure supplied to each hydraulic cylinder using the hydraulic pressure generated by the hydraulic pump as a source pressure.
- the pressure regulator valve regulates the discharge pressure of the oil pump based on the control signal as the line pressure, and the primary regulator valve controls the line pressure based on the control signal.
- a hydraulic control device for a belt-type continuously variable transmission in which a primary pressure is regulated and a linear solenoid regulates a secondary pressure from a line pressure based on a control signal.
- the primary pressure or secondary pressure is not controlled by the solenoid from the line pressure, but the pilot pressure is regulated by the line pressure, and the pilot pressure (hydraulic pressure) is used without the solenoid.
- the hydraulic pressure is controlled by operating the control valve.
- the hydraulic pressure is controlled by a single control valve using a solenoid.
- the control valve controls the hydraulic pressure by operating a solenoid, and includes a feedback mechanism that circulates the actual hydraulic pressure. Due to such a configuration, when the line pressure that is the source pressure is large, it is necessary to operate the valve against this large hydraulic pressure or large feedback pressure, and the solenoid becomes large and the transmission becomes large. There was a problem.
- the present invention has been made in view of such problems, and provides a control device for a continuously variable transmission that can control the speed ratio of the continuously variable transmission without increasing the size of the device. Objective.
- a continuously variable transmission mechanism that changes a transmission ratio by changing a winding diameter of a belt that is mounted on a pulley and is held by a pulley, by hydraulic pressure supplied to a hydraulic cylinder that is mounted on the pulley.
- a hydraulic pressure supply unit that supplies hydraulic oil at a predetermined hydraulic pressure
- a flow rate control unit that controls a flow rate at which the hydraulic oil supplied by the hydraulic pressure supply unit is supplied to a pulley.
- a flow rate setting means for setting a target hydraulic pressure to be supplied to the hydraulic cylinder and for setting a flow rate of the hydraulic oil to be circulated to the flow rate control unit in order to achieve the target hydraulic pressure.
- a continuously variable transmission that changes the gear ratio by changing the speed, a hydraulic pressure supply section that supplies hydraulic oil at a predetermined hydraulic pressure, and a flow rate when hydraulic oil supplied by the hydraulic pressure supply section is supplied to the hydraulic cylinder.
- the target hydraulic pressure supplied to the hydraulic cylinder is set as the flow rate of the hydraulic oil in the flow rate control unit, and the set flow rate is supplied from the flow rate control unit to the hydraulic cylinder. Since the flow rate is uniquely determined by the cross-sectional area of the opening in the flow rate control unit, it is only necessary to set the flow rate control unit so as to have the cross-sectional area. With this configuration, even when only one control valve is used to control the hydraulic pressure supplied to the hydraulic cylinder, the configuration of the control valve and the like does not increase.
- FIG. 1 is an explanatory diagram showing an example of a configuration of a continuously variable transmission (CVT) according to an embodiment of the present invention.
- FIG. 2 is an explanatory diagram showing the configuration of the hydraulic control apparatus according to the embodiment of the present invention.
- FIG. 3 is an explanatory diagram showing the configuration of the secondary control valve according to the embodiment of the present invention.
- FIG. 4 is an explanatory diagram illustrating functional blocks of the controller according to the embodiment of this invention.
- FIG. 5 is a flowchart of control of the secondary control valve executed by the controller according to the embodiment of the present invention.
- FIG. 1 is an explanatory diagram showing an example of a configuration of a continuously variable transmission (CVT) according to an embodiment of the present invention.
- CVT continuously variable transmission
- the rotation of the crankshaft 11 driven by the engine 1 mounted on the vehicle is transmitted to the continuously variable transmission mechanism 4 via the torque converter 2 and the forward / reverse switching mechanism 3.
- the continuously variable transmission mechanism 4 shifts this rotation, and the rotated rotation is transmitted to the wheels via the final reduction gear 18 so that the vehicle moves forward and backward.
- the torque converter 2 includes a lock-up clutch, and is controlled to a converter state and a lock-up state (slip lock-up) by hydraulic pressure.
- the forward / reverse switching mechanism 3 transmits the rotation of the turbine shaft 6 that is the output shaft of the torque converter 2 to the continuously variable transmission mechanism 4 in the forward (forward) direction, and transmits it in the reverse (reverse) direction.
- a reverse brake By engaging and releasing the forward clutch and the reverse brake with each other, the vehicle can be switched forward and backward, and can be controlled so that the driving force of the engine 1 is not transmitted to the wheels.
