WO2015140919A1 - Hydraulic control apparatus - Google Patents

Hydraulic control apparatus Download PDF

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Publication number
WO2015140919A1
WO2015140919A1 PCT/JP2014/057292 JP2014057292W WO2015140919A1 WO 2015140919 A1 WO2015140919 A1 WO 2015140919A1 JP 2014057292 W JP2014057292 W JP 2014057292W WO 2015140919 A1 WO2015140919 A1 WO 2015140919A1
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WO
WIPO (PCT)
Prior art keywords
hydraulic
opening
control unit
time point
time
Prior art date
Application number
PCT/JP2014/057292
Other languages
French (fr)
Japanese (ja)
Inventor
卓馬 西村
高鳥　修
山口　英治
Original Assignee
株式会社小松製作所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 株式会社小松製作所 filed Critical 株式会社小松製作所
Priority to PCT/JP2014/057292 priority Critical patent/WO2015140919A1/en
Publication of WO2015140919A1 publication Critical patent/WO2015140919A1/en

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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
    • 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
    • F16H2061/062—Smoothing ratio shift by controlling rate of change of fluid pressure using electric control means for controlling filling of clutches or brake servos, e.g. fill time, fill level or pressure during filling

Definitions

  • the present invention relates to a hydraulic control device.
  • a control device for hydraulic equipment such as a hydraulic clutch or a hydraulic brake includes a pressure control valve in order to adjust the hydraulic pressure supplied to the hydraulic equipment.
  • a pressure control valve in order to adjust the hydraulic pressure supplied to the hydraulic equipment.
  • completion of filling of hydraulic oil into hydraulic equipment has been detected by various means.
  • Patent Document 1 discloses detecting the completion of filling with a pressure switch.
  • Patent Document 2 discloses detecting the completion of filling with a flow rate detection valve.
  • control device causes a large amount of hydraulic oil to flow for a predetermined time (trigger time) from the start of supply of hydraulic oil in order to shorten the time required for completion of filling (filling completion time). Take control.
  • This filling completion time can be shortened by setting a longer trigger time.
  • a large shock may occur in the hydraulic equipment. For this reason, there is a limit to shortening the filling completion time by adjusting the trigger time.
  • the filling completion time can be shortened by increasing the flow rate of hydraulic oil after the trigger time has elapsed.
  • the riding comfort of the work vehicle may be impaired.
  • An object of the present invention is to shorten the filling completion time without impairing the riding comfort of the work vehicle.
  • the hydraulic control device is a device that controls hydraulic equipment.
  • the hydraulic control device includes a pressure control valve, a filling completion detection unit, and a control unit.
  • the pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the hydraulic equipment.
  • the filling completion detection unit detects completion of filling of hydraulic oil into the hydraulic device.
  • the control unit controls the opening degree of the pressure control valve.
  • the controller sets the opening degree to the first opening degree from the first time point to the second time point.
  • the first time point is a time point when the supply of hydraulic oil to the hydraulic equipment is started.
  • a control part makes a 2nd opening degree smaller than a 1st opening degree in a 2nd time point.
  • the controller increases the opening from the second opening from the second time point to the third time point.
  • the third time point is a time point when the filling completion detection unit detects the completion of filling of the hydraulic oil.
  • the control unit sets an increase rate of the opening degree from the second time point to the third time point based on the reference filling completion time.
  • the reference filling completion time is the time from the first time point to the third time point in the process performed before the target process.
  • the hydraulic device is a hydraulic clutch or a hydraulic brake. When the hydraulic device is a hydraulic clutch, the above-described process is a shift process. When the hydraulic device is a hydraulic brake, the above-described process is a braking process.
  • the controller gradually increases the opening from the second opening during the second time to the third time.
  • the control unit sets the increasing rate of the opening from the second time point to the third time point based on the reference filling completion time.
  • the filling completion time can be shortened without impairing the riding comfort of the work vehicle.
  • the control unit increases the opening degree increase rate from the previous process, thereby increasing the target The filling completion time in processing can be shortened.
  • the control part can make the increase rate of an opening degree smaller than the increase rate in the last process, when the filling completion time is shorter than desired time in the process performed previously.
  • the control unit can stabilize the filling completion time. Therefore, the hydraulic control device according to the first aspect of the present invention can shorten the filling completion time without impairing the riding comfort of the work vehicle.
  • the hydraulic control device further includes an electromagnetic control valve for controlling the opening degree of the pressure control valve.
  • a control part controls the opening degree of a pressure control valve by controlling the electric current value output to an electromagnetic control valve.
  • the control unit makes the increase rate in the target process higher than the increase rate in the process immediately before the target process. According to this configuration, the filling completion time can be shortened.
  • the control unit lowers the increase rate in the target process lower than the increase rate in the process immediately before the target process. According to this configuration, it is possible to prevent the filling completion time from becoming too short, and as a result, the filling completion time can be stabilized.
  • control unit sets the increase rate using the average value of filling completion times in a plurality of processes performed before the target processing as a reference filling completion time.
  • the increase rate can be set using data with higher reliability.
  • the hydraulic device is a hydraulic clutch.
  • the hydraulic clutch includes a first plate, a second plate, a piston, and an oil chamber.
  • the piston is configured to press the first plate toward the second plate.
  • the oil chamber generates a pressing force of the piston.
  • the pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the oil chamber.
  • the hydraulic control device is a device that controls hydraulic equipment.
  • the hydraulic control device includes a pressure control valve, a filling completion detection unit, and a control unit.
  • the pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the hydraulic equipment.
  • the filling completion detection unit detects completion of filling of hydraulic oil into the hydraulic device.
  • the control unit controls the opening degree of the pressure control valve.
  • the controller sets the opening degree to the first opening degree from the first time point to the second time point.
  • the first time point is a time point when the supply of hydraulic oil to the hydraulic equipment is started.
  • the control unit sets the opening degree to a second opening degree smaller than the first opening degree from the second time point to the third time point.
  • the third time point is a time point when the completion of filling of the hydraulic oil is detected by the filling completion detection unit. Then, the control unit sets the second opening based on the reference filling completion time.
  • the reference filling completion time is the time from the first time point to the third time point in the process performed before the target process.
  • the hydraulic device is a hydraulic clutch or a hydraulic brake. When the hydraulic device is a hydraulic clutch, the above-described process is a shift process. When the hydraulic device is a hydraulic brake, the above-described process is a braking process.
  • the control unit sets the second opening, which is the opening from the second time point to the third time point, based on the reference filling completion time.
  • the filling completion time can be shortened without impairing the riding comfort of the work vehicle.
  • the control unit sets the second opening to be larger than the second opening in the previous process.
  • the filling completion time can be shortened.
  • the control part can make a 2nd opening degree smaller than the 2nd opening degree in the last process, when the filling completion time is shorter than desired time in the process performed previously.
  • the control unit can stabilize the filling completion time. Therefore, the hydraulic control apparatus according to the second aspect of the present invention can shorten the filling completion time without impairing the riding comfort of the work vehicle.
  • the hydraulic control device further includes an electromagnetic control valve for controlling the opening degree of the pressure control valve.
  • a control part controls the opening degree of a pressure control valve by controlling the electric current value output to an electromagnetic control valve.
  • the control unit sets the second opening in the target process to be larger than the second opening in the process immediately before the target process. To do. According to this configuration, the filling completion time can be shortened.
  • the control unit makes the second opening degree in the target process smaller than the second opening degree in the process immediately before the target process. To do. According to this configuration, it is possible to prevent the filling completion time from becoming too short, and as a result, the filling completion time can be stabilized.
  • control unit sets the second opening degree using an average value of filling completion times in a plurality of processings performed before the target processing as a reference filling completion time.
  • the second opening degree can be set using data with higher reliability.
  • the hydraulic device is a hydraulic clutch.
  • the hydraulic clutch includes a first plate, a second plate, a piston, and an oil chamber.
  • the piston is configured to press the first plate toward the second plate.
  • the oil chamber generates a pressing force of the piston.
  • the pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the oil chamber.
  • the filling completion time can be shortened without impairing the riding comfort of the work vehicle.
  • FIG. 9 is a flowchart for explaining the operation of a control unit when performing a shift process in Modification 1; The graph which shows the change of the command current in the hydraulic control in the modification 1, and the supply hydraulic pressure.
  • FIG. 1 is a block diagram illustrating a configuration of a work vehicle.
  • the work vehicle 1 includes an engine 5, a power transmission mechanism 6, a traveling mechanism 9, a hydraulic pump 8, a hydraulic control device 2, an operation unit 10, a control unit 3, and the like.
  • the engine 5 is provided with a fuel injection pump 83, and fuel is supplied from the fuel injection pump 83 to the engine 5.
  • the supply amount is controlled by a command signal output from the control unit 3 to the electronic governor 82.
  • the rotational speed of the engine 5 is detected by the engine rotational speed sensor 81 and sent to the control unit 3 as a detection signal.
  • the control unit 3 can control the number of revolutions of the engine 5 by sending a command signal to the electronic governor 82 to control the amount of fuel supplied to the engine 5.
  • the power transmission mechanism 6 is a mechanism for transmitting the driving force from the engine 5 to the drive wheels 12 and includes a torque converter 62 and a transmission 60.
  • the torque converter 62 is connected to the output side of the engine 5.
  • the torque converter 62 is provided with a lockup clutch 70 that directly connects the input shaft and the output shaft of the torque converter 62.
  • the lock-up clutch 70 is a hydraulic clutch that is driven by the hydraulic pressure supplied from the hydraulic pump 8.
  • the control unit 3 controls the hydraulic pressure supplied to the lockup clutch 70 by transmitting a command signal to the lockup clutch control valve device 28.
  • the transmission 60 has various clutches 63 to 69 and a plurality of transmission gears (not shown).
  • the various clutches 63 to 69 are hydraulic clutches that are driven by the hydraulic pressure supplied from the hydraulic pump 8, and are FL clutch 63, FH clutch 64, R clutch 65, 1st clutch 66, 2nd clutch 67, 3rd clutch 68, There is a 4th clutch 69.
  • the various clutches 63 to 69 include a first plate 631, a second plate 632, a piston 634, and an oil chamber 635.
  • the first plate 631 and the second plate 632 are movable in the axial direction (left-right direction in FIG. 10).
  • the piston 633 moves, and as a result, the first plate 631 and the second plate 632 are connected to transmit power.
  • a plurality of first plates 631 and second plates 632 are provided to constitute a multi-plate clutch.
  • the FL clutch 63 and the FH clutch 64 are engaged when the vehicle moves forward.
  • the R clutch 65 is engaged when the vehicle moves backward.
  • the 1st clutch 66, the 2nd clutch 67, the 3rd clutch 68, and the 4th clutch 69 are engaged when transmitting the driving force to the corresponding transmission gears.
  • the speed stage of 1 to 8 speed when moving forward, can be selected by combining any of the FL clutch 63 and the FH clutch 64 and any of the 1st clutch 66 to the 4th clutch 69. Further, at the time of reverse travel, the speed stage of 1st to 4th speed can be selected by a combination of the R clutch 65 and any of the 1st clutch 66 to the 4th clutch 69.
  • the input rotation speed to the FL clutch 63, the FH clutch 64, and the R clutch 65 is detected by the input rotation speed sensor 85 and sent to the control unit 3 as a detection signal. Further, the output rotational speeds from the FL clutch 63, the FH clutch 64, and the R clutch 65 are detected by the output rotational speed sensor 86 and sent to the control unit 3 as a detection signal.
  • the traveling mechanism 9 is a mechanism for traveling the vehicle using the driving force from the engine 5.
  • the traveling mechanism 9 is transmitted with the driving force from the engine 5 via the power transmission mechanism 6.
  • the travel mechanism 9 has a final reduction gear (not shown) and drive wheels 12.
  • the driving force output from the transmission 60 is transmitted to the drive wheels 12 through the final reduction gear. As a result, the drive wheel 12 is driven to rotate and the work vehicle travels.
  • the hydraulic pump 8 is driven by the driving force from the engine 5 and generates hydraulic pressure supplied to the various clutches 63 to 70.
  • the operation unit 10 is a part that is operated by an operator in order to control the traveling of the work vehicle 1 and a work machine (not shown).
  • the operation unit 10 includes operation members such as an accelerator pedal 14, an inching pedal 13, and a shift lever 11.
  • the accelerator pedal 14 is an operation member that is operated to set the engine speed to a desired speed.
  • the inching pedal 13 is an operation member that is operated to cause the FL clutch 63, the FH clutch 64, or the R clutch 65 to slip to reduce the vehicle speed.
  • the shift lever 11 is an operation member that is operated by an operator to manually shift the transmission 60. When each operation member of the operation unit 10 is operated, an operation signal corresponding to the operation is sent to the control unit 3.
  • the hydraulic control device 2 is a device for controlling the various clutches 63 to 70 described above by the hydraulic pressure generated by the hydraulic pump 8.
  • the hydraulic control device 2 includes control valve devices 21 to 28 and a control unit 3.
  • the control valve devices 21 to 28 are electromagnetic proportional control valves capable of adjusting the hydraulic pressure by being electrically controlled by the control unit 3, and include first to seventh clutch control valve devices 21 to 27, lock-ups. There is a clutch control valve device 28 and the like.
  • the lockup clutch control valve device 28 adjusts the hydraulic pressure supplied to the lockup clutch 70.
  • the first to seventh clutch control valve devices 21 to 27 adjust the hydraulic pressure supplied to the various clutches 63 to 69 described above.
  • the first clutch control valve device 21 adjusts the hydraulic pressure supplied to the FL clutch 63.
  • the second clutch control valve device 22 adjusts the hydraulic pressure supplied to the FH clutch 64.
  • the third clutch control valve device 23 adjusts the hydraulic pressure supplied to the R clutch 65.
  • the fourth clutch control valve device 24 adjusts the hydraulic pressure supplied to the first clutch 66.
  • the fifth clutch control valve device 25 adjusts the hydraulic pressure supplied to the 2nd clutch 67.
  • the sixth clutch control valve device 26 adjusts the hydraulic pressure supplied to the 3rd clutch 68.
  • the seventh clutch control valve device 27 adjusts the hydraulic pressure supplied to the 4th clutch 69.
  • the control unit 3 controls the first to seventh clutch control valve devices 21 to 27 on the basis of an operation signal from the operation unit 10, detection signals from various sensors, or the like, so that a speed change suitable for the state of the vehicle is performed. Control can be performed.
  • control unit 3 transmits a command signal to the first clutch control valve device 21 and supplies hydraulic pressure to the FL clutch 63. Then, the controller 3 sends a command signal to the seventh clutch control valve device 27 to supply hydraulic pressure to the 4th clutch 69. As a result, the FL clutch 63 and the 4th clutch 69 are engaged, and the seventh speed stage can be selected.
  • control unit 3 transmits a command signal to the second clutch control valve device 22 to supply hydraulic pressure to the FH clutch 64. Then, the control unit 3 transmits a command signal to the fourth clutch control valve device 24 to supply hydraulic pressure to the first clutch 66. As a result, the FH clutch 64 and the first clutch 66 are engaged, and the second speed stage can be selected.
  • control unit 3 determines the amount of fuel supplied to the engine 5 based on the operation signal from the accelerator pedal 14 and the engine speed detected by the engine speed sensor 81. Then, the control unit 3 transmits a command signal corresponding to the determined supply amount to the electronic governor 82. Thus, the fuel injection amount from the fuel injection pump 83 is adjusted to an amount commensurate with the operation amount of the accelerator pedal 14, and the engine speed is controlled. Thus, the operator can control the output of the work machine and the speed of the vehicle.
