WO2017033888A1 - In-vehicle hydraulic supply device - Google Patents
In-vehicle hydraulic supply device Download PDFInfo
- Publication number
- WO2017033888A1 WO2017033888A1 PCT/JP2016/074381 JP2016074381W WO2017033888A1 WO 2017033888 A1 WO2017033888 A1 WO 2017033888A1 JP 2016074381 W JP2016074381 W JP 2016074381W WO 2017033888 A1 WO2017033888 A1 WO 2017033888A1
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- WIPO (PCT)
- Prior art keywords
- oil
- pulley
- hydraulic
- hydraulic pressure
- check valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/68—Inputs being a function of gearing status
- F16H59/70—Inputs being a function of gearing status dependent on the ratio established
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
Definitions
- the present invention relates to an in-vehicle hydraulic pressure supply device.
- pressure oil is supplied between a first pump that supplies pressure oil to an oil passage between a primary pulley and a secondary pulley, and a hydraulic chamber of the primary pulley and a hydraulic chamber of the secondary pulley.
- An in-vehicle hydraulic pressure supply device is proposed that includes a second pump that supplies and discharges the air.
- the present invention has been made in view of the above points, and an object thereof is to provide an in-vehicle hydraulic pressure supply device capable of reducing consumed energy by suppressing wasteful energy consumption. .
- One aspect of the in-vehicle hydraulic pressure supply device of the present invention is to control the pulley width of each of the primary pulley and the secondary pulley whose pulley width is variable by hydraulic oil to which hydraulic pressure supplied from a hydraulic pressure generation source is attached,
- a check valve provided between the main pulley and hydraulic oil supplied from the main pump via the check valve to the hydraulic oil in one of the primary pulley and the secondary pulley.
- An auxiliary pump that moves from one to the other, a pulley width detector that detects the pulley width state, a shift command that is input, and the pulley width state that the pulley width detector detects Based on any one of a positive direction in which the hydraulic oil is moved from the primary pulley to the secondary pulley, and a negative direction in which the hydraulic oil is moved from the secondary pulley to the primary pulley;
- a control unit that determines a moving speed in the positive direction or the negative direction, and drives and controls the auxiliary pump according to the determined moving direction and the moving speed.
- an in-vehicle hydraulic pressure supply device that can reduce consumed energy is provided.
- FIG. 1 is a block diagram illustrating an example of the configuration of the in-vehicle hydraulic pressure supply device 1 according to the first embodiment.
- the in-vehicle hydraulic pressure supply device 1 supplies hydraulic pressure to the continuously variable transmission 3 of the vehicle based on a shift command from the host unit 2.
- the continuously variable transmission 3 includes a primary pulley PP, a secondary pulley SP, and a belt VT.
- a rotational force output from a prime mover (not shown) is transmitted to the primary pulley PP.
- the belt VT is wound between the primary pulley PP and the secondary pulley SP, and transmits the rotational force transmitted to the primary pulley PP to the secondary pulley SP.
- the secondary pulley SP transmits the rotational force transmitted from the belt VT to a vehicle wheel (not shown) via a rotational force transmission mechanism (not shown).
- Both the primary pulley PP and the secondary pulley SP have a variable pulley width.
- the primary pulley PP includes a fixed primary pulley PP1 and a movable primary pulley PP2.
- the movable primary pulley PP2 moves in the direction of the rotation axis of the pulley, that is, in the direction of the arrow AX1 in the drawing, the pulley width of the primary pulley PP changes.
- the secondary pulley SP includes a fixed secondary pulley SP1 and a movable secondary pulley SP2.
- the pulley width of the secondary pulley SP changes.
- the surface on which the belt VT of these pulleys is wound is conical. In the state where the pulley width is wide, the belt VT contacts the inner peripheral portion of the pulley. In the state where the pulley width is narrow, the belt VT contacts the outer peripheral portion of the pulley.
- the reduction gear ratio is changed by changing the pulley width of the primary pulley PP and the pulley width of the secondary pulley SP.
- the reduction ratio is increased. Conversely, if the pulley width of the primary pulley PP is narrowed and the pulley width of the secondary pulley SP is widened, the reduction gear ratio becomes small.
- Each of the movable primary pulley PP2 and the movable secondary pulley SP2 includes an oil chamber (not shown).
- the position of the movable pulley in the rotational axis direction of the pulley is determined by the amount of hydraulic oil present in the oil chamber.
- These movable pulleys move in the direction in which the pulley width increases as the amount of hydraulic oil present in the oil chamber increases, and move in the direction in which the pulley width decreases as the amount of hydraulic oil decreases.
- these movable pulleys move in a direction in which the pulley width decreases as the amount of hydraulic oil present in the oil chamber increases, and move in a direction in which the pulley width increases as the amount of hydraulic oil decreases. Also good.
- supplying hydraulic oil to the oil chamber of the movable primary pulley PP2 is simply described as supplying hydraulic oil to the primary pulley PP.
- supplying hydraulic fluid to the oil chamber of the movable secondary pulley SP2 is simply described as supplying hydraulic fluid to the secondary pulley SP.
- the primary pulley PP and the secondary pulley SP are applied with a force acting from the belt VT to increase the pulley width by the tension of the belt VT.
- the primary pulley PP and the secondary pulley SP are supplied with hydraulic oil pressurized to a predetermined pressure in order to resist this force.
- this predetermined pressure is also referred to as a source pressure.
- the setting range of the source pressure is about 4 to 5 [Mpa] in the example of the present embodiment. That is, hydraulic oil pressurized to about 4 to 5 [Mpa] is supplied to the primary pulley PP and the secondary pulley SP.
- the in-vehicle hydraulic pressure supply device 1 includes an oil closing path 10, a pulley width detection unit 20, a control unit 30, and a hydraulic pressure supply unit 40.
- the pulley width detector 20 detects the pulley width state of the primary pulley PP or the secondary pulley SP.
- the state of the pulley width refers to the position of the movable pulley in the rotation axis direction, the interval between the fixed pulley and the movable pulley, and the like.
- the pulley width detection unit 20 may detect the pulley width state for both the primary pulley PP and the secondary pulley SP, or may detect the pulley width state for either one of the pulleys.
- the pulley width detection unit 20 includes a position detection sensor 201.
- the position detection sensor 201 is disposed in the vicinity of the primary pulley PP or the secondary pulley SP, and detects the position in the width direction of the movable pulley by measurement using magnetism or an optical system.
- the pulley width detector 20 outputs the detected pulley width state to the control unit 30.
- the oil closing path 10 is provided between the primary pulley PP and the secondary pulley SP, and moves the hydraulic oil between the primary pulley PP and the secondary pulley SP.
- the closed oil passage 10 is not provided with a mechanism for draining oil when the internal hydraulic oil exceeds a predetermined pressure. Therefore, the amount of hydraulic oil in the closed oil passage 10 does not change except when it leaks from the joints of the oil passages, valve gaps, and the like.
- the oil closing path 10 is provided with an auxiliary pump P2, a hydraulic pressure sensor PS2, and a bidirectional check valve V2.
- the oil closing path 10 between the primary pulley PP and the bidirectional check valve V2 is referred to as an oil closing path 101.
- the oil closing passage 10 between the bidirectional check valve V2 and the auxiliary pump P2 is referred to as an oil closing passage 102.
- the closed oil passage 10 between the auxiliary pump P2 and the hydraulic pressure sensor PS2 is referred to as an oil closed passage 103.
- the closed oil passage 10 between the hydraulic sensor PS2 and the secondary pulley SP is referred to as an oil closed passage 104.
- the oil closed path 10 includes an oil closed path 101, an oil closed path 102, an oil closed path 103, and an oil closed path 104, which are connected in the order of description.
- the order of arrangement of the auxiliary pump P2, the hydraulic pressure sensor PS2, and the bidirectional check valve V2 between the primary pulley PP and the secondary pulley SP is an example, and is not limited to the illustrated one.
- the auxiliary pump P2 moves the hydraulic oil inside the oil closed path 10 between the primary pulley PP and the secondary pulley SP.
- the auxiliary pump P2 can rotate forward and backward.
- the auxiliary pump P2 rotates forward to move the hydraulic oil from the primary pulley PP to the secondary pulley SP, that is, in the direction of arrow A in the figure.
- this arrow A direction is also referred to as a positive direction.
- the auxiliary pump P2 rotates in the reverse direction to move the hydraulic oil from the secondary pulley SP to the primary pulley PP, that is, in the direction of arrow B in the drawing.
- this arrow B direction is also referred to as a negative direction.
- the auxiliary pump P2 changes the moving direction of the hydraulic oil by changing the rotation direction.
- the auxiliary pump P2 is an electric pump
- the auxiliary pump P2 operates based on control by the control unit 30.
- the case where the auxiliary pump P2 changes the rotation direction to change the moving direction of the hydraulic oil will be described, but is not limited thereto.
- a configuration may be adopted in which two auxiliary pumps whose hydraulic oil discharge directions are opposite to each other are combined to operate one of the auxiliary pumps to change the moving direction of the hydraulic oil.
- the hydraulic pressure sensor PS2 detects the pressure of the hydraulic oil inside the closed oil passage 10.