- the continuously variable transmission mechanism 4 includes a primary pulley 15 connected to an input shaft 12 that is a rotating shaft on the output side of the forward / reverse switching mechanism 3, and a secondary pulley connected to an output shaft 13 arranged in parallel with the input shaft 12. 16 and a belt-type continuously variable transmission mechanism that includes an endless belt (V-belt) 17 that is stretched between a primary pulley 15 and a secondary pulley 16.
- V-belt endless belt
- the primary pulley 15 includes a fixed pulley (fixed sheave) 15a, and a movable pulley (movable sheave) 15b that is arranged with a sheave surface facing the fixed pulley 15a and forms a V-groove with the fixed pulley. And a hydraulic cylinder 21 provided on the movable pulley 15b for displacing the movable pulley 15b in the axial direction.
- the secondary pulley 16 includes a fixed pulley (fixed sheave) 16a, a movable pulley (movable sheave) 16b, and a hydraulic cylinder 22 provided on the movable pulley 16b to displace the movable pulley 16b in the axial direction.
- the output of the continuously variable transmission mechanism 4 is transmitted to the wheels via the final reduction gear 18 as the rotation of the output shaft 13.
- the hydraulic pressure adjusted by the hydraulic control device 40 is supplied to the hydraulic cylinders 21 and 22.
- the hydraulic control device 40 generates a predetermined line pressure from the hydraulic pressure generated by the oil pump 30, uses the line pressure as a source pressure, and supplies the primary hydraulic pressure Ppri to the hydraulic cylinder 21 of the primary pulley 15 and the hydraulic pressure of the secondary pulley 16.
- the secondary hydraulic pressure Psec supplied to the cylinder 22 is controlled.
- the hydraulic pressure adjusted by the hydraulic control device 40 is supplied to the torque converter 2, the forward / reverse switching mechanism 3, and the like.
- the engagement state of the lockup clutch of the torque converter 2 and the engagement state of the forward clutch and the reverse brake of the forward / reverse switching mechanism 3 are controlled by the supplied hydraulic pressure.
- the hydraulic pressure supplied to the continuously variable transmission mechanism 4 is drained to the oil pan 19 and supplied to the oil pump 30 again.
- the hydraulic pressure is controlled by the following configuration.
- the hydraulic control device 40 is provided with a regulator valve 41 (see FIG. 2) that controls the hydraulic pressure generated by the oil pump 30 to a predetermined line pressure PL.
- the line pressure is supplied not only to the hydraulic cylinders 21 and 22 of the continuously variable transmission mechanism 4 but also to a plurality of friction elements provided in the torque converter 2 and the forward / reverse switching mechanism 3. Is set.
- the hydraulic control device 40 regulates the hydraulic pressure supplied to the hydraulic cylinders 21 and 22 of the continuously variable transmission mechanism 4 using a large line pressure as a source pressure.
- the hydraulic pressure is regulated by hydraulic control valves corresponding to the primary pulley 15 and the secondary pulley 16 respectively.
- the hydraulic control valve includes a spool, a spring, a solenoid, and the like, and controls the hydraulic pressure by changing the position of the spool by operating the solenoid against the biasing force of the spring. Further, the hydraulic control valve is provided with a feedback mechanism that circulates the actual hydraulic pressure. When the line pressure that is the original pressure is large, the feedback mechanism is also enlarged.
- control valve that regulates the pilot pressure which is lower than the line pressure, is not directly controlled by the solenoid from the line pressure, and the hydraulic control valve is operated using the pilot pressure without a solenoid. It was common to control the hydraulic pressure.
- FIG. 2 is an explanatory diagram showing the configuration of the hydraulic control device 40 according to the embodiment of the present invention.
- the hydraulic control device 40 controls a regulator valve 41 that controls the hydraulic pressure generated by the oil pump 30 to a predetermined line pressure PL, and a secondary pressure Psec that is supplied to the hydraulic cylinder 22 of the secondary pulley 16 based on the line pressure PL.
- a secondary control valve 43 that controls the primary pressure Ppri supplied to the hydraulic cylinder 21 of the primary pulley 15 based on the line pressure PL.
- the hydraulic control device 40 includes a controller 45 that controls the operation of the regulator valve 41, the secondary control valve 43, and the primary control valve 42.
- Oil pressure discharged from the oil pump 30 is supplied from the oil passage 401 to the regulator valve 41.