  • the control unit 3 determines whether the first clutch control valve device 21, the second clutch control valve device 22, or the third clutch based on the operation signal from the inching pedal 13. By adjusting the command signal to the control valve device 23, the hydraulic pressure supplied to the FL clutch 63, the FH clutch 64 or the R clutch 65 is reduced. As a result, the driving force transmitted from the power transmission mechanism 6 to the traveling mechanism 9 is reduced, and the vehicle speed is reduced.
  • FIG. 2 is a cross-sectional view of the first clutch control valve device 21. Although the first clutch control valve device 21 is illustrated in FIG. 2, the other control valve devices 22 to 28 have the same configuration.
  • the first clutch control valve device 21 includes a housing 20, a pressure control valve 15, an electromagnetic control valve 18, and a filling completion detection unit 16.
  • the housing 20 is formed with an input port 17, an output port 19, a first drain port 31, and a second drain port 32.
  • a hydraulic pump 8 is connected to the input port 17.
  • An FL clutch 63 is connected to the output port 19.
  • a tank (not shown) is connected to each of the first drain port 31 and the second drain port 32.
  • the pressure control valve 15 is a member that adjusts the hydraulic pressure of the hydraulic oil supplied to the FL clutch 63.
  • the pressure control valve 15 has a first spool 34.
  • the first spool 34 is provided in the housing 20 so as to be movable in the axial direction (left-right direction in FIG. 2).
  • a valve chamber 35 is formed in the housing 20.
  • a substantially central portion in the axial direction of the first spool 34 is located in the valve chamber 35.
  • a feedback chamber 36 is formed inside one axial end portion (hereinafter referred to as “base end portion”) of the first spool 34.
  • the valve chamber 35 and the feedback chamber 36 communicate with each other via a flow path 37 formed in the first spool 34.
  • a spring 38 is provided between the feedback chamber 36 and the inner wall surface of the housing 20.
  • the first spool 34 is urged by the spring 38 toward the other axial end portion (hereinafter referred to as “tip portion”).
  • a pilot chamber 39 is formed inside the tip of the first spool 34.
  • a pressure receiving surface 40 is formed on the end surface of the front end portion of the first spool 34.
  • a groove portion (not shown) is formed in the pressure receiving surface 40 of the first spool 34 for communicating the pilot chamber 39 and a flow path 44 described later.
  • the first spool 34 When the first spool 34 is positioned on the distal end side by the biasing force of the spring 38, that is, when the pressure receiving surface 40 is in contact with a valve seat body 41 of the electromagnetic control valve 18 described later, the first spool 34 is The input port 17 and the valve chamber 35 are shut off, and the valve chamber 35 and the second drain port 32 are communicated.
  • a flow path 43 is formed in the housing 20.
  • the input port 17 and the space in which the pressure receiving surface 40 is disposed communicate with each other through the flow path 43.
  • the flow path 43 has two flow paths 44 and 45.
  • the flow path 45 is a part on the input port 17 side, and the flow path 44 is a part on the pressure receiving surface 40 side.
  • the channel 45 has a larger diameter than the channel 44.
  • a screw plug 46 is provided at a connection portion between the flow path 45 and the flow path 44.
  • the threaded portion of the screw plug 46 is screwed into the small-diameter channel 44, and the head of the screw plug 46 is located in the large-diameter channel 45.
  • an annular minute gap 47 is formed between the outer peripheral surface of the head of the screw plug 46 and the inner peripheral surface of the flow path 45.
  • a throttle channel 48 is formed inside the screw plug 46. The throttle channel 48 communicates the gap 47 and the channel 44.
  • the electromagnetic control valve 18 includes a valve seat body 41, a valve body 50, a connecting member 51, and a proportional solenoid 52.
  • the valve seat body 41 is disposed to face the tip of the first spool 34 and is fixed to one end of the connecting member 51.
  • a pilot chamber 53 is formed at the base end portion of the valve seat body 41.
  • the front end surface of the valve seat body 41 (the left end surface in FIG. 2) and the front end surface of the first spool 34 can be brought into contact with and separated from each other.
  • the pilot chamber 53 of the valve seat body 41 and the pilot chamber 39 of the first spool 34 communicate with each other.
  • a valve storage chamber 54 is formed inside the valve seat body 41.
  • a drain channel 55 extending in the axial direction and a drain channel 56 extending in the radial direction are formed.
  • the drain channel 55 allows the pilot chamber 53 and the valve storage chamber 54 to communicate with each other.
  • the drain passage 56 passes through the valve storage chamber 54 and penetrates the valve seat body 41 in the radial direction.
  • the drain channel 56 communicates the drain channel 55 with the outer peripheral side of the valve seat body 41, and one end of the drain channel 56 communicates with the first drain port 31.
  • a valve seat surface 57 is formed on the left inner wall surface of the valve storage chamber 54.
  • the valve body 50 has a spherical shape and is stored in the valve storage chamber 54 so as to be movable in the left-right direction.
  • the connecting member 51 connects the valve seat body 41 and the proportional solenoid 52.
  • a plunger 58 is inserted into the connecting member 51 so as to be able to advance and retreat in the axial direction (left and right direction in FIG. 2).
  • the tip of the plunger 58 is in contact with the valve body 50.
  • the proportional solenoid 52 advances and retracts the plunger 58 in the axial direction when a command current is input from the control unit 3.
  • the oil from the hydraulic pump 8 is supplied to the input port 17, the gap 47 of the flow path 45, the throttle flow path 48 of the screw plug 46, the flow path 44, the pilot chambers 39 and 53, the drain flow path 55, and the drain flow path 56.
  • the first drain port 31 sequentially flows and is discharged to the tank.
  • the first spool 34 moves to the right side by the urging force of the spring 38.
  • the first spool 34 is positioned in contact with the valve seat body 41.
  • the input port 17 and the valve chamber 35 are closed, and the valve chamber 35 and the second drain port 32 communicate with each other, so that the pressure in the valve chamber 35 does not stand. Since the valve chamber 35 communicates with the FL clutch 63 via the output port 19, no hydraulic pressure is generated in the FL clutch 63. For this reason, the FL clutch 63 is released.
  • the opening degree of the pressure control valve 15 means the amount of movement of the first spool 34.
  • the filling completion detection unit 16 is a member that detects completion of filling of the hydraulic oil into the FL clutch 63.
  • the filling completion detection unit 16 includes a second spool 161, a detection pin 162, a fixing member 164, and an output pin 166.
  • the second spool 161 is provided in the housing 20 so as to be movable in the axial direction (left-right direction in FIG. 2).
  • the second spool 161 has a flange portion 161a. When the flange portion 161a comes into contact with the shoulder portion 201 of the housing 20, the second spool 161 is restricted from moving leftward in FIG.
  • the second spool 161 has a storage chamber 161b inside.
  • a detection pin 162 and a spring 163 are accommodated in the accommodation chamber 161b.
  • the detection pin 162 is biased to the right by a spring 163.
  • the right end of the detection pin 162 passes through the second spool 161 and protrudes to the right.
  • the second spool 161 is constituted by a spool body 161c and a cap member 161d.
  • the spool body 161c has a concave storage chamber 161b.
  • the cap member 161d is connected to the spool body 161c so as to close the accommodation chamber 161b.
  • the fixing member 164 is attached to the outer surface of the housing 20.
  • a spring 165 is provided between the fixing member 164 and the second spool 161.
  • the second spool 161 is urged to the left by the urging force of the spring 165.
  • the output pin 166 is attached to the fixing member 164 and faces the detection pin 162 on the right side of the detection pin 162.
  • the right end portion of the output pin 166 is connected to the control unit 3 (see FIG. 1) via a lead wire (not shown).
  • the filling completion detection unit 16 is provided facing the flow path 59 communicating with the valve chamber 35. Since the valve chamber 35 is connected to the output port 19, when the filling of the hydraulic oil into the FL clutch 63 is completed, the second spool 161 moves to the right against the urging force of the spring 165. As a result, as shown in FIG. 3, the detection pin 162 comes into contact with the output pin 166, and a detection signal indicating completion of filling is sent to the control unit 3.
  • step S1 the control unit 3 determines whether or not a shift command has been generated. Note that the control unit 3 continuously monitors whether or not a shift command from the shift lever 11 is output after the engine is started (No in step S1).
  • step S2 the control unit 3 controls the opening degree of the pressure control valve 15 to set the opening degree of the pressure control valve 15 to 1 opening degree (step S2). Specifically, as shown in FIG. 5, the control unit 3 outputs a command current of the first current value I1 to the proportional solenoid 52 so that the opening degree of the pressure control valve 15 becomes the first opening degree (time point t1). ). As a result, the first spool 34 moves to the left side of FIG. 2 to start supplying hydraulic oil to the clutch, and the supply hydraulic pressure starts to increase as shown in FIG. 5B. Further, the control unit 3 maintains the command current at the first current value I1.
  • the time point t1 at which the supply of hydraulic oil to the clutch is set as the first time point t1. Even if the command current is set to the first current value I1, the hydraulic oil is supplied to the circuit from which oil has been removed, so the supply hydraulic pressure does not increase with the same gradient as the command current value.
  • step S3 the control unit 3 starts counting the timer T (step S3). That is, the control unit 3 starts counting the timer T from the time when it is determined that the shift command has been generated (first time point t1).
  • the controller 3 determines whether or not the timer T has reached a preset time Tt (step S4).
  • This time Tt is referred to as a trigger time.
  • the control unit 3 proceeds to the next step S5.
  • the control unit 3 maintains the command current at the first current value I1.
  • the control unit 3 continues to monitor until the timer T reaches the trigger time Tt (No in step S4).
  • a time point t2 when the trigger time Tt has elapsed from the first time point t1 is set as a second time point t2 (see FIG. 5).
  • the first current value I1 which is the command current at the trigger time Tt, is high, and the first opening of the pressure control valve 15 is large.
  • the filling completion time can be shortened.
  • the trigger time Tt cannot be set so as to be extended to just before filling.
  • the control unit 3 controls the opening degree of the pressure control valve 15 to set the opening degree of the pressure control valve 15 to the second opening degree (step S5).
  • the control unit 4 reduces the command current output to the proportional solenoid 52 to the second current value I2 (see FIG. 5A) so that the opening degree of the pressure control valve 15 becomes the second opening degree.
  • the supply hydraulic pressure decreases (second time point t2).
  • the second opening is smaller than the first opening.
  • the second opening is a fixed value set in advance by experiments or the like.
  • the second current value I2 is set to suppress a shock when the clutch is engaged, and is a considerably lower value than the first current value I1.
  • the control unit 3 outputs the first current value I1 until the trigger time Tt elapses from the time point t1, that is, from the first time point t1 to the second time point t2.
  • the opening degree of the pressure control valve 15 becomes the first opening degree
  • the flow rate of the hydraulic oil supplied to the clutch becomes the relatively large first flow rate.
  • the control unit 3 reduces the command current from the first current value I1 to the second current value I2 at the second time point t2 when the trigger time Tt has elapsed from the first time point t1.
  • the opening degree of the pressure control valve 15 becomes a second opening degree smaller than the first opening degree, and the flow rate of the hydraulic oil supplied to the clutch becomes a relatively small second flow rate.
  • control unit 3 gradually increases the opening degree of the pressure control valve 15 from the second opening degree (step S6). Specifically, the control unit 3 gradually increases the command current to be output from the second current value I2 (see FIG. 5A). Based on the filling completion time (hereinafter referred to as “reference filling completion time”) in the speed change process executed before the speed change process, the control unit 3 sets the rate of increase in the opening degree in step S6. The details of the operation of the control unit 3 when setting the increasing rate of the opening will be described later.
  • control unit 3 determines whether or not the filling of the hydraulic oil into the clutch is completed (step S7). Specifically, the control unit 3 makes a determination based on the detection signal from the filling completion detection unit 16. For example, the filling completion detection unit 16 outputs a detection signal to the control unit 3 when the supply hydraulic pressure Pf is reached. The control unit 3 continuously monitors the detection signal from the filling completion detection unit 16 (No in step S7).
  • Step S8 When the control unit 3 determines that the filling is completed based on the detection signal from the filling completion detection unit 16 (Yes in Step S7), the control unit 3 stores the filling completion time Tf (Step S8).
  • the filling completion time Tf is the time from the start of hydraulic oil supply (first time point t1) to the completion of filling (time point t3) (see FIG. 5). Further, the time point t3 at which the completion of filling is detected by the filling completion detector 16 is set as a third time point t3.
  • the control unit 3 starts modulation from the third time point (step S9).
  • the command current is temporarily reduced to a preset third current value I3. This is to prevent the modulation gradient from changing due to the change in the increase rate of the command current, and as a result, to change the feeling when the clutch is engaged.
  • the third current value I3 may be the same value as the second current value I2, or may be a different value.
  • the control unit 3 changes the command current I so that a desired supply hydraulic pressure is supplied to the clutch.
  • the supply hydraulic pressure reaches the set clutch pressure Pt, and the switching from the clutch released state to the engaged state is completed.
  • the shift process is completed.
  • FIG. 6 is a flowchart for explaining the operation of the control unit 3 when setting the increase rate of the opening degree.
  • the control unit 3 reads the filling completion time in the shift process performed before the target shift process as a reference filling completion time (step S61).
  • the control unit 3 measures and stores the time (filling completion time) Tf from the start of hydraulic oil supply (first time point t1) to the completion of filling (third time point t3) every time the shift process is performed. ing.
  • the control unit 3 may read the filling completion time Tf in the (n ⁇ 1) th shifting process as the reference filling completion time.
  • the control unit 3 may read an average value of a plurality of filling completion times Tf as a reference filling completion time. Specifically, the control unit 3 reads the filling completion time Tf of 10 shift processes from the (n-10) th shift process to the (n-1) th shift process, and calculates an average value thereof. To do. And the control part 3 may read this average value as reference filling completion time.
  • control unit 3 determines whether or not the reference filling completion time read in step S61 is within a preset range (step S62).
  • the control unit 3 determines whether or not the reference filling completion time is equal to or longer than a preset maximum time. When the control unit 3 determines that the reference filling completion time is equal to or longer than the maximum time, the control unit 3 proceeds to step S64 described later. If the control unit 3 determines that the reference filling completion time is smaller than the maximum time, then the control unit 3 determines whether the reference filling completion time is equal to or less than a preset minimum time. When the control unit 3 determines that the reference filling completion time is equal to or shorter than the preset minimum time, the control unit 3 proceeds to step S64 described later. If the control unit 3 determines that the reference filling completion time is larger than the minimum time, the control unit 3 proceeds to step S63 described later.
  • Step S62 the control unit 3 sets the increase rate used in the previous shift process (Step S63). That is, the control unit 3 does not change the increase rate of the opening degree from the previous shift process.
  • the control unit 3 determines that the reference filling completion time is out of the preset range (No in step S62), the control unit 3 changes the increase rate of the opening degree in the target shift process (step S64). Specifically, when the control unit 3 determines that the reference filling completion time is longer than the maximum value in a preset range, the control unit 3 sets the increase rate in the target shift process to be higher than the increase rate in the previous shift process. Make it high. If the control unit 3 determines that the reference filling completion time is shorter than the minimum value in the preset range, the control unit 3 sets the increase rate in the target shift process to be lower than the increase rate in the previous shift process. The current value at the completion of filling is larger than the second current value I2, but the increase rate is set so that the shock at the time of clutch engagement does not become so large.
  • the hydraulic control apparatus has the following characteristics.
  • the control unit 3 sets the increasing rate of the opening from the second time point t2 to the third time point t3 based on the reference filling completion time.
  • the filling completion time can be shortened without impairing the riding comfort of the work vehicle.
  • the control unit 3 increases the opening degree increase rate from the increase rate in the previous shift process.
  • the filling completion time in the target shift process can be shortened.
  • the control unit 3 may make the opening increase rate smaller than the increase rate in the previous shift process. it can. As a result, the control unit 3 can shorten the filling completion time and can stabilize the filling completion time.