- the hydraulic sensor PS2 outputs the detected pressure to the control unit 30.
- the bidirectional check valve V2 includes a positive check valve V21 and a negative check valve V22.
- the forward check valve V21 allows hydraulic oil to pass in the direction of arrow A1 in the drawing, that is, in the positive direction, and does not pass in the direction of arrow B1 in the drawing, that is, in the negative direction.
- the negative direction check valve V22 allows hydraulic oil to pass in the direction of arrow B2 in the drawing, that is, in the negative direction, and not in the direction of arrow A2 in the drawing, that is, in the positive direction.
- These positive direction check valve V21 and negative direction check valve V22 are arranged in parallel with respect to the moving direction of the hydraulic oil.
- the bidirectional check valve V2 may have a hydraulic range in which neither the positive direction check valve V21 nor the negative direction check valve V22 is opened.
- FIG. 2 is a graph showing an example of the valve opening hydraulic pressure threshold value of the bidirectional check valve V2 of the present embodiment.
- the forward check valve V21 opens when the hydraulic oil pressure in the closed oil passage 101 is greater than the hydraulic oil pressure in the closed oil passage 102.
- the forward check valve V21 is such that the difference between the oil pressure of the oil closing passage 101 and the oil pressure of the oil closing passage 102 is such that the threshold value Th1 is set in the positive direction. If exceeded, the valve is opened.
- the negative check valve V22 opens when the hydraulic oil pressure in the closed oil passage 102 is greater than the hydraulic oil pressure in the closed oil passage 101.
- the negative check valve V22 is configured such that the difference between the oil pressure of the oil closing passage 101 and the oil pressure of the oil closing passage 102 causes the threshold Th2 to be negative. If exceeded, the valve is opened.
- the threshold value Th1 is away in the positive direction and the threshold value Th2 is away in the negative direction from the reference position where the differential pressure is 0 (zero)
- the forward direction check valve A hydraulic pressure range is generated in which neither V21 nor the negative check valve V22 is opened.
- the hydraulic pressure of the closed oil passage 101 is higher than the hydraulic pressure of the closed oil passage 102.
- the threshold value Th1 at which the forward check valve V21 opens is 0 (zero)
- the valve is immediately opened when the oil pressure in the oil closing passage 101 increases with respect to the oil pressure in the oil closing passage 102.
- the hydraulic pressure of the closed oil passage 102 is higher than the hydraulic pressure of the closed oil passage 101.
- the valve when the threshold value Th2 for opening the negative check valve V22 is 0 (zero), the valve is immediately opened when the oil pressure in the oil closing passage 102 is increased with respect to the oil pressure in the oil closing passage 101. . That is, when both the threshold value Th1 and the threshold value Th2 are 0 (zero), the bidirectional check valve V2 does not inhibit the movement of the hydraulic oil. In this case, for example, the movement of the hydraulic oil between the primary pulley PP and the secondary pulley SP can be suppressed by rotating the auxiliary pump P2 in the direction opposite to the moving direction of the hydraulic oil. However, if the auxiliary pump P2 is operated in order to suppress the movement of the hydraulic oil, consumption of energy for driving the auxiliary pump P2 occurs.
- the positive direction check valve V21 and the negative direction check valve V22 have a hydraulic pressure range in which neither of them opens, the movement of the hydraulic oil can be suppressed by the bidirectional check valve V2. Therefore, when the positive direction check valve V21 and the negative direction check valve V22 have a hydraulic pressure range in which neither of them opens, it is possible to reduce energy consumption for suppressing the movement of the hydraulic oil. Further, even when force is applied from the belt VT to the primary pulley PP and the secondary pulley SP, the threshold values are set so that neither the positive check valve V21 nor the negative check valve V22 is opened. If set, the above-described energy consumption can be further suppressed.
- the bidirectional check valve V2 is not essential in the in-vehicle hydraulic pressure supply device 1.
- the in-vehicle hydraulic pressure supply device 1 may not include the bidirectional check valve V2.
- the hydraulic pressure supply unit 40 includes an oil pan OP, a main pump P1, a hydraulic pressure sensor PS1, a check valve V1, and a check valve V3, and closes hydraulic oil pressurized by the main pump P1.
- the main pump P ⁇ b> 1 is provided between the oil passage 501 and the oil passage 601, sucks up the hydraulic oil stored in the oil pan OP through the oil passage 501, and discharges it to the oil passage 601. That is, the main pump P1 moves the hydraulic oil in the direction of arrow C in the drawing.
- the main pump P1 is an electric pump will be described, but the present invention is not limited to this.
- the main pump P1 operates based on control by the control unit 30.
- the check valve V3 is provided between the oil passage 601 and the oil passage 602, and allows hydraulic oil to pass in the direction of arrow C in the drawing and not in the direction of arrow D in the drawing.
- the check valve V3 maintains the hydraulic pressure of the hydraulic oil inside the oil passage 602 even when the main pump P1 is stopped.
- the oil pressure sensor PS1 is provided between the oil passage 602 and the oil passage 603, and detects the hydraulic pressure of the hydraulic oil inside the oil passage 602. The hydraulic sensor PS1 outputs the detected pressure to the control unit 30.
- the check valve V ⁇ b> 1 is provided between the oil passage 603 and the oil closing passage 10.
- the check valve V1 includes a check valve V11 and a check valve V12.
- the check valve V11 is also referred to as a first check valve.
- the check valve V12 is also referred to as a second check valve.
- the check valve V11 is provided between the oil passage 603 and the closed oil passage 101, and allows hydraulic oil to pass in the direction of arrow C1 in the drawing and not in the direction of arrow D1 in the drawing.
- the check valve V12 is provided between the oil passage 603 and the oil closing passage 103, and allows hydraulic oil to pass in the direction of arrow C2 in the drawing and not in the direction of arrow D2 in the drawing.
- the check valve V ⁇ b> 11 may be provided between the oil passage 603 and the oil closing passage 102. Further, the check valve V12 may be provided between the oil passage 603 and the oil closing passage 104.
- the check valve V1 supplies the hydraulic oil pressurized by the main pump P1 to the closed oil passage 10 and suppresses the hydraulic oil from flowing from the closed oil passage 10 to the oil passage 603 side. By this check valve V1, the hydraulic pressure of the hydraulic oil inside the closed oil passage 10 is maintained at a predetermined value or more.
- the hydraulic pressure supply unit 40 may include an accumulator ACC.
- the accumulator ACC stores hydraulic oil to which hydraulic pressure generated by the main pump P1 is attached. By providing the accumulator ACC, the hydraulic pressure supply unit 40 can reduce hydraulic pulsation and surge due to the operation of the main pump P1. Further, the hydraulic pressure supply unit 40 includes the accumulator ACC, and can apply pressure to the hydraulic oil in a state where the main pump P1 is stopped.
- the hydraulic pressure supply unit 40 may include a check valve V4.
- This check valve V4 discharges part of the hydraulic oil inside the oil passage 603 to the oil pan OP via the oil passage 502 when the oil pressure inside the oil passage 603 exceeds the relief pressure. That is, the check valve V4 may function as a relief valve.
- the hydraulic pressure supply unit 40 can drain the hydraulic oil and reduce the hydraulic pressure when the hydraulic pressure inside the oil passage 603 rises abnormally.
- This relief valve opens when the hydraulic pressure of the hydraulic oil inside the oil passage 603 is sufficiently higher than the set range of the original pressure. In other words, the relief valve does not open in the set range of the original pressure. That is, this relief valve opens when the hydraulic pressure of the hydraulic oil inside the oil passage 603 rises abnormally.
- the check valve V4 may function as a pressure control valve for adjusting the hydraulic pressure of the hydraulic oil supplied to the closed oil passage 10 within the original pressure setting range.
- the hydraulic pressure supply unit 40 adjusts the hydraulic pressure of the hydraulic oil supplied to the closed oil passage 10 within the set range of the original pressure without precisely controlling the hydraulic pressure by the main pump P1. can do.
- FIG. 3 is a block diagram illustrating an example of a functional configuration of the control unit 30 of the present embodiment.
- the control unit 30 includes a control unit 301, a main pump drive circuit 302, and an auxiliary pump drive circuit 303.
- the input side of the control unit 30 is connected to the host unit 2, the hydraulic sensor PS1, the position detection sensor 201, and the hydraulic sensor PS2.
- the output side of the control unit 30 is connected to the main pump P1 and the auxiliary pump P2.
- the control unit 30 acquires a shift command for the continuously variable transmission 3 from the host unit 2.
- This shift command includes a target value for the gear ratio and a target value for the time required for the shift.
- “Target speed ratio value” is also referred to as “target speed ratio”.
- the “target value of time required for shifting” is also referred to as “target shifting time”.
- the control unit 30 acquires information indicating the hydraulic pressure of the hydraulic oil inside the oil passage 602 detected by the hydraulic sensor PS1 from the hydraulic sensor PS1.
- “Hydraulic pressure detected by the hydraulic pressure sensor PS1” is also referred to as “original pressure actual measurement value”.
- “Information indicating actual measured actual pressure” is also referred to as “original pressure information”.