- the regulator valve 41 adjusts the discharge pressure of the oil pump 30 to a predetermined line pressure and supplies it to the oil passage 402.
- the oil passage 402 is provided with a secondary control valve 43 and a primary control valve 42.
- the secondary control valve 43 is controlled by the control of the controller 45 so that the oil passage 404 communicating with the hydraulic cylinder 22 of the secondary pulley 16 has a predetermined secondary pressure Psec.
- a secondary pressure sensor 46 is provided in the oil passage 404.
- the primary control valve 42 is controlled by the controller 45 so that the oil passage 403 communicating with the hydraulic cylinder 21 of the primary pulley 15 becomes a predetermined primary pressure Ppri.
- the oil passage 403 is provided with a primary pressure sensor 47.
- the regulator valve 41 is connected to an oil passage 405 that supplies hydraulic pressure to other parts that require hydraulic pressure, such as the torque converter 2 and the forward / reverse switching mechanism 3.
- the controller 45 acquires signals from the line pressure sensor 44, the secondary pressure sensor 46, and the primary pressure sensor 47.
- the controller 45 controls the regulator valve 41 so that the actual line pressure PLr acquired from the line pressure sensor 44 becomes the required predetermined line pressure PL.
- the controller 45 controls the control signal for the secondary control valve 43 and the primary control valve 42 from the target hydraulic pressure Pt, the gear ratio, etc. based on the target speed ratio determined based on the vehicle speed, the current speed ratio, the acceleration / deceleration request from the driver, and the like. To decide.
- the determined control signal (current value for the solenoid) is supplied to the secondary control valve 43 and the primary control valve 42 to operate them, thereby controlling each hydraulic pressure.
- the secondary control valve 43 and the primary control valve 42 are configured as flow control valves that control the flow rate of the working oil that passes therethrough. Next, the configuration of the secondary control valve 43 will be described as an example.
- FIG. 3 is an explanatory diagram showing the configuration of the secondary control valve 43 according to the embodiment of the present invention.
- the secondary control valve 43 is configured such that a spool 432 is built in a body 431.
- the spool 432 is urged by a spring 433 and is provided with a solenoid 434 for moving the spool 432.
- the solenoid 434 changes the opening degree of the secondary control valve 43 by moving the spool 432 in the axial direction based on a control signal from the controller 45 and controls the flow rate of the passing hydraulic oil.
- An IN port 435, an OUT port 436, and a drain port 437 are formed in the body 431.
- the IN port 435 communicates with the oil passage 402 and is supplied with the line pressure PL.
- the OUT port 436 communicates with the oil passage 404 and communicates with the hydraulic cylinder 22 of the secondary pulley 16.
- the drain port 437 drains the oil pressure of the oil passage 404.
- the secondary control valve 43 When the secondary control valve 43 receives a control signal (indicated current i) from the controller 45 and the solenoid 434 operates to move the spool 432, the IN port 435 and the OUT port 436 communicate with each other.
- the cross-sectional area of the opening portion of the communicating passage changes.
- the flow rate of the hydraulic oil passing through the secondary control valve 43 is determined by the cross-sectional area and the line pressure.
- the controller 45 controls the secondary control valve 43 by the following operation to control the hydraulic pressure supplied to the hydraulic cylinder 22 of the secondary pulley 16.
- FIG. 4 is an explanatory diagram illustrating functional blocks of the controller 45 according to the embodiment of this invention.
- the controller 45 determines the target oil pressure Pt based on the target gear ratio of the continuously variable transmission mechanism 4, and determines the command current i to be instructed to the solenoid 434 of the secondary control valve 43 based on the determined target oil pressure Pt.
- the command current i is supplied to the solenoid 434
- the secondary control valve 43 controls the flow rate of the secondary control valve 43, and the hydraulic pressure corresponding to the target hydraulic pressure is supplied to the hydraulic cylinder 22 of the secondary pulley 16.
- the controller 45 includes a feed forward (F / F) compensation unit 451, a necessary flow rate computation unit 452, an opening computation unit 453, an indicated current computation unit 454, and a feedback (F / B) compensation unit 456.
- F / F feed forward
- F / B feedback
- the feedforward compensation unit 451 calculates a feedforward compensation amount so that a predetermined response is obtained in order to cancel a disturbance such as noise with respect to the input target hydraulic pressure Pt.
- the feed word compensation unit 451 uses a first-order lag function such as first-order differentiation.