  • the hydraulic control device 2 can shorten the filling completion time without impairing the riding comfort of the work vehicle.
  • the increase in the opening from the second time point t2 to the third time point t3 is not limited to a linear increase, and may be a multi-order curve such as a quadratic curve.
  • the opening at the second time point is the second opening. That is, “between the first time point and the second time point” means that the time is greater than or equal to the first time point and less than the second time point, and does not include the second time point. Similarly, “between the second time point and the third time point” means a period between the second time point and the third time point, and does not include the third time point.
  • the controller 3 of the hydraulic control device 2 controls the rate of increase of the opening during the period from the second time point t2 to the third time point t3 in order to adjust the filling completion time Tf. It is not particularly limited to this.
  • the control unit 3 of the hydraulic control device can adjust the filling completion time Tf by controlling the second opening degree.
  • the control unit 3 executes the processing from step S1 to step S5 as in the above embodiment.
  • the second opening degree in step S5 is a constant fixed value.
  • the second opening degree in step S5 is variable and the control unit 3 opens the second opening. Set the degree.
  • movement of the control part 3 at the time of setting a 2nd opening degree is mentioned later.
  • control unit 3 executes the processing from step S7 to step S9 as in the above embodiment.
  • the control unit 3 does not execute the process in step S6 of the above embodiment. That is, as shown in FIG. 8, the control unit 3 maintains the second opening degree from the second time point t2 to the third time point t3. Therefore, the control unit 3 keeps the command current output to the proportional solenoid 52 from the second time point t2 to the third time point t3 as the second current value I2.
  • FIG. 9 is a flowchart for explaining the operation of the control unit 3 when setting the second opening.
  • control unit 3 executes the processes of steps S61 and S62 as in the above embodiment.
  • control unit 3 determines that the reference filling completion time is within the preset range (Yes in step S62)
  • the control unit 3 sets the same second opening as that in the previous shift process (step S53). That is, the control unit 3 does not change the second opening degree from the previous shift process.
  • control unit 3 determines that the reference filling completion time is out of the preset range (No in step S62)
  • the control unit 3 changes the second opening degree in the target shift process (step S54). Specifically, when the control unit 3 determines that the reference filling completion time is longer than the maximum value in a preset range, the control unit 3 sets the second opening in the target shift process to the previous second opening. Also make it bigger. If the control unit 3 determines that the reference filling completion time is shorter than the minimum value in the preset range, the control unit 3 sets the second opening in the target shift process to the second opening in the previous shift process. Also make it smaller.
  • the trigger time Tt may be a fixed value set in advance or may be variable. That is, the control unit 3 may control the trigger time Tt based on the reference filling completion time. In this case, it is preferable that the control unit 3 preferentially executes the control of the increase rate of the opening from the second time point to the third time point, rather than the control of the trigger time Tt.
  • Modification 3 In the above embodiment, the present invention is applied to the control of the clutch, but the present invention is also applicable to the control of the hydraulic brake.
  • the present invention When the present invention is applied to control of a hydraulic brake, the above-described shift process is replaced with a brake process.
  • the hydraulic brake 73 includes a first plate 731, a second plate 732, a piston 734, and an oil chamber 735.
  • the first plate 731 and the second plate 732 are movable in the axial direction (left-right direction in FIG. 11).
  • the piston 733 moves, and as a result, the first plate 731 and the second plate 732 are connected to transmit power.
  • a plurality of first plates 731 and second plates 732 are provided to constitute a multi-plate brake.
  • Control unit 15 Pressure control valve 16 Filling completion detection unit

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Abstract

The present invention shortens the time to completion of filling without reducing work vehicle riding comfort. A control unit (3) opens the degree of opening to a first opening degree between a first time point and a second time point. Then, at the second time point, the control unit (3) changes the opening degree to a second opening degree that is smaller than the first opening degree. The control unit (3) gradually increases the opening degree from the second opening degree between the second time point and a third time point. The control unit (3) sets the rate of increase in opening degree from the second time point to the third time point on the basis of a reference filling completion time.

Description

油圧制御装置Hydraulic control device
　本発明は、油圧制御装置に関するものである。 The present invention relates to a hydraulic control device.
　油圧式クラッチ又は油圧式ブレーキなどの油圧機器の制御装置は、油圧機器への供給する作動油圧を調整するために、圧力制御弁を備えている。従来、油圧機器への作動油の充填完了が、種々の手段で検出されている。例えば、特許文献１では、圧力スイッチによって充填完了を検出することが開示されている。また、特許文献２では、流量検出弁によって充填完了を検出することが開示されている。 A control device for hydraulic equipment such as a hydraulic clutch or a hydraulic brake includes a pressure control valve in order to adjust the hydraulic pressure supplied to the hydraulic equipment. Conventionally, completion of filling of hydraulic oil into hydraulic equipment has been detected by various means. For example, Patent Document 1 discloses detecting the completion of filling with a pressure switch. Further, Patent Document 2 discloses detecting the completion of filling with a flow rate detection valve.
　上記のいずれの方式においても、制御装置は、充填完了までに要する時間（充填完了時間）を短縮するために、作動油の供給開始から所定時間（トリガ時間）、大流量の作動油を流すという制御を行う。 In any of the above-described methods, the control device causes a large amount of hydraulic oil to flow for a predetermined time (trigger time) from the start of supply of hydraulic oil in order to shorten the time required for completion of filling (filling completion time). Take control.
特開２０１０－１５１２９４号公報JP 2010-151294 A 特開２００３－８３４２８号公報JP 2003-83428 A
　空走時間を低減させるためには充填完了時間を短縮することが好ましい。この充填完了時間は、トリガ時間を長く設定することによって短縮されることができる。しかしながら、トリガ時間中に油圧機器への作動油の充填が完了してしまうと、油圧機器に大きなショックが発生するおそれがある。このため、トリガ時間を調整することによって充填完了時間を短縮することには限界がある。 In order to reduce the idle time, it is preferable to shorten the filling completion time. This filling completion time can be shortened by setting a longer trigger time. However, if the hydraulic oil is completely filled in the hydraulic equipment during the trigger time, a large shock may occur in the hydraulic equipment. For this reason, there is a limit to shortening the filling completion time by adjusting the trigger time.
　また、トリガ時間経過後の作動油の流量を従来よりも多くすることで充填完了時間を短縮することができる。しかしながら、この短縮方法では、作業車両の乗り心地が損なわれるおそれがある。 Also, the filling completion time can be shortened by increasing the flow rate of hydraulic oil after the trigger time has elapsed. However, with this shortening method, the riding comfort of the work vehicle may be impaired.
　本発明の課題は、作業車両の乗り心地を損ねることなく充填完了時間を短縮することにある。 An object of the present invention is to shorten the filling completion time without impairing the riding comfort of the work vehicle.
　本発明の第１側面に係る油圧制御装置は、油圧機器を制御する装置である。この油圧制御装置は、圧力制御弁と、充填完了検出部と、制御部とを備えている。圧力制御弁は、油圧機器に供給される作動油の油圧を制御する。充填完了検出部は、油圧機器への作動油の充填完了を検出する。制御部は、圧力制御弁の開度を制御する。制御部は、第１時点から第２時点までの間、開度を第１開度とする。なお、第１時点とは、油圧機器へ作動油を供給開始する時点である。そして、制御部は、第２時点において、開度を第１開度よりも小さい第２開度とする。そして、制御部は、第２時点から第３時点までの間、開度を第２開度から増加させる。なお、第３時点は、充填完了検出部によって作動油の充填完了が検出される時点である。制御部は、参考充填完了時間に基づき、第２時点から第３時点までにおける開度の増加率を設定する。なお、参考充填完了時間とは、対象の処理よりも前に行われた処理における第１時点から第３時点までの時間である。油圧機器は、油圧式クラッチ又は油圧式ブレーキである。油圧機器が油圧式クラッチの場合、上述した処理は変速処理である。また、油圧機器が油圧式ブレーキの場合、上述した処理は制動処理である。なお、制御部は、第２時点から第３時点までの間、開度を第２開度から徐々に大きくする。 The hydraulic control device according to the first aspect of the present invention is a device that controls hydraulic equipment. The hydraulic control device includes a pressure control valve, a filling completion detection unit, and a control unit. The pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the hydraulic equipment. The filling completion detection unit detects completion of filling of hydraulic oil into the hydraulic device. The control unit controls the opening degree of the pressure control valve. The controller sets the opening degree to the first opening degree from the first time point to the second time point. The first time point is a time point when the supply of hydraulic oil to the hydraulic equipment is started. And a control part makes a 2nd opening degree smaller than a 1st opening degree in a 2nd time point. The controller increases the opening from the second opening from the second time point to the third time point. The third time point is a time point when the filling completion detection unit detects the completion of filling of the hydraulic oil. The control unit sets an increase rate of the opening degree from the second time point to the third time point based on the reference filling completion time. The reference filling completion time is the time from the first time point to the third time point in the process performed before the target process. The hydraulic device is a hydraulic clutch or a hydraulic brake. When the hydraulic device is a hydraulic clutch, the above-described process is a shift process. When the hydraulic device is a hydraulic brake, the above-described process is a braking process. The controller gradually increases the opening from the second opening during the second time to the third time.
　この構成によれば、制御部は、参考充填完了時間に基づき、第２時点から第３時点までの開度の増加率を設定する。この結果、作業車両の乗り心地を損ねることなく充填完了時間を短縮することができる。例えば、制御部は、以前に行われた処理において、充填完了時間が所望の時間よりも長かった場合には、開度の増加率を前回の処理における増加率よりも大きくすることによって、対象の処理における充填完了時間を短くすることができる。また、制御部は、以前に行われた処理において、充填完了時間が所望の時間よりも短かった場合には、開度の増加率を前回の処理における増加率よりも小さくすることができる。この結果、制御部は、充填完了時間を安定させることができる。したがって、本発明の第１側面に係る油圧制御装置は、作業車両の乗り心地を損ねることなく、充填完了時間を短縮することができる。 According to this configuration, the control unit sets the increasing rate of the opening from the second time point to the third time point based on the reference filling completion time. As a result, the filling completion time can be shortened without impairing the riding comfort of the work vehicle. For example, when the filling completion time is longer than the desired time in the previously performed process, the control unit increases the opening degree increase rate from the previous process, thereby increasing the target The filling completion time in processing can be shortened. Moreover, the control part can make the increase rate of an opening degree smaller than the increase rate in the last process, when the filling completion time is shorter than desired time in the process performed previously. As a result, the control unit can stabilize the filling completion time. Therefore, the hydraulic control device according to the first aspect of the present invention can shorten the filling completion time without impairing the riding comfort of the work vehicle.
　好ましくは、油圧制御装置は、圧力制御弁の開度を制御する電磁制御弁をさらに備える。そして、制御部は、電磁制御弁に出力する電流値を制御することによって、圧力制御弁の開度を制御する。 Preferably, the hydraulic control device further includes an electromagnetic control valve for controlling the opening degree of the pressure control valve. And a control part controls the opening degree of a pressure control valve by controlling the electric current value output to an electromagnetic control valve.
　好ましくは、制御部は、予め設定された最大値よりも参考充填完了時間が長い場合、対象の処理における増加率を、対象の処理より１つ前の処理における増加率よりも高くする。この構成によれば、充填完了時間を短縮することができる。 Preferably, when the reference filling completion time is longer than a preset maximum value, the control unit makes the increase rate in the target process higher than the increase rate in the process immediately before the target process. According to this configuration, the filling completion time can be shortened.
　好ましくは、制御部は、予め設定された最小値よりも参考充填完了時間が短い場合、対象の処理における増加率を、対象の処理より１つ前の処理における増加率よりも低くする。この構成によれば、充填完了時間が短くなりすぎることを防ぐことができ、ひいては、充填完了時間を安定させることができる。 Preferably, when the reference filling completion time is shorter than the preset minimum value, the control unit lowers the increase rate in the target process lower than the increase rate in the process immediately before the target process. According to this configuration, it is possible to prevent the filling completion time from becoming too short, and as a result, the filling completion time can be stabilized.
　好ましくは、制御部は、対象の処理よりも前に行われた複数回分の処理における充填完了時間の平均値を参考充填完了時間として、増加率を設定する。この構成によれば、より信頼性の高いデータを用いて、増加率を設定することができる。 Preferably, the control unit sets the increase rate using the average value of filling completion times in a plurality of processes performed before the target processing as a reference filling completion time. According to this configuration, the increase rate can be set using data with higher reliability.
　好ましくは、油圧機器は、油圧式クラッチである。油圧式クラッチは、第１プレートと、第２プレートと、ピストンと、油室とを備える。ピストンは、第１プレートを第２プレートに向かって押圧するように構成されている。油室は、ピストンの押圧力を発生させる。圧力制御弁は、油室に供給される作動油の油圧を制御する。 Preferably, the hydraulic device is a hydraulic clutch. The hydraulic clutch includes a first plate, a second plate, a piston, and an oil chamber. The piston is configured to press the first plate toward the second plate. The oil chamber generates a pressing force of the piston. The pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the oil chamber.
　本発明の第２側面に係る油圧制御装置は、油圧機器を制御する装置である。この油圧制御装置は、圧力制御弁と、充填完了検出部と、制御部とを備えている。圧力制御弁は、油圧機器に供給される作動油の油圧を制御する。充填完了検出部は、油圧機器への作動油の充填完了を検出する。制御部は、圧力制御弁の開度を制御する。制御部は、第１時点から第２時点までの間、開度を第１開度とする。なお、第１時点とは、油圧機器へ作動油を供給開始する時点である。そして、制御部は、第２時点から第３時点までの間、開度を第１開度よりも小さい第２開度とする。なお、第３時点とは、充填完了検出部によって作動油の充填完了が検出される時点である。そして、制御部は、参考充填完了時間に基づき、第２開度を設定する。なお、参考充填完了時間とは、対象の処理よりも前に行われた処理における第１時点から第３時点までの時間である。油圧機器は、油圧式クラッチ又は油圧式ブレーキである。油圧機器が油圧式クラッチの場合、上述した処理は変速処理である。また、油圧機器が油圧式ブレーキの場合、上述した処理は制動処理である。 The hydraulic control device according to the second aspect of the present invention is a device that controls hydraulic equipment. The hydraulic control device includes a pressure control valve, a filling completion detection unit, and a control unit. The pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the hydraulic equipment. The filling completion detection unit detects completion of filling of hydraulic oil into the hydraulic device. The control unit controls the opening degree of the pressure control valve. The controller sets the opening degree to the first opening degree from the first time point to the second time point. The first time point is a time point when the supply of hydraulic oil to the hydraulic equipment is started. Then, the control unit sets the opening degree to a second opening degree smaller than the first opening degree from the second time point to the third time point. The third time point is a time point when the completion of filling of the hydraulic oil is detected by the filling completion detection unit. Then, the control unit sets the second opening based on the reference filling completion time. The reference filling completion time is the time from the first time point to the third time point in the process performed before the target process. The hydraulic device is a hydraulic clutch or a hydraulic brake. When the hydraulic device is a hydraulic clutch, the above-described process is a shift process. When the hydraulic device is a hydraulic brake, the above-described process is a braking process.