- control unit 30 acquires information indicating the position in the width direction of the movable pulley detected by the position detection sensor 201 from the position detection sensor 201. “Information indicating the position in the width direction of the movable pulley output from the position detection sensor 201” is also simply referred to as “position information”. Further, the control unit 30 acquires information indicating the hydraulic pressure of the hydraulic oil inside the closed oil passage 10 detected by the hydraulic sensor PS2 from the hydraulic sensor PS2. The “hydraulic pressure detected by the hydraulic pressure sensor PS2” is also referred to as “actually measured oil pressure on the closed path”. “Information indicating the actual oil pressure value of the closed oil path output from the oil pressure sensor PS2” is also referred to as “oil pressure information of the oil path”.
- the control unit 301 includes a CPU (Central Processing Unit), and includes a main pump control unit 311, an auxiliary pump control unit 312, and a failure detection unit 313 as functional units.
- CPU Central Processing Unit
- the main pump control unit 311 controls the main pump P1 based on the shift command acquired from the host unit 2 and the original pressure information acquired from the hydraulic sensor PS1. With reference to FIG. 4, the control of the main pump P1 by the control unit 301 will be described.
- FIG. 4 is a flowchart showing an example of a control flow of the main pump P1 of the present embodiment.
- the main pump control unit 311 determines whether or not there is a shift command from the host unit 2 (step S10). If it is determined that there is a shift command (step S10; YES), the process proceeds to step S20. If it is determined that there is no shift command (step S10; NO), the main pump control unit 311 returns the process to step S10 and waits for the shift command.
- the main pump control unit 311 calculates the target pressure of the hydraulic oil inside the oil passage 602 (step S20).
- the target pressure of hydraulic oil inside the oil passage 602 is also referred to as a source pressure target value.
- the original pressure target value is determined in advance by a target speed ratio, a target speed change time, etc. included in the speed change command. For example, when the difference between the current speed change ratio and the target speed change ratio is relatively large, or when the target speed change time is relatively short, the original pressure target value is set higher. That is, when the pulley width is changed greatly or when the pulley width is changed quickly, the original pressure target value is set to be high.
- the main pump control unit 311 calculates the source pressure target value based on the predetermined source pressure target value condition and the target gear ratio and target shift time included in the shift command.
- the main pump control unit 311 acquires the original pressure information from the hydraulic pressure sensor PS1 (step S30).
- This source pressure information indicates the actual measured actual pressure value detected by the hydraulic sensor PS1.
- the main pump control unit 311 compares the original pressure target value calculated in Step S20 with the actual measured actual pressure indicated by the original pressure information acquired in Step S30 (Step S40). If the main pump control unit 311 determines that the actual measured pressure value has not reached the target target pressure value (step S40; NO), the main pump P1 is driven (step S50), and the process proceeds to step S30. return. When the main pump control unit 311 determines that the actual measured actual pressure value has reached the original target pressure value (step S40; YES), the main pump control unit 311 stops the main pump P1 (step S60).
- the main pump control unit 311 outputs a drive signal sig1 of the main pump P1 to the main pump drive circuit 302.
- the main pump drive circuit 302 includes a current output circuit such as an inverter, and outputs a drive current I1 to the main pump P1 based on the drive signal sig1.
- the main pump P1 discharges hydraulic oil in the direction of arrow C shown in FIG. Further, the main pump P1 stops discharging the hydraulic oil when the supply of the drive current I1 is stopped.
- the main pump control unit 311 may perform drive control of the main pump P1 based on the original pressure information acquired from the hydraulic sensor PS1 without waiting for a shift command output from the host unit 2. That is, step S10 described above may be omitted.
- the auxiliary pump control unit 312 performs drive control of the auxiliary pump P2 based on the shift command and the position information. The control of the auxiliary pump P2 by the auxiliary pump control unit 312 will be described with reference to FIG.
- FIG. 5 is a flowchart showing an example of a control flow of the auxiliary pump P2 of the present embodiment.
- the auxiliary pump control unit 312 determines whether or not there is a shift command from the host unit 2 (step S100). If it is determined that there is a shift command (step S100; YES), the process proceeds to step S110. If the auxiliary pump control unit 312 determines that there is no shift command (step S100; NO), the process returns to step S100 and waits for a shift command.
- the auxiliary pump control unit 312 acquires position information from the position detection sensor 201 (step S110).
- the position detection sensor 201 is described as detecting the pulley width of the secondary pulley SP and outputting position information indicating the pulley width of the secondary pulley SP.
- the position information output by the position detection sensor 201 is also referred to as “current width of secondary pulley SP” or simply “current width”. That is, in step S110, the auxiliary pump control unit 312 acquires the current width of the secondary pulley SP from the position detection sensor 201.
- the auxiliary pump control unit 312 calculates the target width of the secondary pulley SP based on the target speed ratio included in the speed change command acquired in Step S100 (Step S120).
- the auxiliary pump control unit 312 calculates the change width of the secondary pulley SP based on the current width of the secondary pulley SP acquired in step S110 and the target width calculated in step S120. Further, the auxiliary pump control unit 312 calculates the rotation direction and the rotation speed of the auxiliary pump P2 based on the calculated change width of the secondary pulley SP and the target shift time included in the shift command acquired in step S100. (Step S130).
- the pulley width is widened or narrowed depends on the moving direction of the hydraulic oil inside the closed oil passage 10. That is, the direction of change of the pulley width is determined by the rotation direction of the auxiliary pump P2.
- the auxiliary pump control unit 312 determines the rotation direction of the auxiliary pump P2 in the direction of increasing the pulley width.
- the auxiliary pump control unit 312 determines the rotation direction of the auxiliary pump P2 in the direction of narrowing the pulley width.
- the pulley width changing speed is determined by the moving speed of the hydraulic oil inside the closed oil passage 10, that is, the rotational speed of the auxiliary pump P2.
- the auxiliary pump control unit 312 determines the rotation speed so that the auxiliary pump P2 rotates at a higher speed when the target speed change time of the pulley width is shorter than when it is longer.
- the auxiliary pump control unit 312 drives the auxiliary pump P2 based on the rotation direction and the rotation speed of the auxiliary pump P2 calculated in step S130 (step S140). Specifically, as shown in FIG. 3, the auxiliary pump control unit 312 outputs a drive signal sig ⁇ b> 2 of the auxiliary pump P ⁇ b> 2 to the auxiliary pump drive circuit 303.
- the auxiliary pump drive circuit 303 includes a current output circuit such as an inverter, and outputs a drive current I2 to the auxiliary pump P2 based on the drive signal sig2.
- the auxiliary pump P2 moves the hydraulic oil in the positive direction or the negative direction depending on the rotation direction and the rotation speed based on the drive current I2.
- the auxiliary pump control unit 312 acquires position information from the position detection sensor 201 (step S150), and determines whether or not the pulley width has reached the target width (step S160). When determining that the pulley width has not reached the target width (step S160; NO), the auxiliary pump control unit 312 returns the process to step S140 and continues driving the auxiliary pump P2. On the other hand, when it is determined that the pulley width has reached the target width (step S160; YES), the auxiliary pump control unit 312 stops driving the auxiliary pump P2 (step S170). At this time, the failure detection unit 313 performs failure detection processing (steps S210 to S250).
- FIG. 6 is a flowchart illustrating an example of the flow of failure detection processing according to the present embodiment.
- the failure detection unit 313 calculates the speed of change of the pulley width of the secondary pulley SP based on the position information acquired by the auxiliary pump control unit 312 in step S150 (step S210).
- the failure detection unit 313 acquires closed-path hydraulic pressure information indicating the hydraulic pressure of the closed-path 10 from the hydraulic pressure sensor PS2 (step S220).
- the failure detection unit 313 determines that the relationship between the change speed of the pulley width and the oil pressure of the closed path is based on the speed of change of the pulley width calculated in step S210 and the oil pressure information of the closed oil path acquired in step S220.
- step S230 It is determined whether or not it is appropriate (step S230).
- the change speed of the pulley width is fast, the oil closing passage hydraulic pressure becomes a high value.
- the change speed of the pulley width is low, the oil pressure in the closed oil passage becomes a low value. Therefore, when the oil pressure of the closed oil passage is higher than the reference value even though the changing speed of the pulley width is relatively slow, a failure such as clogging of the oil passage 10 or malfunction of the position detection sensor 201 occurs. It can be determined that there is a possibility of being.
- Step S230 If the failure detection unit 313 determines that the relationship between the change speed of the pulley width and the oil pressure in the closed oil passage is appropriate (step S230; YES), the failure detection unit 313 notifies the upper unit 2 of “no failure” (Step S240). On the other hand, if the failure detection unit 313 determines that the relationship between the change speed of the pulley width and the oil pressure in the closed passage is not appropriate (step S230; NO), the failure detection unit 313 notifies the upper unit 2 of “There is a failure”. (Step S250).
- the host unit 2 When the host unit 2 is notified that there is a failure, it determines that the in-vehicle hydraulic pressure supply device 1 or the continuously variable transmission 3 does not operate normally, for example, a control for fixing without changing the gear ratio, etc. It is possible to control when a failure occurs.