- the required flow rate calculation unit 452 calculates a required flow rate Q for flowing through the secondary control valve 43 in order to achieve the target hydraulic pressure Pt.
- the required flow rate Q is calculated based on the current speed ratio Rt, the feedforward compensation amount, and the feedback compensation amount.
- the opening amount calculation unit 453 calculates an opening amount A that is a cross-sectional area of the opening of the secondary control valve 43 in order for the secondary control valve 43 to flow the calculated necessary flow rate Q. Since the required flow rate Q, the opening amount A, and the hydraulic pressure (line pressure) have a correlation, the opening amount A for the required flow rate Q is determined based on the correlation.
- the command current calculation unit 454 calculates the command current i for commanding the solenoid 434 of the secondary control valve 43 so that the opening amount A is calculated by the secondary control valve 43.
- the command current i is calculated as a current value necessary for operating the solenoid 434 so that the stroke amount of the spool 432 corresponding to the opening amount A is obtained and the obtained stroke amount is obtained.
- the feedback compensation amount calculation unit 456 calculates the feedback compensation amount by performing, for example, proportional / integral / derivative control (PID control) based on the target oil pressure Pt and the secondary actual oil pressure Psr detected by the secondary pressure sensor 46.
- PID control proportional / integral / derivative control
- the controller 45 calculates the necessary flow rate Q for the target hydraulic pressure Pt to act on the hydraulic cylinder 22 via the oil passage 404, and the flow rate that the secondary control valve 43 flows becomes the command flow rate Q.
- the instruction current i is instructed to the solenoid 434 so that the required opening amount A is obtained.
- FIG. 5 is a flowchart of control of the secondary control valve 43 executed by the controller 45.
- the flowchart shown in FIG. 5 is executed by the controller 45 at a predetermined cycle (for example, every 10 ms).
- the controller 45 acquires the target hydraulic pressure Pt, the secondary actual hydraulic pressure Psr, and the current gear ratio Rt (S10).
- the feedforward compensation amount calculation unit 451 of the controller 45 calculates the feedforward compensation amount.
- the feedforward compensation amount is calculated using a first-order lag function or the like based on the target oil pressure Pt (S20).
- the feedback compensation amount calculation unit 456 of the controller 45 calculates the feedback compensation amount.
- the feedback compensation amount is calculated by PID control or the like from the deviation between the target hydraulic pressure Pt and the secondary actual hydraulic pressure Psr (S30).
- the required flow rate Q is calculated by the required flow rate calculation unit 452 of the controller 45.
- the required flow rate Q is calculated based on the current gear ratio Rt, the feedforward compensation amount, and the feedback compensation amount (S40).
- the opening amount A of the secondary control valve 43 is calculated based on the required flow rate Q by the opening amount calculation unit 453 of the controller 45 (S50).
- the command current i instructed to the solenoid 434 of the secondary control valve 43 is calculated based on the opening amount A by the command current calculation unit 454 of the controller 45 (S60).
- the controller 45 instructs the calculated instruction current i to the solenoid 434 of the secondary control valve 43 (S70).
- the solenoid 434 of the secondary control valve 43 is operated, the secondary control valve is controlled to have the opening amount A, and the flow rate of the secondary control valve 43 is controlled to be the required flow rate Q.
- the hydraulic pressure supplied to the hydraulic cylinder 22 of the secondary pulley 16 is controlled by providing only one control valve, that is, the secondary control valve 43 with the line pressure as a source pressure.
- the secondary control valve 43 In general, when directly controlling a large hydraulic pressure such as a line pressure, it is necessary to increase the capacity of the solenoid in order to operate a mechanical feedback system that circulates the hydraulic pressure to the valve.
- the actual feedback system detected by the sensor is performed by the control inside the controller 45, thereby eliminating the mechanical feedback system.
- the responsiveness of the solenoid 434 is low and the initial value cannot be determined.
- the hydraulic pressure supplied to the hydraulic cylinder 22 can be controlled by a single control valve (secondary control valve 43) without increasing the size of the solenoid 434.
- the embodiment of the present invention changes the groove width of each pulley by the hydraulic pressure supplied to the hydraulic cylinder 21 of the primary pulley 15 and the hydraulic cylinder 22 of the secondary pulley 16, and the winding diameter of the V belt 17. It is related with the hydraulic control apparatus 40 which is a control apparatus of the continuously variable transmission mechanism 4 which changes a gear ratio by changing.