　この構成によれば、制御部は、参考充填完了時間に基づき、第２時点から第３時点までの開度である第２開度を設定する。この結果、作業車両の乗り心地を損ねることなく充填完了時間を短縮することができる。例えば、制御部は、以前に行われた処理において、充填完了時間が所望の時間よりも長かった場合には、第２開度を前回の処理における第２開度よりも大きくすることによって、対象の処理における充填完了時間を短くすることができる。また、制御部は、以前に行われた処理において、充填完了時間が所望の時間よりも短かった場合には、第２開度を前回の処理における第２開度よりも小さくすることができる。この結果、制御部は、充填完了時間を安定させることができる。したがって、本発明の第２側面に係る油圧制御装置は、作業車両の乗り心地を損ねることなく、充填完了時間を短縮することができる。 According to this configuration, the control unit sets the second opening, which is the opening from the second time point to the third time point, based on the reference filling completion time. As a result, the filling completion time can be shortened without impairing the riding comfort of the work vehicle. For example, in the previously performed process, when the filling completion time is longer than the desired time, the control unit sets the second opening to be larger than the second opening in the previous process. In this process, the filling completion time can be shortened. Moreover, the control part can make a 2nd opening degree smaller than the 2nd opening degree in the last process, when the filling completion time is shorter than desired time in the process performed previously. As a result, the control unit can stabilize the filling completion time. Therefore, the hydraulic control apparatus according to the second aspect of the present invention can shorten the filling completion time without impairing the riding comfort of the work vehicle.
　好ましくは、油圧制御装置は、圧力制御弁の開度を制御する電磁制御弁をさらに備える。制御部は、電磁制御弁に出力する電流値を制御することによって、圧力制御弁の開度を制御する。 Preferably, the hydraulic control device further includes an electromagnetic control valve for controlling the opening degree of the pressure control valve. A control part controls the opening degree of a pressure control valve by controlling the electric current value output to an electromagnetic control valve.
　好ましくは、制御部は、予め設定された最大値よりも参考充填完了時間が長い場合、対象の処理における第２開度を、対象の処理より１つ前の処理における第２開度よりも大きくする。この構成によれば、充填完了時間を短縮することができる。 Preferably, when the reference filling completion time is longer than a preset maximum value, the control unit sets the second opening in the target process to be larger than the second opening in the process immediately before the target process. To do. According to this configuration, the filling completion time can be shortened.
　好ましくは、制御部は、予め設定された最小値よりも参考充填完了時間が短い場合、対象の処理における第２開度を、対象の処理より１つ前の処理における第２開度よりも小さくする。この構成によれば、充填完了時間が短くなりすぎることを防ぐことができ、ひいては、充填完了時間を安定させることができる。 Preferably, when the reference filling completion time is shorter than a preset minimum value, the control unit makes the second opening degree in the target process smaller than the second opening degree in the process immediately before the target process. To do. According to this configuration, it is possible to prevent the filling completion time from becoming too short, and as a result, the filling completion time can be stabilized.
　好ましくは、制御部は、対象の処理よりも前に行われた複数回分の処理における充填完了時間の平均値を参考充填完了時間として、第２開度を設定する。この構成によれば、より信頼性の高いデータを用いて、第２開度を設定することができる。 Preferably, the control unit sets the second opening degree using an average value of filling completion times in a plurality of processings performed before the target processing as a reference filling completion time. According to this configuration, the second opening degree can be set using data with higher reliability.
　好ましくは、油圧機器は、油圧式クラッチである。油圧式クラッチは、第１プレートと、第２プレートと、ピストンと、油室とを備える。ピストンは、第１プレートを第２プレートに向かって押圧するように構成されている。油室は、ピストンの押圧力を発生させる。圧力制御弁は、油室に供給される作動油の油圧を制御する。 Preferably, the hydraulic device is a hydraulic clutch. The hydraulic clutch includes a first plate, a second plate, a piston, and an oil chamber. The piston is configured to press the first plate toward the second plate. The oil chamber generates a pressing force of the piston. The pressure control valve controls the hydraulic pressure of the hydraulic oil supplied to the oil chamber.
　本発明によれば、作業車両の乗り心地を損ねることなく充填完了時間を短縮することができる。 According to the present invention, the filling completion time can be shortened without impairing the riding comfort of the work vehicle.
作業車両の構成を示すブロック図。The block diagram which shows the structure of a working vehicle. クラッチ制御弁装置の構成を示す断面図。Sectional drawing which shows the structure of a clutch control valve apparatus. クラッチ制御弁装置の構成を示す断面図。Sectional drawing which shows the structure of a clutch control valve apparatus. 変速処理を行う際の制御部の動作を説明するためのフローチャート。The flowchart for demonstrating operation | movement of the control part at the time of performing gear shifting process. 油圧制御での指令電流と供給油圧の変化を示すグラフ。The graph which shows the change of command current and supply oil pressure in oil pressure control. 開度の増加率を設定する際の制御部の動作を説明するためのフローチャート。The flowchart for demonstrating operation | movement of the control part at the time of setting the increase rate of an opening degree. 変形例１における変速処理を行う際の制御部の動作を説明するためのフローチャート。9 is a flowchart for explaining the operation of a control unit when performing a shift process in Modification 1; 変形例１における油圧制御での指令電流と供給油圧の変化を示すグラフ。The graph which shows the change of the command current in the hydraulic control in the modification 1, and the supply hydraulic pressure. 変形例１における第２開度を設定する際の制御部の動作を説明するためのフローチャート。The flowchart for demonstrating operation | movement of the control part at the time of setting the 2nd opening degree in the modification 1. FIG. 油圧式クラッチを示す概略図。Schematic which shows a hydraulic clutch. 油圧式ブレーキを示す概略図。Schematic which shows a hydraulic brake.
　以下、本発明に係る油圧制御装置が適用された作業車両の実施形態について図面を参照しつつ説明する。図１は、作業車両の構成を示すブロック図である。 Hereinafter, an embodiment of a work vehicle to which a hydraulic control device according to the present invention is applied will be described with reference to the drawings. FIG. 1 is a block diagram illustrating a configuration of a work vehicle.
　〔全体構成〕
　図１に示すように、作業車両１は、エンジン５、動力伝達機構６、走行機構９、油圧ポンプ８、油圧制御装置２、操作部１０、及び制御部３などを備えている。 〔overall structure〕
As shown in FIG. 1, the work vehicle 1 includes an engine 5, a power transmission mechanism 6, a traveling mechanism 9, a hydraulic pump 8, a hydraulic control device 2, an operation unit 10, a control unit 3, and the like.
　エンジン５には、燃料噴射ポンプ８３が付設されており、燃料噴射ポンプ８３からエンジン５に燃料が供給される。その供給量は、制御部３から電子ガバナ８２に出力される指令信号によって制御される。なお、エンジン５の回転数は、エンジン回転数センサ８１によって検知され、検知信号として制御部３へ送られる。制御部３は、電子ガバナ８２へ指令信号を送ることにより、エンジン５への燃料の供給量を制御して、エンジン５の回転数を制御することができる。 The engine 5 is provided with a fuel injection pump 83, and fuel is supplied from the fuel injection pump 83 to the engine 5. The supply amount is controlled by a command signal output from the control unit 3 to the electronic governor 82. The rotational speed of the engine 5 is detected by the engine rotational speed sensor 81 and sent to the control unit 3 as a detection signal. The control unit 3 can control the number of revolutions of the engine 5 by sending a command signal to the electronic governor 82 to control the amount of fuel supplied to the engine 5.
　動力伝達機構６は、エンジン５からの駆動力を駆動輪１２に伝達するための機構であり、トルクコンバータ６２およびトランスミッション６０を有している。 The power transmission mechanism 6 is a mechanism for transmitting the driving force from the engine 5 to the drive wheels 12 and includes a torque converter 62 and a transmission 60.
　トルクコンバータ６２は、エンジン５の出力側に接続されている。トルクコンバータ６２には、トルクコンバータ６２の入力軸と出力軸とを直結するロックアップクラッチ７０が設けられている。 The torque converter 62 is connected to the output side of the engine 5. The torque converter 62 is provided with a lockup clutch 70 that directly connects the input shaft and the output shaft of the torque converter 62.
　ロックアップクラッチ７０は、油圧ポンプ８から供給される油圧により駆動される油圧式クラッチである。制御部３は、ロックアップクラッチ制御弁装置２８に指令信号を送信することにより、ロックアップクラッチ７０に供給される油圧を制御する。 The lock-up clutch 70 is a hydraulic clutch that is driven by the hydraulic pressure supplied from the hydraulic pump 8. The control unit 3 controls the hydraulic pressure supplied to the lockup clutch 70 by transmitting a command signal to the lockup clutch control valve device 28.
　トランスミッション６０は、各種のクラッチ６３～６９および複数の変速ギア（図示省略）などを有している。 The transmission 60 has various clutches 63 to 69 and a plurality of transmission gears (not shown).
　各種のクラッチ６３～６９は、油圧ポンプ８から供給される油圧により駆動される油圧式クラッチであり、ＦＬクラッチ６３、ＦＨクラッチ６４、Ｒクラッチ６５、１ｓｔクラッチ６６、２ｎｄクラッチ６７、３ｒｄクラッチ６８、４ｔｈクラッチ６９がある。 The various clutches 63 to 69 are hydraulic clutches that are driven by the hydraulic pressure supplied from the hydraulic pump 8, and are FL clutch 63, FH clutch 64, R clutch 65, 1st clutch 66, 2nd clutch 67, 3rd clutch 68, There is a 4th clutch 69.
　図１０に示すように、上記各種のクラッチ６３～６９は、第１プレート６３１、第２プレート６３２、ピストン６３４、及び油室６３５を有している。第１プレート６３１及び第２プレート６３２は、軸方向（図１０の左右方向）に移動可能である。油室６３４に作動油が供給されるとピストン６３３が移動し、この結果、第１プレート６３１と第２プレート６３２とが連結して動力が伝達される。なお、第１プレート６３１及び第２プレート６３２は複数設けられていて多板クラッチを構成している。 As shown in FIG. 10, the various clutches 63 to 69 include a first plate 631, a second plate 632, a piston 634, and an oil chamber 635. The first plate 631 and the second plate 632 are movable in the axial direction (left-right direction in FIG. 10). When hydraulic oil is supplied to the oil chamber 634, the piston 633 moves, and as a result, the first plate 631 and the second plate 632 are connected to transmit power. A plurality of first plates 631 and second plates 632 are provided to constitute a multi-plate clutch.
　ＦＬクラッチ６３およびＦＨクラッチ６４は、車両が前進する場合に係合状態となる。Ｒクラッチ６５は、車両が後進する場合に係合状態となる。１ｓｔクラッチ６６、２ｎｄクラッチ６７、３ｒｄクラッチ６８、４ｔｈクラッチ６９は、それぞれ対応する変速ギアに駆動力を伝達する場合に係合状態となる。 The FL clutch 63 and the FH clutch 64 are engaged when the vehicle moves forward. The R clutch 65 is engaged when the vehicle moves backward. The 1st clutch 66, the 2nd clutch 67, the 3rd clutch 68, and the 4th clutch 69 are engaged when transmitting the driving force to the corresponding transmission gears.
　このトランスミッション６０では、前進時には、ＦＬクラッチ６３およびＦＨクラッチ６４のいずれかと、１ｓｔクラッチ６６～４ｔｈクラッチ６９のいずれかと、の組合せによって、１～８速の速度段の選択が可能となっている。また、後進時には、Ｒクラッチ６５と、１ｓｔクラッチ６６～４ｔｈクラッチ６９のいずれかと、の組合せによって、１～４速の速度段の選択が可能となっている。 In this transmission 60, when moving forward, the speed stage of 1 to 8 speed can be selected by combining any of the FL clutch 63 and the FH clutch 64 and any of the 1st clutch 66 to the 4th clutch 69. Further, at the time of reverse travel, the speed stage of 1st to 4th speed can be selected by a combination of the R clutch 65 and any of the 1st clutch 66 to the 4th clutch 69.
　なお、ＦＬクラッチ６３、ＦＨクラッチ６４、及びＲクラッチ６５への入力回転数は、入力回転数センサ８５によって検知され、検知信号として制御部３へ送られる。また、ＦＬクラッチ６３、ＦＨクラッチ６４、及びＲクラッチ６５からの出力回転数は、出力回転数センサ８６によって検知され、検知信号として制御部３へ送られる。 In addition, the input rotation speed to the FL clutch 63, the FH clutch 64, and the R clutch 65 is detected by the input rotation speed sensor 85 and sent to the control unit 3 as a detection signal. Further, the output rotational speeds from the FL clutch 63, the FH clutch 64, and the R clutch 65 are detected by the output rotational speed sensor 86 and sent to the control unit 3 as a detection signal.
　走行機構９は、エンジン５からの駆動力を用いて車両を走行させるための機構である。走行機構９は、動力伝達機構６を介してエンジン５からの駆動力が伝達される。走行機構９は、最終減速機（図示省略）、及び駆動輪１２を有している。トランスミッション６０から出力された駆動力は、最終減速機を介して駆動輪１２に伝達される。この結果、駆動輪１２が回転駆動されて作業車両が走行する。 The traveling mechanism 9 is a mechanism for traveling the vehicle using the driving force from the engine 5. The traveling mechanism 9 is transmitted with the driving force from the engine 5 via the power transmission mechanism 6. The travel mechanism 9 has a final reduction gear (not shown) and drive wheels 12. The driving force output from the transmission 60 is transmitted to the drive wheels 12 through the final reduction gear. As a result, the drive wheel 12 is driven to rotate and the work vehicle travels.
　油圧ポンプ８は、エンジン５からの駆動力によって駆動され、各種クラッチ６３～７０に供給される油圧を発生させる。 The hydraulic pump 8 is driven by the driving force from the engine 5 and generates hydraulic pressure supplied to the various clutches 63 to 70.
　操作部１０は、作業車両１の走行や作業機（図示省略）などを制御するためにオペレータによって作業される部分である。操作部１０は、アクセルペダル１４、インチングペダル１３、及び変速レバー１１などの操作部材を有している。 The operation unit 10 is a part that is operated by an operator in order to control the traveling of the work vehicle 1 and a work machine (not shown). The operation unit 10 includes operation members such as an accelerator pedal 14, an inching pedal 13, and a shift lever 11.
　アクセルペダル１４は、エンジン回転数を所望の回転数に設定するために操作される操作部材である。インチングペダル１３は、ＦＬクラッチ６３、ＦＨクラッチ６４、又はＲクラッチ６５に滑りを生じさせて車速を低減させるために操作される操作部材である。変速レバー１１は、オペレータが手動でトランスミッション６０の変速を行うために操作される操作部材である。操作部１０の各操作部材が操作されると、その操作に対応した操作信号が制御部３へ送られる。 The accelerator pedal 14 is an operation member that is operated to set the engine speed to a desired speed. The inching pedal 13 is an operation member that is operated to cause the FL clutch 63, the FH clutch 64, or the R clutch 65 to slip to reduce the vehicle speed. The shift lever 11 is an operation member that is operated by an operator to manually shift the transmission 60. When each operation member of the operation unit 10 is operated, an operation signal corresponding to the operation is sent to the control unit 3.
　油圧制御装置２は、油圧ポンプ８によって生成される油圧によって上述した各種のクラッチ６３～７０を制御するための装置である。油圧制御装置２は、制御弁装置２１～２８および制御部３を有する。 The hydraulic control device 2 is a device for controlling the various clutches 63 to 70 described above by the hydraulic pressure generated by the hydraulic pump 8. The hydraulic control device 2 includes control valve devices 21 to 28 and a control unit 3.
　制御弁装置２１～２８は、制御部３によって電気的に制御されることにより、油圧を調整することができる電磁比例制御弁であり、第１～第７クラッチ制御弁装置２１～２７、ロックアップクラッチ制御弁装置２８などがある。ロックアップクラッチ制御弁装置２８は、ロックアップクラッチ７０に供給される油圧を調整する。第１～第７クラッチ制御弁装置２１～２７は、上述した各種のクラッチ６３～６９へ供給される油圧を調整する。 The control valve devices 21 to 28 are electromagnetic proportional control valves capable of adjusting the hydraulic pressure by being electrically controlled by the control unit 3, and include first to seventh clutch control valve devices 21 to 27, lock-ups. There is a clutch control valve device 28 and the like. The lockup clutch control valve device 28 adjusts the hydraulic pressure supplied to the lockup clutch 70. The first to seventh clutch control valve devices 21 to 27 adjust the hydraulic pressure supplied to the various clutches 63 to 69 described above.