- the auxiliary pump control unit 312 may control the auxiliary pump P2 based on the oil pressure of the closed passage detected by the hydraulic sensor PS2.
- the hydraulic pressure sensor PS2 may be more difficult to break than the position detection sensor 201.
- the auxiliary pump control unit 312 controls the auxiliary pump P2 based on the closed-path hydraulic pressure detected by the hydraulic sensor PS2.
- the in-vehicle hydraulic pressure supply device 1 of the present embodiment controls the original pressure without providing a mechanism for draining hydraulic oil such as a pressure control valve.
- the mechanism is provided with a mechanism for draining hydraulic oil such as a pressure control valve
- the hydraulic oil pressurized by the main pump P1 to a pressure higher than the original pressure is discharged to an oil pan or the like for pressure control. Oil.
- the hydraulic pump is pressurized to a pressure higher than the original pressure, so that the main pump P1 is large.
- the hydraulic oil once pressurized to the original pressure or higher is discharged without using the pressure, so that a part of the energy consumed by the main pump P1 is wasted.
- the main pump P1 can be reduced in size and the energy consumption of the main pump P1 can be reduced because the main pressure is controlled without draining the hydraulic oil. Can do.
- the vehicle-mounted hydraulic pressure supply device 1 drives the main pump P1 by pressure feedback by the hydraulic pressure sensor PS1, it is possible to precisely control the original pressure.
- the in-vehicle hydraulic pressure supply device 1 of the present embodiment does not include a mechanism that drains hydraulic oil from the closed oil passage 10. Therefore, according to the in-vehicle hydraulic pressure supply device 1, since the driving frequency of the main pump P1 can be reduced, the energy consumption of the main pump P1 can be reduced.
- a check valve V1 is provided between the oil closing passage 10 and the main pump P1.
- the check valve V ⁇ b> 1 prevents the hydraulic oil in the closed oil passage 10 from flowing back to the hydraulic pressure supply unit 40.
- the vehicle-mounted hydraulic pressure supply device 1 can maintain the hydraulic pressure in the closed oil passage 10 even when the main pump P1 is not operating. That is, the vehicle-mounted hydraulic pressure supply device 1 can reduce the driving frequency of the main pump P1 by providing the check valve V1, and therefore can reduce the energy consumption of the main pump P1.
- the vehicle-mounted hydraulic pressure supply device 1 of the present embodiment allows the hydraulic oil to move between the primary pulley PP and the secondary pulley SP without the hydraulic oil being drained from the closed oil passage 10 by the auxiliary pump P2. This is done by controlling the pressure.
- the pressure of the hydraulic oil is controlled by draining the hydraulic oil from the closed oil passage 10 by a pressure control valve or the like, the hydraulic oil is discharged to an oil pan or the like for pressure control. Oil.
- the auxiliary pump P2 becomes large because the hydraulic oil is pressurized beyond the pressure necessary for the movement of the hydraulic oil.
- the hydraulic oil once pressurized is drained without using the pressure, and thus a part of the energy consumed by the auxiliary pump P2 is wasted.
- the in-vehicle hydraulic pressure supply device 1 of the present embodiment the movement of hydraulic oil between the primary pulley PP and the secondary pulley SP is controlled without draining the hydraulic oil.
- the auxiliary pump P2 can be reduced in size, and the energy consumption of the auxiliary pump P2 can be reduced.
- the in-vehicle hydraulic pressure supply device 1 drives the auxiliary pump P2 on the basis of the input shift command and the detection result of the pulley width state by the pulley width detector 20, and therefore precisely controls the pulley width. Can do.
- the vehicle-mounted hydraulic pressure supply device 1 of the present embodiment includes two check valves V1, that is, a first check valve and a second check valve.
- the in-vehicle hydraulic pressure supply device 1 includes a check valve V11 with respect to the oil closing passage 10 between the primary pulley PP and the auxiliary pump P2.
- the vehicle-mounted hydraulic pressure supply device 1 includes a check valve V12 that supplies hydraulic pressure from the main pump P1 to the closed oil passage 10 between the secondary pulley SP and the auxiliary pump P2. That is, the in-vehicle hydraulic pressure supply device 1 includes a mechanism for supplying a source pressure between the auxiliary pump P2 and the two pulleys. For this reason, since the vehicle-mounted hydraulic pressure supply device 1 can apply a uniform source pressure between the auxiliary pump P2 and the two pulleys, the pulley width can be precisely controlled.
- FIG. 7 is a block diagram illustrating an example of a configuration of the in-vehicle hydraulic pressure supply device 1A according to the second embodiment.
- the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted.
- the in-vehicle hydraulic pressure supply device 1A of the present embodiment is different from the first embodiment in that the main pressure can be varied by forward and reverse rotation of the main pump P1A.
- the in-vehicle hydraulic pressure supply device 1A includes a hydraulic pressure supply unit 40A.
- the hydraulic pressure supply unit 40A includes a bidirectional check valve V10 instead of the check valve V1 described above.
- the bidirectional check valve V10 includes a forward check valve V101 and a reverse check valve V102 which are two check valves arranged in parallel with respect to the moving direction of the hydraulic oil.
- the forward check valve V101 passes hydraulic oil in the forward direction from the main pump P1A to the closed oil passage 10, that is, in the direction of the arrow C1 in FIG. 7, and in the reverse direction from the closed oil passage 10 to the main pump P1A, that is, It does not pass in the direction of arrow D1 in FIG.
- the reverse direction check valve V102 allows hydraulic oil to pass in the reverse direction and not in the forward direction.
- the main pump P1A of this embodiment performs forward and reverse rotation.
- the main pump P1A discharges hydraulic oil in the direction of arrow C in FIG. 7 by rotating forward, and discharges hydraulic oil in the direction of arrow D in FIG. 7 by reverse rotation.
- the in-vehicle hydraulic pressure supply device 1A can control the pulley width more precisely than in the first embodiment.
- the in-vehicle hydraulic pressure supply device 1A may include an orifice ORF shown in FIG.
- the orifice ORF discharges hydraulic oil from the oil passage 601 through the oil passage 502 to the oil pan OP.
- the in-vehicle hydraulic pressure supply device 1A can suppress an increase in the source pressure when the main pump P1 is pressurized to a desired source pressure or higher.
- the in-vehicle hydraulic pressure supply device 1A includes the orifice ORF, so that the original pressure can be controlled within an appropriate range without precisely controlling the main pump P1.
- FIG. 8 is a block diagram illustrating an example of a configuration of an in-vehicle hydraulic pressure supply device 1B according to a modification of the second embodiment.
- the same components as those in the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted.
- the in-vehicle hydraulic pressure supply device 1B of the present embodiment differs from the second embodiment described above in that it includes two bidirectional check valves.
- the in-vehicle hydraulic pressure supply device 1B includes a hydraulic pressure supply unit 40B.
- the hydraulic pressure supply unit 40B includes a bidirectional check valve V10A.
- This bidirectional check valve V10A includes two sets of a forward check valve and a reverse check valve. That is, the bidirectional check valve V10A includes a forward check valve V103 and a reverse check valve V104 in addition to the forward check valve V101 and the reverse check valve V102 described above.
- the in-vehicle hydraulic pressure supply device 1B includes a forward check valve V103 and a reverse check valve V104 with respect to the closed oil passage 10 between the primary pulley PP and the auxiliary pump P2.
- the in-vehicle hydraulic pressure supply device 1B includes a forward check valve V101 and a reverse check valve V102 with respect to the closed oil passage 10 between the secondary pulley SP and the auxiliary pump P2. That is, the in-vehicle hydraulic pressure supply device 1B includes a mechanism for supplying the original pressure between the auxiliary pump P2 and the two pulleys. For this reason, since the vehicle-mounted hydraulic pressure supply device 1B can apply a uniform source pressure between the auxiliary pump P2 and the two pulleys, the pulley width can be precisely controlled.
- FIG. 9 is a block diagram illustrating an example of the configuration of the in-vehicle hydraulic pressure supply device 1C according to the third embodiment.
- the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted.
- the in-vehicle hydraulic pressure supply device 1C according to the present embodiment is different from the first embodiment in that the closed oil passage 10 includes a bypass oil passage BP1.
- the bypass oil passage BP1 is arranged in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil, and includes a bypass valve VBP1 and an orifice ORF2.
- the bypass valve VBP1 allows hydraulic oil to pass when the hydraulic pressure in the closed oil passage 10 is less than a predetermined value, and does not allow hydraulic oil to pass when the hydraulic pressure exceeds a predetermined value.
- the orifice ORF2 suppresses the flow rate of the hydraulic oil that passes through the bypass oil passage BP1.
- An oil filter F1 and an oil filter F2 that suppress clogging of the orifice ORF2 may be provided before and after the orifice ORF2 of the bypass oil passage BP1.
- the auxiliary pump P2 When the auxiliary pump P2 is less than the predetermined number of revolutions, the oil pressure in the closed oil passage 10 becomes less than a predetermined value. In this case, the bypass valve VBP1 is opened and allows hydraulic oil to pass therethrough.
- the case where the auxiliary pump P2 is less than the predetermined number of rotations is a case where the change width of the pulley width is small or a target shift time of the pulley width is long. That is, the case where the auxiliary pump P2 is less than the predetermined rotation number is a case where the change in the pulley width is moderate.