- the hydraulic control device 40 controls an oil pump 30 that functions as a hydraulic pressure supply unit that supplies hydraulic oil at a predetermined hydraulic pressure (line pressure), and a flow rate at which the hydraulic oil supplied by the oil pump 30 is supplied to the hydraulic cylinder 22.
- a secondary control valve 43 functioning as a flow rate control unit, and a flow rate setting means for setting a target hydraulic pressure Pt to be supplied to the hydraulic cylinder 22 and setting a flow rate of hydraulic fluid to be circulated through the secondary control valve 43 in order to achieve the target hydraulic pressure Pt.
- a controller 45 functioning as
- the target hydraulic pressure Pt to be supplied to the hydraulic cylinder 22 is set as the flow rate of the hydraulic oil that passes through the secondary control valve 43 that is a flow rate control valve, and the set flow rate is supplied from the secondary control valve 43 to the hydraulic cylinder 22. .
- the secondary control valve 43 that is a flow rate control valve
- the set flow rate is supplied from the secondary control valve 43 to the hydraulic cylinder 22.
- the hydraulic pressure supplied to the hydraulic cylinder 22 is not controlled by controlling the flow rate of the secondary control valve 43 as a flow rate control unit, instead of controlling the hydraulic pressure using the line pressure as a source pressure. Configured to control.
- the controller 45 only needs to control the flow rate of the secondary control valve 43, that is, the opening cross-sectional area of the valve, and the responsiveness of the hydraulic pressure is prevented from being lowered without increasing the size of the solenoid.
- a secondary hydraulic sensor 46 is provided as a hydraulic pressure detection unit that detects the secondary actual hydraulic pressure Psr supplied to the hydraulic cylinder 22, and the controller 45 has a difference between the target hydraulic pressure Pt supplied to the hydraulic cylinder 22 and the detected secondary actual hydraulic pressure Psr. Based on the above, the flow rate of the working oil to be circulated through the secondary control valve 43 is set. In this way, by performing feedback control using the actual hydraulic pressure in the control of the controller 45, the mechanical feedback system can be eliminated, and the solenoid 434 can be prevented from being enlarged.
- the secondary control valve 43 includes a solenoid 434 that slides the spool 432 in the axial direction as an actuator, the flow rate is controlled by the operation of the solenoid 434, and the controller 45 generates an instruction current i that is a command value for operating the solenoid 434. By instructing, the flow rate of the hydraulic oil is set. In this way, the secondary pressure supplied to the hydraulic cylinder 22 is not controlled by hydraulic control but by flow control, and the control amount is controlled by the operation amount of the solenoid 434, thereby eliminating the mechanical feedback system. This can prevent the solenoid 434 from becoming large.
- the controller 45 includes a hydraulic flow rate converter 452 as a flow rate determining unit that determines the flow rate of hydraulic oil in the secondary control valve 43 in order to achieve the target hydraulic pressure Pt, and a secondary control valve 43 in order to achieve the determined flow rate.
- An area converter 453 as an area determining unit that determines an opening area, and a current conversion as an operation amount determining unit that determines an instruction current i that is a control amount for operating the solenoid 434 in order to achieve the determined opening area Instrument 454.
- the controller 45 only needs to control the flow rate of the secondary control valve 43, that is, the opening cross-sectional area of the valve, and the hydraulic response is prevented from being lowered without increasing the size of the solenoid.
- the belt-type continuously variable transmission mechanism 4 in which the V-belt 17 is spanned between the pulleys has been described as an example, but the present invention is not limited thereto.
- a continuously variable transmission mechanism in which a chain is stretched between pulleys may be used.
- a sub-transmission mechanism having a stepped gear stage in series with the continuously variable transmission mechanism 4 may be provided.
- the present invention is not limited thereto.
- the operation of the primary pulley 15 is the same.
- the present invention can also be applied to other configurations in which the pilot pressure is regulated using the line pressure as the original pressure, and the valve opening is controlled by the regulated pilot pressure to control the hydraulic pressure.
- the present invention may be applied to a hydraulic circuit for controlling the engagement state of the forward clutch and the reverse brake of the forward / reverse switching mechanism 3.