　具体的には、第１クラッチ制御弁装置２１は、ＦＬクラッチ６３へ供給される油圧を調整する。第２クラッチ制御弁装置２２は、ＦＨクラッチ６４へ供給される油圧を調整する。第３クラッチ制御弁装置２３は、Ｒクラッチ６５へ供給される油圧を調整する。第４クラッチ制御弁装置２４は、１ｓｔクラッチ６６へ供給される油圧を調整する。第５クラッチ制御弁装置２５は、２ｎｄクラッチ６７へ供給される油圧を調整する。第６クラッチ制御弁装置２６は、３ｒｄクラッチ６８へ供給される油圧を調整する。第７クラッチ制御弁装置２７は、４ｔｈクラッチ６９へ供給される油圧を調整する。 Specifically, the first clutch control valve device 21 adjusts the hydraulic pressure supplied to the FL clutch 63. The second clutch control valve device 22 adjusts the hydraulic pressure supplied to the FH clutch 64. The third clutch control valve device 23 adjusts the hydraulic pressure supplied to the R clutch 65. The fourth clutch control valve device 24 adjusts the hydraulic pressure supplied to the first clutch 66. The fifth clutch control valve device 25 adjusts the hydraulic pressure supplied to the 2nd clutch 67. The sixth clutch control valve device 26 adjusts the hydraulic pressure supplied to the 3rd clutch 68. The seventh clutch control valve device 27 adjusts the hydraulic pressure supplied to the 4th clutch 69.
　制御部３は、操作部１０からの操作信号、又は各種センサからの検知信号などに基づいて、第１～第７クラッチ制御弁装置２１～２７を制御することにより、車両の状態に適した変速制御を行うことができる。 The control unit 3 controls the first to seventh clutch control valve devices 21 to 27 on the basis of an operation signal from the operation unit 10, detection signals from various sensors, or the like, so that a speed change suitable for the state of the vehicle is performed. Control can be performed.
　例えば、制御部３は、第１クラッチ制御弁装置２１へ指令信号を送信して、ＦＬクラッチ６３へ油圧を供給する。そして、制御部３は、第７クラッチ制御弁装置２７へ指令信号を送信して、４ｔｈクラッチ６９へ油圧を供給する。これによって、ＦＬクラッチ６３および４ｔｈクラッチ６９が係合状態となり、７速の速度段を選択することができる。 For example, the control unit 3 transmits a command signal to the first clutch control valve device 21 and supplies hydraulic pressure to the FL clutch 63. Then, the controller 3 sends a command signal to the seventh clutch control valve device 27 to supply hydraulic pressure to the 4th clutch 69. As a result, the FL clutch 63 and the 4th clutch 69 are engaged, and the seventh speed stage can be selected.
　他にも、制御部３は、第２クラッチ制御弁装置２２へ指令信号を送信して、ＦＨクラッチ６４へ油圧を供給する。そして、制御部３は、第４クラッチ制御弁装置２４へ指令信号を送信して、１ｓｔクラッチ６６へ油圧を供給する。これによって、ＦＨクラッチ６４および１ｓｔクラッチ６６が係合状態となり、２速の速度段を選択することができる。 In addition, the control unit 3 transmits a command signal to the second clutch control valve device 22 to supply hydraulic pressure to the FH clutch 64. Then, the control unit 3 transmits a command signal to the fourth clutch control valve device 24 to supply hydraulic pressure to the first clutch 66. As a result, the FH clutch 64 and the first clutch 66 are engaged, and the second speed stage can be selected.
　また、制御部３は、アクセルペダル１４からの操作信号とエンジン回転数センサ８１によって検知されたエンジン回転数とに基づいて、エンジン５への燃料の供給量を決定する。そして、制御部３は、決定された供給量に対応した指令信号を電子ガバナ８２に送信する。これによって、燃料噴射ポンプ８３からの燃料噴射量が、アクセルペダル１４の操作量に見合った量に調整され、エンジン回転数が制御される。これによって、オペレータは、作業機の出力や車両の速度を制御することができる。 Also, the control unit 3 determines the amount of fuel supplied to the engine 5 based on the operation signal from the accelerator pedal 14 and the engine speed detected by the engine speed sensor 81. Then, the control unit 3 transmits a command signal corresponding to the determined supply amount to the electronic governor 82. Thus, the fuel injection amount from the fuel injection pump 83 is adjusted to an amount commensurate with the operation amount of the accelerator pedal 14, and the engine speed is controlled. Thus, the operator can control the output of the work machine and the speed of the vehicle.
　また、制御部３は、インチングペダル１３が操作されている場合には、インチングペダル１３からの操作信号に基づいて、第１クラッチ制御弁装置２１、第２クラッチ制御弁装置２２、又は第３クラッチ制御弁装置２３への指令信号を調整することによって、ＦＬクラッチ６３、ＦＨクラッチ６４、又はＲクラッチ６５へ供給される油圧を低減させる。これによって、動力伝達機構６から走行機構９へと伝達される駆動力が低減され、車速が低減する。 Further, when the inching pedal 13 is operated, the control unit 3 determines whether the first clutch control valve device 21, the second clutch control valve device 22, or the third clutch based on the operation signal from the inching pedal 13. By adjusting the command signal to the control valve device 23, the hydraulic pressure supplied to the FL clutch 63, the FH clutch 64 or the R clutch 65 is reduced. As a result, the driving force transmitted from the power transmission mechanism 6 to the traveling mechanism 9 is reduced, and the vehicle speed is reduced.
　〔制御弁装置の構成〕
　次に、制御弁装置２１～２８の構成を図２に基づいて説明する。図２は、第１クラッチ制御弁装置２１の断面図である。図２では、第１クラッチ制御弁装置２１を図示しているが、他の制御弁装置２２～２８も同様の構成である。 [Configuration of control valve device]
Next, the configuration of the control valve devices 21 to 28 will be described with reference to FIG. FIG. 2 is a cross-sectional view of the first clutch control valve device 21. Although the first clutch control valve device 21 is illustrated in FIG. 2, the other control valve devices 22 to 28 have the same configuration.
　図２に示すように、第１クラッチ制御弁装置２１は、ハウジング２０、圧力制御弁１５、電磁制御弁１８、及び充填完了検出部１６を有する。 As shown in FIG. 2, the first clutch control valve device 21 includes a housing 20, a pressure control valve 15, an electromagnetic control valve 18, and a filling completion detection unit 16.
　ハウジング２０には、入力ポート１７、出力ポート１９、第１ドレンポート３１、第２ドレンポート３２が形成されている。入力ポート１７には油圧ポンプ８が接続される。出力ポート１９にはＦＬクラッチ６３が接続される。第１ドレンポート３１および第２ドレンポート３２には、タンク（図示省略）がそれぞれ接続される。 The housing 20 is formed with an input port 17, an output port 19, a first drain port 31, and a second drain port 32. A hydraulic pump 8 is connected to the input port 17. An FL clutch 63 is connected to the output port 19. A tank (not shown) is connected to each of the first drain port 31 and the second drain port 32.
　圧力制御弁１５は、ＦＬクラッチ６３に供給される作動油の油圧を調整する部材である。圧力制御弁１５は、第１スプール３４を有している。 The pressure control valve 15 is a member that adjusts the hydraulic pressure of the hydraulic oil supplied to the FL clutch 63. The pressure control valve 15 has a first spool 34.
　第１スプール３４は、ハウジング２０内において軸方向（図２における左右方向）に移動可能に設けられている。ハウジング２０内にはバルブ室３５が形成されている。第１スプール３４の軸方向における略中央部は、バルブ室３５内に位置している。第１スプール３４の軸方向一端部（以下、「基端部」と呼ぶ）の内部にはフィードバック室３６が形成されている。 The first spool 34 is provided in the housing 20 so as to be movable in the axial direction (left-right direction in FIG. 2). A valve chamber 35 is formed in the housing 20. A substantially central portion in the axial direction of the first spool 34 is located in the valve chamber 35. A feedback chamber 36 is formed inside one axial end portion (hereinafter referred to as “base end portion”) of the first spool 34.
　バルブ室３５とフィードバック室３６とは、第１スプール３４内に形成された流路３７を介して連通している。また、フィードバック室３６とハウジング２０の内壁面との間には、バネ３８が設けられている。このバネ３８によって、第１スプール３４は軸方向他端部（以下、「先端部」と呼ぶ）側に付勢されている。 The valve chamber 35 and the feedback chamber 36 communicate with each other via a flow path 37 formed in the first spool 34. A spring 38 is provided between the feedback chamber 36 and the inner wall surface of the housing 20. The first spool 34 is urged by the spring 38 toward the other axial end portion (hereinafter referred to as “tip portion”).
　第１スプール３４の先端部の内部には、パイロット室３９が形成されている。また、第１スプール３４の先端部の端面には、受圧面４０が形成されている。なお、第１スプール３４の受圧面４０には、パイロット室３９と後述する流路４４とを連通するための溝部（図示省略）が形成されている。 A pilot chamber 39 is formed inside the tip of the first spool 34. A pressure receiving surface 40 is formed on the end surface of the front end portion of the first spool 34. A groove portion (not shown) is formed in the pressure receiving surface 40 of the first spool 34 for communicating the pilot chamber 39 and a flow path 44 described later.
　バネ３８の付勢力によって第１スプール３４が先端側に位置しているとき、すなわち、受圧面４０が後述の電磁制御弁１８の弁シート体４１に当接しているとき、第１スプール３４は、入力ポート１７とバルブ室３５とを遮断し、バルブ室３５と第２ドレンポート３２とを連通させる。 When the first spool 34 is positioned on the distal end side by the biasing force of the spring 38, that is, when the pressure receiving surface 40 is in contact with a valve seat body 41 of the electromagnetic control valve 18 described later, the first spool 34 is The input port 17 and the valve chamber 35 are shut off, and the valve chamber 35 and the second drain port 32 are communicated.
　一方、図３に示すように、バネ３８の付勢力に抗して第１スプール３４が基端側に位置しているときには、第１スプール３４は、入力ポート１７とバルブ室３５との間を連通させ、バルブ室３５と第２ドレンポート３２との間を遮断する。 On the other hand, as shown in FIG. 3, when the first spool 34 is positioned on the base end side against the biasing force of the spring 38, the first spool 34 moves between the input port 17 and the valve chamber 35. The valve chamber 35 and the second drain port 32 are blocked by communication.
　図２に示すように、ハウジング２０内には流路４３が形成されている。この流路４３を介して、入力ポート１７と、受圧面４０が配置されている空間と、が連通している。流路４３は、２つの流路４４，４５を有している。流路４５は入力ポート１７側の部分であり、流路４４は受圧面４０側の部分である。流路４５は、流路４４よりも径が大きい。 As shown in FIG. 2, a flow path 43 is formed in the housing 20. The input port 17 and the space in which the pressure receiving surface 40 is disposed communicate with each other through the flow path 43. The flow path 43 has two flow paths 44 and 45. The flow path 45 is a part on the input port 17 side, and the flow path 44 is a part on the pressure receiving surface 40 side. The channel 45 has a larger diameter than the channel 44.
　この流路４５と流路４４との接続部分には、ねじ栓４６が設けられている。ねじ栓４６のねじ部は、小径の流路４４にねじ込まれており、ねじ栓４６の頭部は、大径の流路４５内に位置している。このため、ねじ栓４６の頭部の外周面と流路４５の内周面との間には、環状の微小な隙間４７が形成されている。また、ねじ栓４６の内部には、絞り流路４８が形成されている。絞り流路４８は、隙間４７と流路４４とを連通する。 A screw plug 46 is provided at a connection portion between the flow path 45 and the flow path 44. The threaded portion of the screw plug 46 is screwed into the small-diameter channel 44, and the head of the screw plug 46 is located in the large-diameter channel 45. For this reason, an annular minute gap 47 is formed between the outer peripheral surface of the head of the screw plug 46 and the inner peripheral surface of the flow path 45. In addition, a throttle channel 48 is formed inside the screw plug 46. The throttle channel 48 communicates the gap 47 and the channel 44.
　電磁制御弁１８は、弁シート体４１と、弁体５０と、連結部材５１と、比例ソレノイド５２とを有している。 The electromagnetic control valve 18 includes a valve seat body 41, a valve body 50, a connecting member 51, and a proportional solenoid 52.
　弁シート体４１は、第１スプール３４の先端部に対向して配置されており、連結部材５１の一端に固定されている。弁シート体４１の基端部にはパイロット室５３が形成されている。弁シート体４１の先端面（図２の左端面）と第１スプール３４の先端面とは、当接および離反することができる。弁シート体４１のパイロット室５３と、第１スプール３４のパイロット室３９とは、連通している。 The valve seat body 41 is disposed to face the tip of the first spool 34 and is fixed to one end of the connecting member 51. A pilot chamber 53 is formed at the base end portion of the valve seat body 41. The front end surface of the valve seat body 41 (the left end surface in FIG. 2) and the front end surface of the first spool 34 can be brought into contact with and separated from each other. The pilot chamber 53 of the valve seat body 41 and the pilot chamber 39 of the first spool 34 communicate with each other.
　弁シート体４１の内部には、弁収納室５４が形成されている。また、弁シート体４１内には、軸方向に延びるドレン流路５５と、径方向に延びるドレン流路５６とがそれぞれ形成されている。 A valve storage chamber 54 is formed inside the valve seat body 41. In the valve seat body 41, a drain channel 55 extending in the axial direction and a drain channel 56 extending in the radial direction are formed.
　ドレン流路５５は、パイロット室５３と弁収納室５４とを連通させる。ドレン流路５６は、弁収納室５４を通り径方向に弁シート体４１を貫通している。ドレン流路５６は、ドレン流路５５と弁シート体４１の外周側とを連通させており、ドレン流路５６の一方の端部は、第１ドレンポート３１に連通している。また、弁収納室５４の左側内壁面には、弁シート面５７が形成されている。 The drain channel 55 allows the pilot chamber 53 and the valve storage chamber 54 to communicate with each other. The drain passage 56 passes through the valve storage chamber 54 and penetrates the valve seat body 41 in the radial direction. The drain channel 56 communicates the drain channel 55 with the outer peripheral side of the valve seat body 41, and one end of the drain channel 56 communicates with the first drain port 31. A valve seat surface 57 is formed on the left inner wall surface of the valve storage chamber 54.
　弁体５０は、球状の形状を有しており、弁収納室５４において左右方向に移動可能に収納されている。 The valve body 50 has a spherical shape and is stored in the valve storage chamber 54 so as to be movable in the left-right direction.
　連結部材５１は、弁シート体４１と比例ソレノイド５２とを連結している。連結部材５１の内部には、軸方向（図２における左右方向）に進退可能に設けられたプランジャ５８が挿入されている。プランジャ５８の先端部は、弁体５０に当接している。 The connecting member 51 connects the valve seat body 41 and the proportional solenoid 52. A plunger 58 is inserted into the connecting member 51 so as to be able to advance and retreat in the axial direction (left and right direction in FIG. 2). The tip of the plunger 58 is in contact with the valve body 50.
　比例ソレノイド５２は、制御部３から指令電流が入力されることによって、プランジャ５８を軸方向に進退させる。 The proportional solenoid 52 advances and retracts the plunger 58 in the axial direction when a command current is input from the control unit 3.