- the hydraulic pressure in the closed oil passage 10 is equal to or higher than a predetermined value.
- the bypass valve VBP1 is closed and does not allow hydraulic oil to pass.
- the case where the auxiliary pump P2 is equal to or higher than the predetermined number of rotations is a case where the change width of the pulley width is large or a target shift time of the pulley width is short. That is, the case where the auxiliary pump P2 is equal to or higher than the predetermined rotation number is a case where the change in the pulley width is abrupt.
- the upper unit 2 outputs a shift command for gently changing the pulley width.
- the auxiliary pump P2 rotates at a low speed in order to gently change the pulley width.
- the increase in the hydraulic pressure in the oil closing passage 10 is moderate, and the bypass valve VBP1 does not close.
- the bypass valve VBP1 when the hydraulic oil in the closed oil passage 10 moves from one pulley to the other pulley, part of it flows again into the auxiliary pump P2 via the bypass oil passage BP1. That is, when the bypass valve VBP1 is in the open state, even if the auxiliary pump P2 discharges hydraulic oil, the entire amount does not move to the other pulley, but only a part moves to the other pulley. Therefore, the pulley width can be gradually changed without precisely controlling the rotation speed of the auxiliary pump P2. That is, the on-board hydraulic pressure supply device 1C can improve the controllability of the pulley width by including the bypass oil passage BP1.
- the upper unit 2 outputs a shift command for changing the pulley width abruptly.
- the auxiliary pump P2 rotates at a high speed in order to rapidly change the pulley width.
- the hydraulic pressure in the oil closing passage 10 increases rapidly, and the bypass valve VBP1 is closed.
- the hydraulic oil in the closed oil passage 10 moves from one pulley to the other pulley via the auxiliary pump P2, not via the bypass oil passage BP1. Therefore, when the bypass valve VBP1 is closed, the moving speed of the hydraulic oil is increased. That is, the in-vehicle hydraulic pressure supply device 1 ⁇ / b> C can improve the control speed of the pulley width by including the bypass valve VBP ⁇ b> 1.
- the in-vehicle hydraulic pressure supply device 1C includes both the bypass oil passage BP1 and the bypass valve VBP1, thereby making it possible to improve both the controllability of the pulley width and the control speed of the pulley width.
- FIG. 10 is a block diagram illustrating an example of a configuration of an in-vehicle hydraulic pressure supply device 1D according to a modification of the third embodiment.
- the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted.
- the in-vehicle hydraulic pressure supply device 1D of the present embodiment is different from the third embodiment in that the closed oil passage 10 further includes a bypass oil passage BP2.
- the bypass oil passage BP2 is disposed in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil, and includes a bypass valve VBP2 and an auxiliary pump P3.
- the bypass valve VBP2 prevents movement of the hydraulic oil in the bypass oil passage BP2 when the oil pressure in the bypass oil passage BP2 is less than a predetermined value, and bypass oil passage when the oil pressure in the bypass oil passage BP2 exceeds a predetermined value. Allows movement of hydraulic oil in BP2.
- the auxiliary pump P3 is provided in the bypass oil passage BP2, and moves the hydraulic oil in the closed oil passage 10 from one of the primary pulley PP and the secondary pulley SP to the other.
- the in-vehicle hydraulic pressure supply device 1D drives the auxiliary pump P3 when the host unit 2 outputs a shift command that causes the pulley width to change abruptly.
- the hydraulic pressure in the bypass oil passage BP2 increases and the bypass valve VBP2 is opened.
- the hydraulic oil in the closed oil passage 10 moves from one pulley to the other pulley via the bypass oil passage BP2 and the auxiliary pump P3. Accordingly, the movement speed of the hydraulic oil is increased by opening the bypass valve VBP2. That is, the in-vehicle hydraulic pressure supply apparatus 1D can improve the control speed of the pulley width by including the bypass oil passage BP2 and the auxiliary pump P3.
- the vehicle-mounted hydraulic pressure supply device 1D can share the hydraulic oil discharge capacity between the auxiliary pump P2 and the auxiliary pump P3 by including the bypass oil passage BP2 and the auxiliary pump P3. Therefore, the auxiliary pump P2 can be downsized as compared with the third embodiment described above. Further, it is possible to share parts for the auxiliary pump P2 and the auxiliary pump P3, and the parts cost can be reduced as compared with a configuration including one large pump.
- the on-vehicle hydraulic pressure supply device 1D includes the bypass valve VBP2, when the pulley width is gradually changed, the auxiliary pump P3 can be stopped, so that the energy consumption of the auxiliary pump P3 can be reduced.
- the in-vehicle hydraulic pressure supply device 1D is provided in the second bypass oil passage and the second bypass oil passage that are arranged in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil.
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Abstract
Provided is an in-vehicle hydraulic supply device for a continuously variable transmission, the device controlling pulley width and thereby varying a speed reduction ratio, wherein the in-vehicle hydraulic supply device is provided with: a closed oil passage provided between a primary pulley and a secondary pulley; a check valve provided between the closed oil passage and a main pump that supplies hydraulic pressure; an auxiliary pump that moves hydraulic oil which is inside the closed oil passage and to which hydraulic pressure supplied from the main pump via the check valve is applied, from either the primary pulley or the secondary pulley to the other; a pulley width detection unit for detecting the state of the pulley width; and a control unit that, on the basis of a gear change command that is inputted and the state of the pulley width detected by the pulley width detection unit, determines the movement direction of either of a positive direction in which the hydraulic oil is moved from the primary pulley to the secondary pulley and a negative direction in which the hydraulic oil is moved from the secondary pulley to the primary pulley, and the movement speed of the hydraulic oil in the positive direction or the negative direction, and drives and controls the auxiliary pump according to the determined movement direction and movement speed.
Description
本発明は、車載油圧供給装置に関する。
The present invention relates to an in-vehicle hydraulic pressure supply device.
例えば、特許文献1に示すように、プライマリプーリとセカンダリプーリとの間の油路に圧油を供給する第1のポンプと、プライマリプーリの油圧室とセカンダリプーリの油圧室との間において圧油の給排を行わせる第2のポンプと、を備える車載油圧供給装置が提案されている。
For example, as shown in Patent Document 1, pressure oil is supplied between a first pump that supplies pressure oil to an oil passage between a primary pulley and a secondary pulley, and a hydraulic chamber of the primary pulley and a hydraulic chamber of the secondary pulley. An in-vehicle hydraulic pressure supply device is proposed that includes a second pump that supplies and discharges the air.
上述のような車載油圧供給装置においては、第1のポンプが加圧した圧油が所望の圧力を超える場合には、圧油の圧力を低下させるために圧油が排油される。したがって、加圧された圧油の圧力が利用されることなく排油されるため、第1のポンプが無駄なエネルギーを消費してしまうという問題があった。
In the on-vehicle hydraulic pressure supply device as described above, when the pressure oil pressurized by the first pump exceeds a desired pressure, the pressure oil is discharged to reduce the pressure oil pressure. Accordingly, since the pressure of the pressurized pressure oil is discharged without being used, there is a problem that the first pump consumes useless energy.
本発明は上記の点に鑑みてなされたものであり、無駄なエネルギーの消費を抑制することにより、消費されるエネルギーを低減することができる車載油圧供給装置を提供することを目的の一つとする。
The present invention has been made in view of the above points, and an object thereof is to provide an in-vehicle hydraulic pressure supply device capable of reducing consumed energy by suppressing wasteful energy consumption. .
本発明の車載油圧供給装置の一つの態様は、油圧発生源から供給される油圧が付された作動油によってプーリ幅が可変するプライマリプーリ及びセカンダリプーリの、それぞれのプーリ幅を制御することにより、減速比を可変する無段階変速機の車載油圧供給装置であって、前記プライマリプーリと、前記セカンダリプーリとの間に設けられた閉油路と、前記閉油路と、油圧を供給する主ポンプとの間に設けられた逆止弁と、前記逆止弁を介して前記主ポンプから供給される油圧が付された前記閉油路内の作動油を、前記プライマリプーリ及び前記セカンダリプーリの一方から他方へ移動させる補助ポンプと、前記プーリ幅の状態を検出するプーリ幅検出部と、入力される変速指令と、前記プーリ幅検出部が検出する前記プーリ幅の状態とに基づいて、前記プライマリプーリから前記セカンダリプーリに前記作動油を移動させる正方向、及び前記セカンダリプーリから前記プライマリプーリに前記作動油を移動させる負方向のいずれかの移動方向と、前記作動油の前記正方向又は前記負方向への移動速度とを決定し、決定した前記移動方向及び前記移動速度によって前記補助ポンプを駆動制御する制御部とを備える。
One aspect of the in-vehicle hydraulic pressure supply device of the present invention is to control the pulley width of each of the primary pulley and the secondary pulley whose pulley width is variable by hydraulic oil to which hydraulic pressure supplied from a hydraulic pressure generation source is attached, A vehicle-mounted hydraulic pressure supply device for a continuously variable transmission that varies a reduction ratio, the closed oil path provided between the primary pulley and the secondary pulley, the closed oil path, and a main pump for supplying hydraulic pressure A check valve provided between the main pulley and hydraulic oil supplied from the main pump via the check valve to the hydraulic oil in one of the primary pulley and the secondary pulley. An auxiliary pump that moves from one to the other, a pulley width detector that detects the pulley width state, a shift command that is input, and the pulley width state that the pulley width detector detects Based on any one of a positive direction in which the hydraulic oil is moved from the primary pulley to the secondary pulley, and a negative direction in which the hydraulic oil is moved from the secondary pulley to the primary pulley; A control unit that determines a moving speed in the positive direction or the negative direction, and drives and controls the auxiliary pump according to the determined moving direction and the moving speed.