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Abstract
Description
Claims (5)
- 車両に搭載され、一組のプーリに備えられる一組の油圧シリンダの少なくとも一方に供給される油圧により、前記一組のプーリによって挟持されるベルトの巻掛け径を変更して変速比を変更する無段変速機の制御装置であって、
作動油を所定の油圧で供給する油圧供給部と、
前記油圧供給部によって供給される作動油を前記油圧シリンダに供給するときの流量を制御する流量制御部と、
前記油圧シリンダに供給する目標油圧を設定し、前記目標油圧を達成するため前記流量制御部における作動油の流量を設定する流量設定手段と、を備える
無段変速機の制御装置。 - 請求項1に記載の無段変速機の制御装置であって、
前記油圧シリンダに供給される実油圧を検出する実油圧検出部を備え、
前記流量設定手段は、前記油圧シリンダに供給する目標油圧と前記検出された実油圧との差分に基づいて、前記流量制御部に流通させる作動油の流量を設定する
無段変速機の制御装置。 - 請求項1又は2に記載の無段変速機の制御装置であって、
前記流量制御部はアクチュエータを備え、前記アクチュエータの動作によって流量が制御され、
前記流量設定手段は、前記アクチュエータを動作させる指令を行うことで、前記流量制御部における作動油の流量を設定する
無段変速機の制御装置。 - 請求項3に記載の無段変速機の制御装置であって、
前記流量設定手段は、
前記目標油圧を達成するため前記流量制御部における作動油の流量を決定する流量決定部と、
前記流量決定部により決定された前記流量を達成するために、前記流量制御部における開口面積を決定する面積決定部と、
前記面積決定部により決定された前記開口面積を達成するために、前記アクチュエータを動作させる制御量を決定する動作量決定部と、を備え、
前記動作量決定部により決定された前記制御量を指示することにより前記アクチュエータを動作させて、前記流量制御部に流通させる作動油の流量を設定する
無段変速機の制御装置。 - 車両に搭載され、一組のプーリに備えられる一組の油圧シリンダの少なくとも一方に供給される油圧により、前記一組のプーリによって挟持されるベルトの巻掛け径を変更して変速比を変更する無段変速機と、作動油を所定の油圧で供給する油圧供給部と、前記油圧供給部によって供給される作動油を前記油圧シリンダに供給するときの流量を制御する流量制御部と、が備えられる制御装置とによって、無段変速機を制御する制御方法であって、
前記油圧シリンダに供給する目標油圧を設定し、
前記目標油圧を達成するため前記流量制御部における作動油の流量を設定し、
前記流量制御部に、前記設定された流量によって作動油を流通させる
無段変速機の制御方法。
Priority Applications (4)
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EP14775636.5A EP2980455A1 (en) | 2013-03-25 | 2014-02-04 | Continuously variable transmission control device and control method |
CN201480013540.1A CN105190114A (zh) | 2013-03-25 | 2014-02-04 | 无级变速器的控制装置及控制方法 |
US14/777,585 US20160290501A1 (en) | 2013-03-25 | 2014-02-04 | Control apparatus and control method for continuously variable transmission |
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JP2013-062509 | 2013-03-25 | ||
JP2013062509A JP2014185751A (ja) | 2013-03-25 | 2013-03-25 | 無段変速機の制御装置及び制御方法 |
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EP (1) | EP2980455A1 (ja) |
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Cited By (1)
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JP2021001677A (ja) * | 2019-06-24 | 2021-01-07 | ジヤトコ株式会社 | 車両の制御装置及び車両の制御方法 |
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CN113494598B (zh) * | 2020-04-08 | 2022-09-13 | 上海汽车集团股份有限公司 | 基于液压系统的流量需求的转速控制方法、控制器及汽车 |
WO2022091638A1 (ja) * | 2020-11-02 | 2022-05-05 | ジヤトコ株式会社 | プーリ圧制御弁のダンピング圧供給回路 |
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- 2014-02-04 EP EP14775636.5A patent/EP2980455A1/en not_active Withdrawn
- 2014-02-04 KR KR1020157020067A patent/KR20150102078A/ko not_active Application Discontinuation
- 2014-02-04 US US14/777,585 patent/US20160290501A1/en not_active Abandoned
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JP7165105B2 (ja) | 2019-06-24 | 2022-11-02 | ジヤトコ株式会社 | 車両の制御装置及び車両の制御方法 |
Also Published As
Publication number | Publication date |
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JP2014185751A (ja) | 2014-10-02 |
CN105190114A (zh) | 2015-12-23 |
EP2980455A1 (en) | 2016-02-03 |
US20160290501A1 (en) | 2016-10-06 |
KR20150102078A (ko) | 2015-09-04 |
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