　制御部３から比例ソレノイド５２への指令電流がゼロである場合、図２に示すように、プランジャ５８は比例ソレノイド５２側に移動して引き込まれた状態となる。このため、弁体５０は、パイロット室３９，５３内の油圧によって押されて、弁シート面５７から離れる。これによりドレン流路５５とドレン流路５６が連通する。 When the command current from the control unit 3 to the proportional solenoid 52 is zero, the plunger 58 is moved to the proportional solenoid 52 side and pulled in as shown in FIG. For this reason, the valve body 50 is pushed by the hydraulic pressure in the pilot chambers 39 and 53 and is separated from the valve seat surface 57. As a result, the drain channel 55 and the drain channel 56 communicate with each other.
　このため、油圧ポンプ８からの油は、入力ポート１７、流路４５の隙間４７、ねじ栓４６の絞り流路４８、流路４４、パイロット室３９，５３、ドレン流路５５、ドレン流路５６、第１ドレンポート３１を順に流れてタンクへ排出される。この場合、パイロット室３９内のパイロット圧が立たないため、第１スプール３４は、バネ３８の付勢力によって右側に移動する。そして、第１スプール３４は、弁シート体４１に当接して位置決めされる。 Therefore, the oil from the hydraulic pump 8 is supplied to the input port 17, the gap 47 of the flow path 45, the throttle flow path 48 of the screw plug 46, the flow path 44, the pilot chambers 39 and 53, the drain flow path 55, and the drain flow path 56. The first drain port 31 sequentially flows and is discharged to the tank. In this case, since the pilot pressure in the pilot chamber 39 is not established, the first spool 34 moves to the right side by the urging force of the spring 38. The first spool 34 is positioned in contact with the valve seat body 41.
　したがって、入力ポート１７とバルブ室３５との間は閉じられると共に、バルブ室３５と第２ドレンポート３２との間は連通し、バルブ室３５の圧は立たない。バルブ室３５は、出力ポート１９を介してＦＬクラッチ６３に連通しているため、ＦＬクラッチ６３内に油圧は発生しない。このため、ＦＬクラッチ６３は開放状態となる。 Therefore, the input port 17 and the valve chamber 35 are closed, and the valve chamber 35 and the second drain port 32 communicate with each other, so that the pressure in the valve chamber 35 does not stand. Since the valve chamber 35 communicates with the FL clutch 63 via the output port 19, no hydraulic pressure is generated in the FL clutch 63. For this reason, the FL clutch 63 is released.
　次に、制御部３から比例ソレノイド５２に所定値の指令電流が印加されると、プランジャ５８は、指令電流の大きさに応じた力で弁体５０側に突き出される。そして、プランジャ５８は、弁体５０を弁シート面５７に押しつける。この結果、図３に示すように、ドレン流路５５，５６間が絞られて、パイロット室３９と第１ドレンポート３１の間が絞られる。 Next, when a command current having a predetermined value is applied from the control unit 3 to the proportional solenoid 52, the plunger 58 is protruded toward the valve body 50 with a force corresponding to the magnitude of the command current. Then, the plunger 58 presses the valve body 50 against the valve seat surface 57. As a result, as shown in FIG. 3, the space between the drain flow paths 55 and 56 is narrowed, and the space between the pilot chamber 39 and the first drain port 31 is narrowed.
　これによって、パイロット室３９には指令電流の大きさに応じたパイロット圧が立つ。すると、第１スプール３４は、このパイロット圧とバネ３８の付勢力とがバランスする位置まで基端側に移動する。この状態では、バルブ室３５と第２ドレンポート３２との間は閉じられ、バルブ室３５と入力ポート１７との間が連通される。このため、油圧ポンプ８からの油は、入力ポート１７、バルブ室３５、及び出力ポート１９を経由して、ＦＬクラッチ６３に流れ込む。なお、このときの圧力制御弁１５の開度は、制御部３から比例ソレノイド５２への指令電流値の大きさに応じて変化する。また、本実施形態において、圧力制御弁１５の開度とは第１スプール３４の移動量を意味する。圧力制御弁１５の開度が大きいと、第１スプール３４が図２の左側へより移動し、入力ポート１７から出力ポート１９へ流れる作動油の流量が増える。 Thus, a pilot pressure corresponding to the magnitude of the command current is established in the pilot chamber 39. Then, the first spool 34 moves to the base end side to a position where the pilot pressure and the biasing force of the spring 38 are balanced. In this state, the valve chamber 35 and the second drain port 32 are closed, and the valve chamber 35 and the input port 17 communicate with each other. For this reason, the oil from the hydraulic pump 8 flows into the FL clutch 63 via the input port 17, the valve chamber 35, and the output port 19. Note that the opening degree of the pressure control valve 15 at this time changes according to the magnitude of the command current value from the control unit 3 to the proportional solenoid 52. In the present embodiment, the opening degree of the pressure control valve 15 means the amount of movement of the first spool 34. When the opening degree of the pressure control valve 15 is large, the first spool 34 moves from the left side in FIG. 2 and the flow rate of the hydraulic oil flowing from the input port 17 to the output port 19 increases.
　図２に示すように、充填完了検出部１６は、ＦＬクラッチ６３への作動油の充填完了を検出する部材である。詳細には、充填完了検出部１６は、第２スプール１６１、検出ピン１６２、固定部材１６４、及び出力ピン１６６を有する。 As shown in FIG. 2, the filling completion detection unit 16 is a member that detects completion of filling of the hydraulic oil into the FL clutch 63. Specifically, the filling completion detection unit 16 includes a second spool 161, a detection pin 162, a fixing member 164, and an output pin 166.
　第２スプール１６１は、ハウジング２０内において軸方向（図２における左右方向）に移動可能に設けられている。なお、第２スプール１６１は、フランジ部１６１ａを有している。このフランジ部１６１ａがハウジング２０の肩部２０１と当接することによって、第２スプール１６１は、図２の左方向への移動が規制される。 The second spool 161 is provided in the housing 20 so as to be movable in the axial direction (left-right direction in FIG. 2). The second spool 161 has a flange portion 161a. When the flange portion 161a comes into contact with the shoulder portion 201 of the housing 20, the second spool 161 is restricted from moving leftward in FIG.
　第２スプール１６１は、内部に収容室１６１ｂを有している。この収容室１６１ｂ内には、検出ピン１６２と、バネ１６３とが収容されている。検出ピン１６２は、バネ１６３によって、右側に付勢されている。検出ピン１６２の右端部は、第２スプール１６１を貫通して右側に突出している。 The second spool 161 has a storage chamber 161b inside. A detection pin 162 and a spring 163 are accommodated in the accommodation chamber 161b. The detection pin 162 is biased to the right by a spring 163. The right end of the detection pin 162 passes through the second spool 161 and protrudes to the right.
　なお、第２スプール１６１は、スプール本体部１６１ｃとキャップ部材１６１ｄとによって、構成されている。スプール本体部１６１ｃは、凹状の収容室１６１ｂを有している。キャップ部材１６１ｄは、収容室１６１ｂを塞ぐように、スプール本体部１６１ｃと連結している。 The second spool 161 is constituted by a spool body 161c and a cap member 161d. The spool body 161c has a concave storage chamber 161b. The cap member 161d is connected to the spool body 161c so as to close the accommodation chamber 161b.
　固定部材１６４は、ハウジング２０の外面に取り付けられている。固定部材１６４と第２スプール１６１との間には、バネ１６５が設けられている。このバネ１６５の付勢力によって、第２スプール１６１が左側に付勢されている。 The fixing member 164 is attached to the outer surface of the housing 20. A spring 165 is provided between the fixing member 164 and the second spool 161. The second spool 161 is urged to the left by the urging force of the spring 165.
　出力ピン１６６は、固定部材１６４に取り付けられており、検出ピン１６２の右側において検出ピン１６２と対向している。出力ピン１６６の右側端部は、図示しないリード線を介して制御部３（図１参照）に接続されている。 The output pin 166 is attached to the fixing member 164 and faces the detection pin 162 on the right side of the detection pin 162. The right end portion of the output pin 166 is connected to the control unit 3 (see FIG. 1) via a lead wire (not shown).
　この充填完了検出部１６は、バルブ室３５に連通する流路５９に面して設けられている。バルブ室３５は出力ポート１９に繋がっているため、ＦＬクラッチ６３への作動油の充填が完了すると、第２スプール１６１がバネ１６５の付勢力に抗して右側へ移動する。この結果、図３に示すように、検出ピン１６２が出力ピン１６６と接触し、制御部３へ充填完了を示す検知信号が送られる。 The filling completion detection unit 16 is provided facing the flow path 59 communicating with the valve chamber 35. Since the valve chamber 35 is connected to the output port 19, when the filling of the hydraulic oil into the FL clutch 63 is completed, the second spool 161 moves to the right against the urging force of the spring 165. As a result, as shown in FIG. 3, the detection pin 162 comes into contact with the output pin 166, and a detection signal indicating completion of filling is sent to the control unit 3.
　〔油圧制御装置による制御〕
　次に、油圧制御装置２によって変速処理を実行する際の制御部３の動作について、図４に示すフローチャートおよび図５に示すタイムチャートを参照して説明する。ここでは、制御対象であるクラッチが開放状態から係合状態に切り換えられる場合を例として説明する。なお、図５において横軸は時間（ｔ）を表している。また、図５（ａ）の縦軸は、比例ソレノイド５２への指令電流（Ｉ）を表している。図５（ｂ）の縦軸は、クラッチへの供給油圧（Ｐ）を表している。 [Control by hydraulic control device]
Next, the operation of the control unit 3 when executing the shift process by the hydraulic control device 2 will be described with reference to the flowchart shown in FIG. 4 and the time chart shown in FIG. Here, a case where the clutch to be controlled is switched from the released state to the engaged state will be described as an example. In FIG. 5, the horizontal axis represents time (t). Further, the vertical axis of FIG. 5A represents the command current (I) to the proportional solenoid 52. The vertical axis | shaft of FIG.5 (b) represents the hydraulic pressure (P) supplied to a clutch.
　クラッチが開放状態である場合には、図５（ａ）に示すように、制御部３から比例ソレノイド５２への指令電流Ｉは零となっている（時点ｔ０）。 When the clutch is in the disengaged state, as shown in FIG. 5A, the command current I from the control unit 3 to the proportional solenoid 52 is zero (time point t0).
　図４に示すように、まず、制御部３は、変速指令が発生したか否かを判定する（ステップＳ１）。なお、制御部３は、エンジン始動後、変速レバー１１からの変速指令が出力されたか否かを継続して監視している（ステップＳ１のＮｏ）。 As shown in FIG. 4, first, the control unit 3 determines whether or not a shift command has been generated (step S1). Note that the control unit 3 continuously monitors whether or not a shift command from the shift lever 11 is output after the engine is started (No in step S1).
　制御部３は、変速指令が発生したと判定すると（ステップＳ１のＹｅｓ）、圧力制御弁１５の開度を制御して、圧力制御弁１５の開度を１開度にする（ステップＳ２）。詳細には、図５に示すように、制御部３は、圧力制御弁１５の開度が第１開度となるよう、第１電流値Ｉ１の指令電流を比例ソレノイド５２に出力する（時点ｔ１）。これにより、第１スプール３４が図２の左側に移動してクラッチへの作動油の供給が開始され、図５（ｂ）に示すように供給油圧が上昇し始める。また、制御部３は、指令電流を第１電流値Ｉ１に維持する。なお、このクラッチへ作動油を供給開始した時点ｔ１を第１時点ｔ１とする。指令電流を第１電流値Ｉ１にしても、油が抜けている回路に作動油を供給するため、指令電流値と同様の勾配で供給油圧は上がらない。 When the control unit 3 determines that a shift command has been generated (Yes in step S1), the control unit 3 controls the opening degree of the pressure control valve 15 to set the opening degree of the pressure control valve 15 to 1 opening degree (step S2). Specifically, as shown in FIG. 5, the control unit 3 outputs a command current of the first current value I1 to the proportional solenoid 52 so that the opening degree of the pressure control valve 15 becomes the first opening degree (time point t1). ). As a result, the first spool 34 moves to the left side of FIG. 2 to start supplying hydraulic oil to the clutch, and the supply hydraulic pressure starts to increase as shown in FIG. 5B. Further, the control unit 3 maintains the command current at the first current value I1. The time point t1 at which the supply of hydraulic oil to the clutch is set as the first time point t1. Even if the command current is set to the first current value I1, the hydraulic oil is supplied to the circuit from which oil has been removed, so the supply hydraulic pressure does not increase with the same gradient as the command current value.
　図４に示すように、次に、制御部３は、タイマーＴのカウントを開始する（ステップＳ３）。すなわち、制御部３は、変速指令が発生したと判定したとき（第１時点ｔ１）からタイマーＴのカウントを開始する。 As shown in FIG. 4, next, the control unit 3 starts counting the timer T (step S3). That is, the control unit 3 starts counting the timer T from the time when it is determined that the shift command has been generated (first time point t1).
　次に、制御部３は、タイマーＴが予め設定された時間Ｔｔに達したか否かを判定する（ステップＳ４）。なお、この時間Ｔｔをトリガ時間と称する。制御部３は、タイマーＴがトリガ時間Ｔｔに達した場合には、次のステップＳ５に進む。また、制御部３は、タイマーＴが所定のトリガ時間Ｔｔに達していない場合は、指令電流は第１電流値Ｉ１のまま維持される。なお、制御部３は、タイマーＴがトリガ時間Ｔｔに達するまで継続して監視を続ける（ステップＳ４のＮｏ）。また、第１時点ｔ１からトリガ時間Ｔｔが経過した時点ｔ２を、第２時点ｔ２とする（図５参照）。トリガ時間Ｔｔにおける指令電流である第１電流値Ｉ１は高く、圧力制御弁１５の第１開度は大きい。このように多量の作動油をクラッチの油室に供給することにより、充填完了時間を短縮することができる。ただし、第１電流値Ｉ１のまま充填が完了すると、多量の作動油が供給されている状態であるため、クラッチ係合時のショックが非常に大きくなってしまう。一方、充填完了時間は油温又は油の劣化などによって変化するため、トリガ時間Ｔｔを充填間際まで延ばすように設定することができない。 Next, the controller 3 determines whether or not the timer T has reached a preset time Tt (step S4). This time Tt is referred to as a trigger time. When the timer T reaches the trigger time Tt, the control unit 3 proceeds to the next step S5. In addition, when the timer T has not reached the predetermined trigger time Tt, the control unit 3 maintains the command current at the first current value I1. The control unit 3 continues to monitor until the timer T reaches the trigger time Tt (No in step S4). Further, a time point t2 when the trigger time Tt has elapsed from the first time point t1 is set as a second time point t2 (see FIG. 5). The first current value I1, which is the command current at the trigger time Tt, is high, and the first opening of the pressure control valve 15 is large. Thus, by supplying a large amount of hydraulic oil to the oil chamber of the clutch, the filling completion time can be shortened. However, when the filling is completed with the first current value I1, a large amount of hydraulic oil is being supplied, so the shock at the time of clutch engagement becomes very large. On the other hand, since the filling completion time varies depending on the oil temperature or the deterioration of the oil, the trigger time Tt cannot be set so as to be extended to just before filling.
　次に、制御部３は、圧力制御弁１５の開度を制御して、圧力制御弁１５の開度を第２開度にする（ステップＳ５）。詳細には、制御部４は、圧力制御弁１５の開度が第２開度となるように、比例ソレノイド５２に出力する指令電流を第２電流値Ｉ２（図５（ａ）参照）に低減させる。これによって、供給油圧が低下する（第２時点ｔ２）。なお、第２開度は、第１開度よりも小さい。また、第２開度は、実験などによって予め設定された固定値とする。第２電流値Ｉ２は、クラッチ係合時のショックを抑えるために設定されており、第１電流値Ｉ１と比べてかなり低い値である。 Next, the control unit 3 controls the opening degree of the pressure control valve 15 to set the opening degree of the pressure control valve 15 to the second opening degree (step S5). Specifically, the control unit 4 reduces the command current output to the proportional solenoid 52 to the second current value I2 (see FIG. 5A) so that the opening degree of the pressure control valve 15 becomes the second opening degree. Let As a result, the supply hydraulic pressure decreases (second time point t2). Note that the second opening is smaller than the first opening. The second opening is a fixed value set in advance by experiments or the like. The second current value I2 is set to suppress a shock when the clutch is engaged, and is a considerably lower value than the first current value I1.