本発明の一つの態様によれば、消費されるエネルギーを低減することができる車載油圧供給装置が提供される。
According to one aspect of the present invention, an in-vehicle hydraulic pressure supply device that can reduce consumed energy is provided.
以下、図面を参照しながら、本発明の実施形態に係る車載油圧供給装置について説明する。なお、本発明の範囲は、以下の実施の形態に限定されるものではなく、本発明の技術的思想の範囲内で任意に変更可能である。
Hereinafter, an in-vehicle hydraulic pressure supply device according to an embodiment of the present invention will be described with reference to the drawings. The scope of the present invention is not limited to the following embodiment, and can be arbitrarily changed within the scope of the technical idea of the present invention.
[第1実施形態]
図1から図6を参照して、第1実施形態に係る車載油圧供給装置1について説明する。図1は、第1実施形態の車載油圧供給装置1の構成の一例を示すブロック図である。この車載油圧供給装置1は、上位ユニット2による変速指令に基づいて、車両の無段階変速装置3に油圧を供給する。 [First Embodiment]
An in-vehicle hydraulicpressure supply device 1 according to the first embodiment will be described with reference to FIGS. 1 to 6. FIG. 1 is a block diagram illustrating an example of the configuration of the in-vehicle hydraulic pressure supply device 1 according to the first embodiment. The in-vehicle hydraulic pressure supply device 1 supplies hydraulic pressure to the continuously variable transmission 3 of the vehicle based on a shift command from the host unit 2.
図1から図6を参照して、第1実施形態に係る車載油圧供給装置1について説明する。図1は、第1実施形態の車載油圧供給装置1の構成の一例を示すブロック図である。この車載油圧供給装置1は、上位ユニット2による変速指令に基づいて、車両の無段階変速装置3に油圧を供給する。 [First Embodiment]
An in-vehicle hydraulic
[無段階変速装置3の概要]
無段階変速装置3は、プライマリプーリPPと、セカンダリプーリSPと、ベルトVTとを備えている。プライマリプーリPPには、原動機(不図示)が出力する回転力が伝達される。ベルトVTは、プライマリプーリPPと、セカンダリプーリSPとの間に巻きかけられており、プライマリプーリPPに伝達された回転力を、セカンダリプーリSPに伝達する。セカンダリプーリSPは、ベルトVTから伝達された回転力を、回転力の伝達機構(不図示)を介して、車両の車輪(不図示)に伝達する。 [Outline of continuously variable transmission 3]
The continuouslyvariable transmission 3 includes a primary pulley PP, a secondary pulley SP, and a belt VT. A rotational force output from a prime mover (not shown) is transmitted to the primary pulley PP. The belt VT is wound between the primary pulley PP and the secondary pulley SP, and transmits the rotational force transmitted to the primary pulley PP to the secondary pulley SP. The secondary pulley SP transmits the rotational force transmitted from the belt VT to a vehicle wheel (not shown) via a rotational force transmission mechanism (not shown).
無段階変速装置3は、プライマリプーリPPと、セカンダリプーリSPと、ベルトVTとを備えている。プライマリプーリPPには、原動機(不図示)が出力する回転力が伝達される。ベルトVTは、プライマリプーリPPと、セカンダリプーリSPとの間に巻きかけられており、プライマリプーリPPに伝達された回転力を、セカンダリプーリSPに伝達する。セカンダリプーリSPは、ベルトVTから伝達された回転力を、回転力の伝達機構(不図示)を介して、車両の車輪(不図示)に伝達する。 [Outline of continuously variable transmission 3]
The continuously
プライマリプーリPP、及びセカンダリプーリSPは、いずれもプーリ幅が可変である。具体的には、プライマリプーリPPは、固定側プライマリプーリPP1と、可動側プライマリプーリPP2とを備えている。可動側プライマリプーリPP2がプーリの回転軸方向に、すなわち図中の矢印AX1の方向に移動することにより、プライマリプーリPPのプーリ幅が変化する。
また、セカンダリプーリSPは、固定側セカンダリプーリSP1と、可動側セカンダリプーリSP2とを備えている。可動側セカンダリプーリSP2がプーリの回転軸方向に、すなわち図中の矢印AX2の方向に移動することにより、セカンダリプーリSPのプーリ幅が変化する。これらのプーリのベルトVTが巻きかけられている面は、円錐状である。プーリ幅が広い状態では、ベルトVTは、プーリの内周部分に接する。プーリ幅が狭い状態では、ベルトVTは、プーリの外周部分に接する。プライマリプーリPPのプーリ幅と、セカンダリプーリSPのプーリ幅とを変化させることにより、減速比が変化する。具体的には、プライマリプーリPPのプーリ幅を広く、セカンダリプーリSPのプーリ幅を狭くすると、減速比が大きくなる。逆に、プライマリプーリPPのプーリ幅を狭く、セカンダリプーリSPのプーリ幅を広くすると、減速比が小さくなる。 Both the primary pulley PP and the secondary pulley SP have a variable pulley width. Specifically, the primary pulley PP includes a fixed primary pulley PP1 and a movable primary pulley PP2. When the movable primary pulley PP2 moves in the direction of the rotation axis of the pulley, that is, in the direction of the arrow AX1 in the drawing, the pulley width of the primary pulley PP changes.
The secondary pulley SP includes a fixed secondary pulley SP1 and a movable secondary pulley SP2. As the movable secondary pulley SP2 moves in the direction of the rotation axis of the pulley, that is, in the direction of the arrow AX2 in the drawing, the pulley width of the secondary pulley SP changes. The surface on which the belt VT of these pulleys is wound is conical. In the state where the pulley width is wide, the belt VT contacts the inner peripheral portion of the pulley. In the state where the pulley width is narrow, the belt VT contacts the outer peripheral portion of the pulley. The reduction gear ratio is changed by changing the pulley width of the primary pulley PP and the pulley width of the secondary pulley SP. Specifically, when the pulley width of the primary pulley PP is widened and the pulley width of the secondary pulley SP is narrowed, the reduction ratio is increased. Conversely, if the pulley width of the primary pulley PP is narrowed and the pulley width of the secondary pulley SP is widened, the reduction gear ratio becomes small.
また、セカンダリプーリSPは、固定側セカンダリプーリSP1と、可動側セカンダリプーリSP2とを備えている。可動側セカンダリプーリSP2がプーリの回転軸方向に、すなわち図中の矢印AX2の方向に移動することにより、セカンダリプーリSPのプーリ幅が変化する。これらのプーリのベルトVTが巻きかけられている面は、円錐状である。プーリ幅が広い状態では、ベルトVTは、プーリの内周部分に接する。プーリ幅が狭い状態では、ベルトVTは、プーリの外周部分に接する。プライマリプーリPPのプーリ幅と、セカンダリプーリSPのプーリ幅とを変化させることにより、減速比が変化する。具体的には、プライマリプーリPPのプーリ幅を広く、セカンダリプーリSPのプーリ幅を狭くすると、減速比が大きくなる。逆に、プライマリプーリPPのプーリ幅を狭く、セカンダリプーリSPのプーリ幅を広くすると、減速比が小さくなる。 Both the primary pulley PP and the secondary pulley SP have a variable pulley width. Specifically, the primary pulley PP includes a fixed primary pulley PP1 and a movable primary pulley PP2. When the movable primary pulley PP2 moves in the direction of the rotation axis of the pulley, that is, in the direction of the arrow AX1 in the drawing, the pulley width of the primary pulley PP changes.
The secondary pulley SP includes a fixed secondary pulley SP1 and a movable secondary pulley SP2. As the movable secondary pulley SP2 moves in the direction of the rotation axis of the pulley, that is, in the direction of the arrow AX2 in the drawing, the pulley width of the secondary pulley SP changes. The surface on which the belt VT of these pulleys is wound is conical. In the state where the pulley width is wide, the belt VT contacts the inner peripheral portion of the pulley. In the state where the pulley width is narrow, the belt VT contacts the outer peripheral portion of the pulley. The reduction gear ratio is changed by changing the pulley width of the primary pulley PP and the pulley width of the secondary pulley SP. Specifically, when the pulley width of the primary pulley PP is widened and the pulley width of the secondary pulley SP is narrowed, the reduction ratio is increased. Conversely, if the pulley width of the primary pulley PP is narrowed and the pulley width of the secondary pulley SP is widened, the reduction gear ratio becomes small.