　このように、制御部３は、時点ｔ１からトリガ時間Ｔｔが経過するまで、すなわち、第１時点ｔ１から第２時点ｔ２の間は、第１電流値Ｉ１を出力する。この結果、圧力制御弁１５の開度が第１開度となり、クラッチへ供給される作動油の流量が比較的大きな第１流量となる。また、制御部３は、第１時点ｔ１からトリガ時間Ｔｔが経過した第２時点ｔ２で、第１電流値Ｉ１から第２電流値Ｉ２へ指令電流を低減させる。この結果、圧力制御弁１５の開度が第１開度よりも小さい第２開度となり、クラッチへ供給される作動油の流量は比較的小さな第２流量となる。これにより、図５（ｂ）に示すように、供給油圧が低下する（第２時点ｔ２）。 As described above, the control unit 3 outputs the first current value I1 until the trigger time Tt elapses from the time point t1, that is, from the first time point t1 to the second time point t2. As a result, the opening degree of the pressure control valve 15 becomes the first opening degree, and the flow rate of the hydraulic oil supplied to the clutch becomes the relatively large first flow rate. Further, the control unit 3 reduces the command current from the first current value I1 to the second current value I2 at the second time point t2 when the trigger time Tt has elapsed from the first time point t1. As a result, the opening degree of the pressure control valve 15 becomes a second opening degree smaller than the first opening degree, and the flow rate of the hydraulic oil supplied to the clutch becomes a relatively small second flow rate. Thereby, as shown in FIG.5 (b), supply hydraulic pressure falls (2nd time t2).
　次に、制御部３は、圧力制御弁１５の開度を第２開度から徐々に増加させる（ステップＳ６）。詳細には、制御部３は、出力する指令電流を第２電流値Ｉ２から徐々に増加させる（図５（ａ）参照）。制御部３は、本変速処理よりも前に実行した変速処理における充填完了時間（以下、「参考充填完了時間」と称する）に基づき、このステップＳ６における開度の増加率を設定する。なお、この開度の増加率を設定する際の制御部３の動作の詳細については、後述する。 Next, the control unit 3 gradually increases the opening degree of the pressure control valve 15 from the second opening degree (step S6). Specifically, the control unit 3 gradually increases the command current to be output from the second current value I2 (see FIG. 5A). Based on the filling completion time (hereinafter referred to as “reference filling completion time”) in the speed change process executed before the speed change process, the control unit 3 sets the rate of increase in the opening degree in step S6. The details of the operation of the control unit 3 when setting the increasing rate of the opening will be described later.
　次に、制御部３は、クラッチへの作動油の充填が完了したか否か判定する（ステップＳ７）。詳細には、制御部３は、充填完了検出部１６からの検知信号に基づき、判定する。例えば、充填完了検出部１６は、供給油圧Ｐｆになると、検知信号を制御部３に出力する。なお、制御部３は、継続して充填完了検出部１６からの検知信号を監視している（ステップＳ７のＮｏ）。 Next, the control unit 3 determines whether or not the filling of the hydraulic oil into the clutch is completed (step S7). Specifically, the control unit 3 makes a determination based on the detection signal from the filling completion detection unit 16. For example, the filling completion detection unit 16 outputs a detection signal to the control unit 3 when the supply hydraulic pressure Pf is reached. The control unit 3 continuously monitors the detection signal from the filling completion detection unit 16 (No in step S7).
　制御部３は、充填完了検出部１６からの検知信号に基づき充填完了であると判定すると（ステップＳ７のＹｅｓ）、制御部３は、充填完了時間Ｔｆを記憶する（ステップＳ８）。なお、充填完了時間Ｔｆは、作動油の供給開始（第１時点ｔ１）から充填完了（時点ｔ３）までの時間である（図５参照）。また、充填完了検出部１６によって充填完了が検出された時点ｔ３を、第３時点ｔ３とする。 When the control unit 3 determines that the filling is completed based on the detection signal from the filling completion detection unit 16 (Yes in Step S7), the control unit 3 stores the filling completion time Tf (Step S8). The filling completion time Tf is the time from the start of hydraulic oil supply (first time point t1) to the completion of filling (time point t3) (see FIG. 5). Further, the time point t3 at which the completion of filling is detected by the filling completion detector 16 is set as a third time point t3.
　また、制御部３は、第３時点からモジュレーションを開始する（ステップＳ９）。第３時点ｔ２において、指令電流を予め設定された第３電流値Ｉ３に一旦下げる。指令電流の増加率の変化によってモジュレーションの勾配が変わり、その結果、クラッチ係合時のフィーリングが変わることを防ぐためである。この第３電流値Ｉ３は第２電流値Ｉ２と同じ値であってもよいし、違う値であってもよい。モジュレーションでは、制御部３は、図５（ａ）に示すように、所望の供給油圧がクラッチに供給されるように、指令電流Ｉを変化させる。そして、時点ｔ４で供給油圧が設定クラッチ圧Ｐｔに達して、クラッチの開放状態から係合状態への切替が完了する。以上によって、変速処理が完了する。 Further, the control unit 3 starts modulation from the third time point (step S9). At the third time point t2, the command current is temporarily reduced to a preset third current value I3. This is to prevent the modulation gradient from changing due to the change in the increase rate of the command current, and as a result, to change the feeling when the clutch is engaged. The third current value I3 may be the same value as the second current value I2, or may be a different value. In the modulation, as shown in FIG. 5A, the control unit 3 changes the command current I so that a desired supply hydraulic pressure is supplied to the clutch. At time t4, the supply hydraulic pressure reaches the set clutch pressure Pt, and the switching from the clutch released state to the engaged state is completed. Thus, the shift process is completed.
　次に、開度の増加率を設定する際の制御部３の動作について、図６を参照しつつ説明する。図６は、開度の増加率を設定する際の制御部３の動作を説明するためのフローチャートである。 Next, the operation of the control unit 3 when setting the increase rate of the opening will be described with reference to FIG. FIG. 6 is a flowchart for explaining the operation of the control unit 3 when setting the increase rate of the opening degree.
　図６に示すように、制御部３は、対象の変速処理よりも前に行った変速処理における充填完了時間を参考充填完了時間として読み込む（ステップＳ６１）。なお、制御部３は、変速処理が行われる度に、作動油の供給開始（第１時点ｔ１）から充填完了（第３時点ｔ３）までの時間（充填完了時間）Ｔｆを測定して記憶している。 As shown in FIG. 6, the control unit 3 reads the filling completion time in the shift process performed before the target shift process as a reference filling completion time (step S61). The control unit 3 measures and stores the time (filling completion time) Tf from the start of hydraulic oil supply (first time point t1) to the completion of filling (third time point t3) every time the shift process is performed. ing.
　例えば、制御部３は、対象の変速処理がｎ回目であるとすると、（ｎ－１）回目の変速処理における充填完了時間Ｔｆを参考充填完了時間として読み込んでもよい。他にも、制御部３は、複数回分の充填完了時間Ｔｆの平均値を参考充填完了時間として読み込んでもよい。具体的には、制御部３は、（ｎ－１０）回目の変速処理から（ｎ－１）回目の変速処理までの１０回分の変速処理の充填完了時間Ｔｆを読み込み、これらの平均値を算出する。そして、制御部３は、この平均値を、参考充填完了時間として読み込んでもよい。 For example, if the target shift process is the nth, the control unit 3 may read the filling completion time Tf in the (n−1) th shifting process as the reference filling completion time. In addition, the control unit 3 may read an average value of a plurality of filling completion times Tf as a reference filling completion time. Specifically, the control unit 3 reads the filling completion time Tf of 10 shift processes from the (n-10) th shift process to the (n-1) th shift process, and calculates an average value thereof. To do. And the control part 3 may read this average value as reference filling completion time.
　次に、制御部３は、ステップＳ６１によって読み込まれた参考充填完了時間が、予め設定された範囲内であるか否か判定する（ステップＳ６２）。 Next, the control unit 3 determines whether or not the reference filling completion time read in step S61 is within a preset range (step S62).
　例えば、制御部３は、参考充填完了時間が、予め設定された最大時間以上か否か判定する。制御部３は、参考充填完了時間が最大時間以上であると判定すると、後述するステップＳ６４に移行する。また、制御部３は、参考充填完了時間が最大時間より小さいと判定すると、次に、制御部３は、参考充填完了時間が、予め設定された最小時間以下か否か判定する。制御部３は、参考充填完了時間が予め設定された最小時間以下であると判定すると、後述するステップＳ６４に移行する。また、制御部３は、参考充填完了時間が最小時間より大きいと判定すると、後述するステップＳ６３に移行する。 For example, the control unit 3 determines whether or not the reference filling completion time is equal to or longer than a preset maximum time. When the control unit 3 determines that the reference filling completion time is equal to or longer than the maximum time, the control unit 3 proceeds to step S64 described later. If the control unit 3 determines that the reference filling completion time is smaller than the maximum time, then the control unit 3 determines whether the reference filling completion time is equal to or less than a preset minimum time. When the control unit 3 determines that the reference filling completion time is equal to or shorter than the preset minimum time, the control unit 3 proceeds to step S64 described later. If the control unit 3 determines that the reference filling completion time is larger than the minimum time, the control unit 3 proceeds to step S63 described later.
　制御部３は、参考充填完了時間が予め設定された範囲内であると判定すると（ステップＳ６２のＹｅｓ）、前回の変速処理の際に用いた増加率を設定する（ステップＳ６３）。すなわち、制御部３は、前回の変速処理から開度の増加率を変更しない。 When the control unit 3 determines that the reference filling completion time is within the preset range (Yes in Step S62), the control unit 3 sets the increase rate used in the previous shift process (Step S63). That is, the control unit 3 does not change the increase rate of the opening degree from the previous shift process.
　一方、制御部３は、参考充填完了時間が予め設定された範囲から外れていると判定すると（ステップＳ６２のＮｏ）、対象の変速処理における開度の増加率を変更する（ステップＳ６４）。具体的には、制御部３は、予め設定された範囲の最大値よりも参考充填完了時間の方が長いと判定すると、対象の変速処理における増加率を、前回の変速処理の増加率よりも高くする。また、制御部３は、予め設定された範囲の最小値よりも参考充填完了時間の方が短いと判定すると、対象の変速処理における増加率を、前回の変速処理の増加率よりも低くする。充填完了時の電流値は第２電流値Ｉ２と比べて大きくなるが、クラッチ係合時のショックがさほど大きくならないように増加率を設定している。 On the other hand, when the control unit 3 determines that the reference filling completion time is out of the preset range (No in step S62), the control unit 3 changes the increase rate of the opening degree in the target shift process (step S64). Specifically, when the control unit 3 determines that the reference filling completion time is longer than the maximum value in a preset range, the control unit 3 sets the increase rate in the target shift process to be higher than the increase rate in the previous shift process. Make it high. If the control unit 3 determines that the reference filling completion time is shorter than the minimum value in the preset range, the control unit 3 sets the increase rate in the target shift process to be lower than the increase rate in the previous shift process. The current value at the completion of filling is larger than the second current value I2, but the increase rate is set so that the shock at the time of clutch engagement does not become so large.
　［特徴］
　本実施形態に係る油圧制御装置は、次の特徴を有する。 [Characteristic]
The hydraulic control apparatus according to the present embodiment has the following characteristics.
　制御部３は、参考充填完了時間に基づき、第２時点ｔ２から第３時点ｔ３までの開度の増加率を設定する。この結果、作業車両の乗り心地を損ねることなく充填完了時間を短縮することができる。例えば、制御部３は、以前に行われた変速処理において、充填完了時間が所望の時間よりも長かった場合には、開度の増加率を前回の変速処理における増加率よりも大きくすることによって、対象の変速処理における充填完了時間を短くすることができる。また、制御部３は、以前に行われた変速処理において、充填完了時間が所望の時間よりも短かった場合には、開度の増加率を前回の変速処理における増加率よりも小さくすることができる。この結果、制御部３は、充填完了時間を短縮することができるとともに、充填完了時間を安定させることができる。したがって、油圧制御装置２は、作業車両の乗り心地を損ねることなく、充填完了時間を短縮することができる。なお、第２時点ｔ２から第３時点ｔ３までの開度の増加は、直線的な増加に限らず、２次曲線のような多次曲線であってもよい。 The control unit 3 sets the increasing rate of the opening from the second time point t2 to the third time point t3 based on the reference filling completion time. As a result, the filling completion time can be shortened without impairing the riding comfort of the work vehicle. For example, when the filling completion time is longer than the desired time in the previously performed shift process, the control unit 3 increases the opening degree increase rate from the increase rate in the previous shift process. The filling completion time in the target shift process can be shortened. In addition, when the filling completion time is shorter than the desired time in the previously performed shift process, the control unit 3 may make the opening increase rate smaller than the increase rate in the previous shift process. it can. As a result, the control unit 3 can shorten the filling completion time and can stabilize the filling completion time. Therefore, the hydraulic control device 2 can shorten the filling completion time without impairing the riding comfort of the work vehicle. The increase in the opening from the second time point t2 to the third time point t3 is not limited to a linear increase, and may be a multi-order curve such as a quadratic curve.
　なお、第２時点における開度は第２開度である。すなわち、「第１時点から第２時点までの間」とは、第１時点以上第２時点未満を意味し、第２時点を含まない。同様に、「第２時点から第３時点までの間」とは、第２時点以上第３時点未満を意味し、第３時点を含まない。 The opening at the second time point is the second opening. That is, “between the first time point and the second time point” means that the time is greater than or equal to the first time point and less than the second time point, and does not include the second time point. Similarly, “between the second time point and the third time point” means a period between the second time point and the third time point, and does not include the third time point.
　［変形例］
　以上、本発明の実施形態について説明したが、本発明はこれらに限定されるものではなく、本発明の趣旨を逸脱しない限りにおいて種々の変更が可能である。 [Modification]
As mentioned above, although embodiment of this invention was described, this invention is not limited to these, A various change is possible unless it deviates from the meaning of this invention.
　変形例１
　上記実施形態では、油圧制御装置２の制御部３は、充填完了時間Ｔｆを調整するために、第２時点ｔ２から第３時点ｔ３までの期間における開度の増加率を制御しているが、特にこれに限定されない。例えば、図７に示すように、油圧制御装置の制御部３は、第２開度を制御することによって、充填完了時間Ｔｆを調整することができる。 Modification 1
In the above embodiment, the controller 3 of the hydraulic control device 2 controls the rate of increase of the opening during the period from the second time point t2 to the third time point t3 in order to adjust the filling completion time Tf. It is not particularly limited to this. For example, as shown in FIG. 7, the control unit 3 of the hydraulic control device can adjust the filling completion time Tf by controlling the second opening degree.
　まず、制御部３は、上記実施形態と同様に、ステップＳ１からステップＳ５までの処理を実行する。ここで、上記実施形態では、ステップＳ５における第２開度は一定の固定値であったが、変形例１では、ステップＳ５における第２開度は可変であって、制御部３が第２開度を設定する。なお、第２開度を設定する際の制御部３の動作は後述する。 First, the control unit 3 executes the processing from step S1 to step S5 as in the above embodiment. Here, in the above-described embodiment, the second opening degree in step S5 is a constant fixed value. However, in the first modification, the second opening degree in step S5 is variable and the control unit 3 opens the second opening. Set the degree. In addition, operation | movement of the control part 3 at the time of setting a 2nd opening degree is mentioned later.