可動側プライマリプーリPP2及び可動側セカンダリプーリSP2は、いずれも油室(不図示)を備えている。これらの可動側プーリは、油室に存在する作動油の量によって、プーリの回転軸方向の位置が定められる。これらの可動側プーリは、油室に存在する作動油の量が多いほどプーリ幅が広がる方向に移動し、作動油の量が少ないほどプーリ幅が狭まる方向に移動する。逆に、これらの可動側プーリは、油室に存在する作動油の量が多いほどプーリ幅が狭まる方向に移動し、作動油の量が少ないほどプーリ幅が広がる方向に移動する構成であってもよい。
なお、以下の説明においては、固定側、可動側の区別、及び油室の記載は省略する。例えば、可動側プライマリプーリPP2の油室に作動油を供給することを、単に、プライマリプーリPPに作動油を供給する、と記載する。また、可動側セカンダリプーリSP2の油室に作動油を供給することを、単に、セカンダリプーリSPに作動油を供給する、と記載する。 Each of the movable primary pulley PP2 and the movable secondary pulley SP2 includes an oil chamber (not shown). The position of the movable pulley in the rotational axis direction of the pulley is determined by the amount of hydraulic oil present in the oil chamber. These movable pulleys move in the direction in which the pulley width increases as the amount of hydraulic oil present in the oil chamber increases, and move in the direction in which the pulley width decreases as the amount of hydraulic oil decreases. Conversely, these movable pulleys move in a direction in which the pulley width decreases as the amount of hydraulic oil present in the oil chamber increases, and move in a direction in which the pulley width increases as the amount of hydraulic oil decreases. Also good.
In the following description, the distinction between the fixed side and the movable side and the description of the oil chamber are omitted. For example, supplying hydraulic oil to the oil chamber of the movable primary pulley PP2 is simply described as supplying hydraulic oil to the primary pulley PP. Moreover, supplying hydraulic fluid to the oil chamber of the movable secondary pulley SP2 is simply described as supplying hydraulic fluid to the secondary pulley SP.
なお、以下の説明においては、固定側、可動側の区別、及び油室の記載は省略する。例えば、可動側プライマリプーリPP2の油室に作動油を供給することを、単に、プライマリプーリPPに作動油を供給する、と記載する。また、可動側セカンダリプーリSP2の油室に作動油を供給することを、単に、セカンダリプーリSPに作動油を供給する、と記載する。 Each of the movable primary pulley PP2 and the movable secondary pulley SP2 includes an oil chamber (not shown). The position of the movable pulley in the rotational axis direction of the pulley is determined by the amount of hydraulic oil present in the oil chamber. These movable pulleys move in the direction in which the pulley width increases as the amount of hydraulic oil present in the oil chamber increases, and move in the direction in which the pulley width decreases as the amount of hydraulic oil decreases. Conversely, these movable pulleys move in a direction in which the pulley width decreases as the amount of hydraulic oil present in the oil chamber increases, and move in a direction in which the pulley width increases as the amount of hydraulic oil decreases. Also good.
In the following description, the distinction between the fixed side and the movable side and the description of the oil chamber are omitted. For example, supplying hydraulic oil to the oil chamber of the movable primary pulley PP2 is simply described as supplying hydraulic oil to the primary pulley PP. Moreover, supplying hydraulic fluid to the oil chamber of the movable secondary pulley SP2 is simply described as supplying hydraulic fluid to the secondary pulley SP.
プライマリプーリPP及びセカンダリプーリSPには、ベルトVTの張力によって、プーリ幅を広げる方向に働く力がベルトVTから加えられる。プライマリプーリPP及びセカンダリプーリSPには、この力に抗するために、所定の圧力に加圧された作動油が供給される。以下の説明において、この所定の圧力を、元圧とも記載する。元圧の設定範囲は、本実施形態の一例では、4~5[Mpa]程度である。つまり、プライマリプーリPP及びセカンダリプーリSPには、4~5[Mpa]程度に加圧された作動油が供給される。
The primary pulley PP and the secondary pulley SP are applied with a force acting from the belt VT to increase the pulley width by the tension of the belt VT. The primary pulley PP and the secondary pulley SP are supplied with hydraulic oil pressurized to a predetermined pressure in order to resist this force. In the following description, this predetermined pressure is also referred to as a source pressure. The setting range of the source pressure is about 4 to 5 [Mpa] in the example of the present embodiment. That is, hydraulic oil pressurized to about 4 to 5 [Mpa] is supplied to the primary pulley PP and the secondary pulley SP.
[車載油圧供給装置1の構成]
次に、これらプライマリプーリPP及びセカンダリプーリSPのプーリ幅を制御する車載油圧供給装置1の構成について説明する。車載油圧供給装置1は、閉油路10と、プーリ幅検出部20と、制御ユニット30と、油圧供給部40とを備える。 [Configuration of In-vehicle Hydraulic Supply Device 1]
Next, the configuration of the in-vehicle hydraulicpressure supply device 1 that controls the pulley widths of the primary pulley PP and the secondary pulley SP will be described. The in-vehicle hydraulic pressure supply device 1 includes an oil closing path 10, a pulley width detection unit 20, a control unit 30, and a hydraulic pressure supply unit 40.
次に、これらプライマリプーリPP及びセカンダリプーリSPのプーリ幅を制御する車載油圧供給装置1の構成について説明する。車載油圧供給装置1は、閉油路10と、プーリ幅検出部20と、制御ユニット30と、油圧供給部40とを備える。 [Configuration of In-vehicle Hydraulic Supply Device 1]
Next, the configuration of the in-vehicle hydraulic
プーリ幅検出部20は、プライマリプーリPP又はセカンダリプーリSPのプーリ幅の状態を検出する。ここで、プーリ幅の状態とは、可動側プーリの回転軸方向の位置や、固定側プーリと可動側プーリとの間隔などである。プーリ幅検出部20は、プライマリプーリPP及びセカンダリプーリSPの両方のプーリについて、プーリ幅の状態を検出してもよく、いずれか一方のプーリについて、プーリ幅の状態を検出してもよい。
一例として、プーリ幅検出部20は、位置検出センサ201を備えている。この位置検出センサ201は、プライマリプーリPP又はセカンダリプーリSPの近傍に配置されており、磁気や光学系による計測によって、可動側プーリの幅方向の位置の検出を行う。
プーリ幅検出部20は、検出したプーリ幅の状態を、制御ユニット30に出力する。 Thepulley width detector 20 detects the pulley width state of the primary pulley PP or the secondary pulley SP. Here, the state of the pulley width refers to the position of the movable pulley in the rotation axis direction, the interval between the fixed pulley and the movable pulley, and the like. The pulley width detection unit 20 may detect the pulley width state for both the primary pulley PP and the secondary pulley SP, or may detect the pulley width state for either one of the pulleys.
As an example, the pulleywidth detection unit 20 includes a position detection sensor 201. The position detection sensor 201 is disposed in the vicinity of the primary pulley PP or the secondary pulley SP, and detects the position in the width direction of the movable pulley by measurement using magnetism or an optical system.
Thepulley width detector 20 outputs the detected pulley width state to the control unit 30.
一例として、プーリ幅検出部20は、位置検出センサ201を備えている。この位置検出センサ201は、プライマリプーリPP又はセカンダリプーリSPの近傍に配置されており、磁気や光学系による計測によって、可動側プーリの幅方向の位置の検出を行う。
プーリ幅検出部20は、検出したプーリ幅の状態を、制御ユニット30に出力する。 The
As an example, the pulley
The
閉油路10は、プライマリプーリPPと、セカンダリプーリSPとの間に設けられており、プライマリプーリPPとセカンダリプーリSPとの間において、作動油を移動させる。なお、閉油路10には、内部の作動油が所定圧を超える場合に排油する機構が備えられていない。したがって、油路のつなぎ目や弁の隙間等から漏れ出るような場合を除き、閉油路10の内部の作動油の油量は、変化しない。
The oil closing path 10 is provided between the primary pulley PP and the secondary pulley SP, and moves the hydraulic oil between the primary pulley PP and the secondary pulley SP. Note that the closed oil passage 10 is not provided with a mechanism for draining oil when the internal hydraulic oil exceeds a predetermined pressure. Therefore, the amount of hydraulic oil in the closed oil passage 10 does not change except when it leaks from the joints of the oil passages, valve gaps, and the like.