　次に、制御部３は、上記実施形態と同様に、ステップＳ７からステップＳ９までの処理を実行する。なお、変形例１では、制御部３は、上記実施形態のステップＳ６の処理を実行しない。すなわち、制御部３は、図８に示すように、第２時点ｔ２から第３時点ｔ３まで、第２開度を維持する。よって、制御部３は、第２時点ｔ２から第３時点ｔ３まで、比例ソレノイド５２に出力する指令電流を第２電流値Ｉ２のままとする。 Next, the control unit 3 executes the processing from step S7 to step S9 as in the above embodiment. In the first modification, the control unit 3 does not execute the process in step S6 of the above embodiment. That is, as shown in FIG. 8, the control unit 3 maintains the second opening degree from the second time point t2 to the third time point t3. Therefore, the control unit 3 keeps the command current output to the proportional solenoid 52 from the second time point t2 to the third time point t3 as the second current value I2.
　次に、第２開度を設定する際の制御部３の動作について、図９を参照しつつ説明する。図９は、第２開度を設定する際の制御部３の動作を説明するフローチャートである。 Next, the operation of the control unit 3 when setting the second opening will be described with reference to FIG. FIG. 9 is a flowchart for explaining the operation of the control unit 3 when setting the second opening.
　図９に示すように、制御部３は、上記実施形態と同様に、ステップＳ６１及びＳ６２の処理を実行する。 As shown in FIG. 9, the control unit 3 executes the processes of steps S61 and S62 as in the above embodiment.
　制御部３は、参考充填完了時間が予め設定された範囲内であると判定すると（ステップＳ６２のＹｅｓ）、前回の変速処理の際と同じ第２開度を設定する（ステップＳ５３）。すなわち、制御部３は、前回の変速処理から第２開度を変更しない。 When the control unit 3 determines that the reference filling completion time is within the preset range (Yes in step S62), the control unit 3 sets the same second opening as that in the previous shift process (step S53). That is, the control unit 3 does not change the second opening degree from the previous shift process.
　一方、制御部３は、参考充填完了時間が予め設定された範囲から外れていると判定すると（ステップＳ６２のＮｏ）、対象の変速処理における第２開度を変更する（ステップＳ５４）。具体的には、制御部３は、予め設定された範囲の最大値よりも参考充填完了時間の方が長いと判定すると、対象の変速処理における第２開度を、前回の第２開度よりも大きくする。また、制御部３は、予め設定された範囲の最小値よりも参考充填完了時間の方が短いと判定すると、対象の変速処理における第２開度を、前回の変速処理の第２開度よりも小さくする。 On the other hand, when the control unit 3 determines that the reference filling completion time is out of the preset range (No in step S62), the control unit 3 changes the second opening degree in the target shift process (step S54). Specifically, when the control unit 3 determines that the reference filling completion time is longer than the maximum value in a preset range, the control unit 3 sets the second opening in the target shift process to the previous second opening. Also make it bigger. If the control unit 3 determines that the reference filling completion time is shorter than the minimum value in the preset range, the control unit 3 sets the second opening in the target shift process to the second opening in the previous shift process. Also make it smaller.
　変形例２
　トリガ時間Ｔｔは、予め設定された固定値であってもよいし、可変であってもよい。すなわち、制御部３は、参考充填完了時間に基づき、トリガ時間Ｔｔを制御してもよい。この場合、制御部３は、トリガ時間Ｔｔの制御よりも、第２時点から第３時点までの開度の増加率の制御を優先的に実行することが好ましい。 Modification 2
The trigger time Tt may be a fixed value set in advance or may be variable. That is, the control unit 3 may control the trigger time Tt based on the reference filling completion time. In this case, it is preferable that the control unit 3 preferentially executes the control of the increase rate of the opening from the second time point to the third time point, rather than the control of the trigger time Tt.
　変形例３
　上記実施形態では、クラッチの制御に対して本発明が適用されているが、本発明は油圧式ブレーキの制御にも適用可能である。本発明を油圧式ブレーキの制御に適用した場合、上述した変速処理は制動処理に置き換わる。 Modification 3
In the above embodiment, the present invention is applied to the control of the clutch, but the present invention is also applicable to the control of the hydraulic brake. When the present invention is applied to control of a hydraulic brake, the above-described shift process is replaced with a brake process.
　図１１に示すように、油圧式ブレーキ７３は、第１プレート７３１、第２プレート７３２、ピストン７３４、及び油室７３５を有している。第１プレート７３１及び第２プレート７３２は、軸方向（図１１の左右方向）に移動可能である。油室７３４に作動油が供給されるとピストン７３３が移動し、この結果、第１プレート７３１と第２プレート７３２とが連結して動力が伝達される。なお、第１プレート７３１及び第２プレート７３２は複数設けられていて多板ブレーキを構成している。 As shown in FIG. 11, the hydraulic brake 73 includes a first plate 731, a second plate 732, a piston 734, and an oil chamber 735. The first plate 731 and the second plate 732 are movable in the axial direction (left-right direction in FIG. 11). When hydraulic oil is supplied to the oil chamber 734, the piston 733 moves, and as a result, the first plate 731 and the second plate 732 are connected to transmit power. A plurality of first plates 731 and second plates 732 are provided to constitute a multi-plate brake.
　３　　制御部
　１５　　圧力制御弁
　１６　　充填完了検出部 3 Control unit 15 Pressure control valve 16 Filling completion detection unit

Claims (12)

  1. 　油圧機器を制御する装置であって、
    　前記油圧機器に供給される作動油の油圧を制御する圧力制御弁と、
    　前記油圧機器への作動油の充填完了を検出する充填完了検出部と、
    　前記圧力制御弁の開度を制御する制御部と、
    を備え、
    　前記制御部は、前記油圧機器へ作動油を供給開始する第１時点から第２時点までの間、前記開度を第１開度に変更し、前記第２時点において、前記開度を前記第１開度から前記第１開度よりも小さい第２開度とし、前記第２時点から前記充填完了検出部によって前記作動油の充填完了が検出される第３時点までの間、前記開度を前記第２開度から増加させ、
    　前記制御部は、対象の処理よりも前に行われた処理における前記第１時点から前記第３時点までの時間である参考充填完了時間に基づき、前記第２時点から前記第３時点までにおける前記開度の増加率を設定し、
    　前記油圧機器は、油圧式クラッチ又は油圧式ブレーキであり、
    　前記油圧機器が油圧式クラッチの場合における前記処理は変速処理であり、前記油圧機器が油圧式ブレーキの場合における前記処理は制動処理である、
    油圧制御装置。     A device for controlling hydraulic equipment,
    A pressure control valve for controlling the hydraulic pressure of hydraulic oil supplied to the hydraulic equipment;
    A filling completion detector for detecting completion of filling of hydraulic oil into the hydraulic device;
    A control unit for controlling the opening of the pressure control valve;
    With
    The controller changes the opening to a first opening during a period from a first time point at which supply of hydraulic oil to the hydraulic equipment is started to a second time point, and the opening degree is changed to the first opening point at the second time point. The first opening is set to a second opening smaller than the first opening, and the opening is set between the second time point and the third time point when the filling completion detection unit detects completion of filling of the hydraulic oil. Increasing from the second opening,
    The control unit, based on a reference filling completion time that is a time from the first time point to the third time point in the process performed before the target process, the time from the second time point to the third time point Set the rate of increase of opening,
    The hydraulic device is a hydraulic clutch or a hydraulic brake,
    When the hydraulic device is a hydraulic clutch, the process is a shift process, and when the hydraulic device is a hydraulic brake, the process is a braking process.
    Hydraulic control device.
  2. 　前記圧力制御弁の開度を制御する電磁制御弁をさらに備え、
    　前記制御部は、前記電磁制御弁に出力する電流値を制御することによって、前記圧力制御弁の前記開度を制御する、
    請求項１に記載の油圧制御装置。     An electromagnetic control valve for controlling the opening of the pressure control valve;
    The control unit controls the opening degree of the pressure control valve by controlling a current value output to the electromagnetic control valve.
    The hydraulic control device according to claim 1.
  3. 　前記制御部は、予め設定された最大値よりも前記参考充填完了時間が長い場合、前記対象の処理における前記増加率を、前記対象の処理より１つ前の処理における前記増加率よりも高くする、
    請求項１又は２に記載の油圧制御装置。     When the reference filling completion time is longer than a preset maximum value, the control unit increases the increase rate in the target process higher than the increase rate in the process immediately before the target process. ,
    The hydraulic control device according to claim 1 or 2.
  4. 　前記制御部は、予め設定された最小値よりも前記参考充填完了時間が短い場合、前記対象の処理における前記増加率を、前記対象の処理より１つ前の処理における前記増加率よりも低くする、
    請求項１から３のいずれかに記載の油圧制御装置。     When the reference filling completion time is shorter than a preset minimum value, the control unit lowers the increase rate in the target process lower than the increase rate in the process immediately before the target process. ,
    The hydraulic control device according to claim 1.
  5. 　前記制御部は、前記対象の処理よりも前に行われた複数回分の処理における充填完了時間の平均値を前記参考充填完了時間として、前記増加率を設定する、
    請求項１から４のいずれかに記載の油圧制御装置。     The control unit sets the increase rate using the reference filling completion time as an average value of the filling completion time in a plurality of processes performed before the target process,
    The hydraulic control device according to claim 1.
  6. 　前記油圧機器は、油圧式クラッチであって、
    　前記油圧式クラッチは、
    　　第１プレートと、
    　　第２プレートと、
    　　前記第１プレートを前記第２プレートに向かって押圧するように構成されたピストンと、
    　　前記ピストンの押圧力を発生させる油室と、
    を備え、
    　前記圧力制御弁は、前記油室に供給される作動油の油圧を制御する、
    請求項１から５のいずれかに記載の油圧制御装置。     The hydraulic device is a hydraulic clutch,
    The hydraulic clutch is
    A first plate;
    A second plate;
    A piston configured to press the first plate toward the second plate;
    An oil chamber for generating a pressing force of the piston;
    With
    The pressure control valve controls a hydraulic pressure of hydraulic oil supplied to the oil chamber;
    The hydraulic control apparatus according to claim 1.
  7. 　油圧機器を制御する装置であって、
    　前記油圧機器に供給される作動油の油圧を制御する圧力制御弁と、
    　前記油圧機器への作動油の充填完了を検出する充填完了検出部と、
    　前記圧力制御弁の開度を制御する制御部と、
    を備え、
    　前記制御部は、前記油圧機器へ作動油を供給開始する第１時点から第２時点までの間、前記開度を第１開度とし、前記第２時点から前記充填完了検出部によって前記作動油の充填完了が検出される第３時点までの間、前記開度を前記第１開度よりも小さい第２開度とし、
    　前記制御部は、対象の処理よりも前に行われた処理における前記第１時点から前記第３時点までの時間である参考充填完了時間に基づき、前記第２開度を設定し、
    　前記油圧機器は、油圧式クラッチ又は油圧式ブレーキであり、
    　前記油圧機器が油圧式クラッチの場合における前記処理は変速処理であり、前記油圧機器が油圧式ブレーキの場合における前記処理は制動処理である、
    油圧制御装置。     A device for controlling hydraulic equipment,
    A pressure control valve for controlling the hydraulic pressure of hydraulic oil supplied to the hydraulic equipment;
    A filling completion detector for detecting completion of filling of hydraulic oil into the hydraulic device;
    A control unit for controlling the opening of the pressure control valve;
    With
    The control unit sets the opening degree to a first opening degree from a first time point to a second time point at which supply of hydraulic oil to the hydraulic equipment is started, and the hydraulic oil is detected by the filling completion detection unit from the second time point. Until the third time point when the completion of filling is detected, the opening is a second opening smaller than the first opening,
    The control unit sets the second opening based on a reference filling completion time which is a time from the first time point to the third time point in the process performed before the target process,
    The hydraulic device is a hydraulic clutch or a hydraulic brake,
    When the hydraulic device is a hydraulic clutch, the process is a shift process, and when the hydraulic device is a hydraulic brake, the process is a braking process.
    Hydraulic control device.
  8. 　前記圧力制御弁の開度を制御する電磁制御弁をさらに備え、
    　前記制御部は、前記電磁制御弁に出力する電流値を制御することによって、前記圧力制御弁の前記開度を制御する、
    請求項７に記載の油圧制御装置。     An electromagnetic control valve for controlling the opening of the pressure control valve;
    The control unit controls the opening degree of the pressure control valve by controlling a current value output to the electromagnetic control valve.
    The hydraulic control apparatus according to claim 7.
  9. 　前記制御部は、予め設定された最大値よりも前記参考充填完了時間が長い場合、前記対象の処理における前記第２開度を、前記対象の処理より１つ前の処理における前記第２開度よりも大きくする、
    請求項７又は８に記載の油圧制御装置。     When the reference filling completion time is longer than a preset maximum value, the control unit sets the second opening in the target process to the second opening in the process immediately before the target process. Bigger than
    The hydraulic control device according to claim 7 or 8.
  10. 　前記制御部は、予め設定された最小値よりも前記参考充填完了時間が短い場合、前記対象の処理における前記第２開度を、前記対象の処理より１つ前の処理における前記第２開度よりも小さくする、
    請求項７から９のいずれかに記載の油圧制御装置。     When the reference filling completion time is shorter than a preset minimum value, the control unit sets the second opening in the target process to the second opening in the process immediately before the target process. Smaller than,
    The hydraulic control device according to claim 7.
  11. 　前記制御部は、前記対象の処理よりも前に行われた複数回分の処理における充填完了時間の平均値を前記参考充填完了時間として、前記第２開度を設定する、
    請求項７から１０のいずれかに記載の油圧制御装置。     The control unit sets the second opening as the reference filling completion time as an average value of filling completion times in a plurality of processes performed before the target process.
    The hydraulic control device according to claim 7.
  12. 　前記油圧機器は、油圧式クラッチであって、
    　前記油圧式クラッチは、
    　　第１プレートと、
    　　第２プレートと、
    　　前記第１プレートを前記第２プレートに向かって押圧するように構成されたピストンと、
    　　前記ピストンの押圧力を発生させる油室と、
    を備え、
    　前記圧力制御弁は、前記油室に供給される作動油の油圧を制御する、
    請求項７から１１のいずれかに記載の油圧制御装置。
          The hydraulic device is a hydraulic clutch,
    The hydraulic clutch is
    A first plate;
    A second plate;
    A piston configured to press the first plate toward the second plate;
    An oil chamber for generating a pressing force of the piston;
    With
    The pressure control valve controls a hydraulic pressure of hydraulic oil supplied to the oil chamber;
    The hydraulic control device according to claim 7.
PCT/JP2014/057292 2014-03-18 2014-03-18 Hydraulic control apparatus WO2015140919A1 (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63251653A (en) * 1987-04-06 1988-10-19 Komatsu Ltd Method of controlling clutch pressure of speed change gear
JPH1089455A (en) * 1996-09-19 1998-04-07 Aisin Aw Co Ltd Hydraulic control device of automatic transmission
JP2007263338A (en) * 2006-03-30 2007-10-11 Jatco Ltd Control device of automatic transmission
JP2008106871A (en) * 2006-10-26 2008-05-08 Toyota Motor Corp Control device for vehicular automatic transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63251653A (en) * 1987-04-06 1988-10-19 Komatsu Ltd Method of controlling clutch pressure of speed change gear
JPH1089455A (en) * 1996-09-19 1998-04-07 Aisin Aw Co Ltd Hydraulic control device of automatic transmission
JP2007263338A (en) * 2006-03-30 2007-10-11 Jatco Ltd Control device of automatic transmission
JP2008106871A (en) * 2006-10-26 2008-05-08 Toyota Motor Corp Control device for vehicular automatic transmission

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