閉油路10には、補助ポンプP2、油圧センサPS2、及び双方向逆止弁V2が備えられている。以下の説明において必要がある場合には、プライマリプーリPPと双方向逆止弁V2との間の閉油路10を、閉油路101と記載する。双方向逆止弁V2と補助ポンプP2との間の閉油路10を、閉油路102と記載する。補助ポンプP2と油圧センサPS2との間の閉油路10を、閉油路103と記載する。油圧センサPS2とセカンダリプーリSPとの間の閉油路10を、閉油路104と記載する。すなわち、閉油路10は、閉油路101、閉油路102、閉油路103、及び閉油路104を備え、これらが記載順に接続されている。なお、プライマリプーリPPとセカンダリプーリSPとの間の、補助ポンプP2、油圧センサPS2、及び双方向逆止弁V2の配置の順序は一例であって、図示したものに限られない。
The oil closing path 10 is provided with an auxiliary pump P2, a hydraulic pressure sensor PS2, and a bidirectional check valve V2. When necessary in the following description, the oil closing path 10 between the primary pulley PP and the bidirectional check valve V2 is referred to as an oil closing path 101. The oil closing passage 10 between the bidirectional check valve V2 and the auxiliary pump P2 is referred to as an oil closing passage 102. The closed oil passage 10 between the auxiliary pump P2 and the hydraulic pressure sensor PS2 is referred to as an oil closed passage 103. The closed oil passage 10 between the hydraulic sensor PS2 and the secondary pulley SP is referred to as an oil closed passage 104. In other words, the oil closed path 10 includes an oil closed path 101, an oil closed path 102, an oil closed path 103, and an oil closed path 104, which are connected in the order of description. The order of arrangement of the auxiliary pump P2, the hydraulic pressure sensor PS2, and the bidirectional check valve V2 between the primary pulley PP and the secondary pulley SP is an example, and is not limited to the illustrated one.
補助ポンプP2は、プライマリプーリPPとセカンダリプーリSPとの間において、閉油路10の内部の作動油を移動させる。補助ポンプP2は、正回転及び逆回転が可能である。補助ポンプP2は、正回転して、プライマリプーリPPからセカンダリプーリSPに、つまり図中の矢印A方向に、作動油を移動させる。以下の説明において、この矢印A方向を、正方向とも記載する。また、補助ポンプP2は、逆回転して、セカンダリプーリSPからプライマリプーリPPに、つまり図中の矢印B方向に、作動油を移動させる。以下の説明において、この矢印B方向を、負方向とも記載する。つまり、補助ポンプP2は、回転方向を変化させることにより、作動油の移動方向を変化させる。以下の説明において、補助ポンプP2が電動ポンプである例について説明するが、これに限られない。補助ポンプP2は、制御ユニット30による制御に基づいて動作する。
なお、この一例においては、補助ポンプP2が、回転方向を変化させて作動油の移動方向を変化させる場合について説明するが、これに限られない。例えば、作動油の吐出方向が互いに逆方向の2台の補助ポンプが組み合わされて、いずれか一方の補助ポンプを動作させることにより、作動油の移動方向を変更する構成であってもよい。 The auxiliary pump P2 moves the hydraulic oil inside the oil closedpath 10 between the primary pulley PP and the secondary pulley SP. The auxiliary pump P2 can rotate forward and backward. The auxiliary pump P2 rotates forward to move the hydraulic oil from the primary pulley PP to the secondary pulley SP, that is, in the direction of arrow A in the figure. In the following description, this arrow A direction is also referred to as a positive direction. Further, the auxiliary pump P2 rotates in the reverse direction to move the hydraulic oil from the secondary pulley SP to the primary pulley PP, that is, in the direction of arrow B in the drawing. In the following description, this arrow B direction is also referred to as a negative direction. That is, the auxiliary pump P2 changes the moving direction of the hydraulic oil by changing the rotation direction. In the following description, an example in which the auxiliary pump P2 is an electric pump will be described, but the present invention is not limited to this. The auxiliary pump P2 operates based on control by the control unit 30.
In this example, the case where the auxiliary pump P2 changes the rotation direction to change the moving direction of the hydraulic oil will be described, but is not limited thereto. For example, a configuration may be adopted in which two auxiliary pumps whose hydraulic oil discharge directions are opposite to each other are combined to operate one of the auxiliary pumps to change the moving direction of the hydraulic oil.
なお、この一例においては、補助ポンプP2が、回転方向を変化させて作動油の移動方向を変化させる場合について説明するが、これに限られない。例えば、作動油の吐出方向が互いに逆方向の2台の補助ポンプが組み合わされて、いずれか一方の補助ポンプを動作させることにより、作動油の移動方向を変更する構成であってもよい。 The auxiliary pump P2 moves the hydraulic oil inside the oil closed
In this example, the case where the auxiliary pump P2 changes the rotation direction to change the moving direction of the hydraulic oil will be described, but is not limited thereto. For example, a configuration may be adopted in which two auxiliary pumps whose hydraulic oil discharge directions are opposite to each other are combined to operate one of the auxiliary pumps to change the moving direction of the hydraulic oil.
油圧センサPS2は、閉油路10の内部の作動油の圧力を検出する。油圧センサPS2は、検出した圧力を制御ユニット30に出力する。
The hydraulic pressure sensor PS2 detects the pressure of the hydraulic oil inside the closed oil passage 10. The hydraulic sensor PS2 outputs the detected pressure to the control unit 30.
[双方向逆止弁V2について]
双方向逆止弁V2は、正方向逆止弁V21と、負方向逆止弁V22とを備えている。正方向逆止弁V21は、作動油を、図中の矢印A1方向、つまり正方向に通過させ、かつ図中の矢印B1方向、つまり負方向に通過させない。負方向逆止弁V22は、作動油を、図中の矢印B2方向、つまり負方向に通過させ、かつ図中の矢印A2方向、つまり正方向に通過させない。これら正方向逆止弁V21及び負方向逆止弁V22は、作動油の移動方向に対して並列に配置されている。作動油が正方向に移動する場合には、正方向逆止弁V21が開弁し、負方向逆止弁V22が閉弁する。作動油が負方向に移動する場合には、正方向逆止弁V21が閉弁し、負方向逆止弁V22が開弁する。 [Bidirectional check valve V2]
The bidirectional check valve V2 includes a positive check valve V21 and a negative check valve V22. The forward check valve V21 allows hydraulic oil to pass in the direction of arrow A1 in the drawing, that is, in the positive direction, and does not pass in the direction of arrow B1 in the drawing, that is, in the negative direction. The negative direction check valve V22 allows hydraulic oil to pass in the direction of arrow B2 in the drawing, that is, in the negative direction, and not in the direction of arrow A2 in the drawing, that is, in the positive direction. These positive direction check valve V21 and negative direction check valve V22 are arranged in parallel with respect to the moving direction of the hydraulic oil. When the hydraulic oil moves in the forward direction, the forward direction check valve V21 is opened and the negative direction check valve V22 is closed. When the hydraulic oil moves in the negative direction, the positive direction check valve V21 is closed and the negative direction check valve V22 is opened.
双方向逆止弁V2は、正方向逆止弁V21と、負方向逆止弁V22とを備えている。正方向逆止弁V21は、作動油を、図中の矢印A1方向、つまり正方向に通過させ、かつ図中の矢印B1方向、つまり負方向に通過させない。負方向逆止弁V22は、作動油を、図中の矢印B2方向、つまり負方向に通過させ、かつ図中の矢印A2方向、つまり正方向に通過させない。これら正方向逆止弁V21及び負方向逆止弁V22は、作動油の移動方向に対して並列に配置されている。作動油が正方向に移動する場合には、正方向逆止弁V21が開弁し、負方向逆止弁V22が閉弁する。作動油が負方向に移動する場合には、正方向逆止弁V21が閉弁し、負方向逆止弁V22が開弁する。 [Bidirectional check valve V2]
The bidirectional check valve V2 includes a positive check valve V21 and a negative check valve V22. The forward check valve V21 allows hydraulic oil to pass in the direction of arrow A1 in the drawing, that is, in the positive direction, and does not pass in the direction of arrow B1 in the drawing, that is, in the negative direction. The negative direction check valve V22 allows hydraulic oil to pass in the direction of arrow B2 in the drawing, that is, in the negative direction, and not in the direction of arrow A2 in the drawing, that is, in the positive direction. These positive direction check valve V21 and negative direction check valve V22 are arranged in parallel with respect to the moving direction of the hydraulic oil. When the hydraulic oil moves in the forward direction, the forward direction check valve V21 is opened and the negative direction check valve V22 is closed. When the hydraulic oil moves in the negative direction, the positive direction check valve V21 is closed and the negative direction check valve V22 is opened.
この双方向逆止弁V2は、図2に示すように、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない油圧範囲を有していてもよい。
図2は、本実施形態の双方向逆止弁V2の開弁油圧しきい値の一例を示すグラフである。正方向逆止弁V21は、閉油路101の作動油の油圧が、閉油路102の作動油の油圧に比べて大きい場合に、開弁する。具体的には、図2(a)に示すように、正方向逆止弁V21は、閉油路101の油圧と、閉油路102の油圧との差が、しきい値Th1を正方向に超える場合に、開弁する。また、負方向逆止弁V22は、閉油路102の作動油の油圧が、閉油路101の作動油の油圧に比べて大きい場合に開弁する。具体的には、図2(b)に示すように、負方向逆止弁V22は、閉油路101の油圧と、閉油路102の油圧との差が、しきい値Th2を負方向に超える場合に、開弁する。図2に示すように、差圧が0(ゼロ)である基準位置から、しきい値Th1が正方向に、しきい値Th2が負方向にそれぞれ離れている場合には、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない油圧範囲が生じる。 As shown in FIG. 2, the bidirectional check valve V2 may have a hydraulic range in which neither the positive direction check valve V21 nor the negative direction check valve V22 is opened.
FIG. 2 is a graph showing an example of the valve opening hydraulic pressure threshold value of the bidirectional check valve V2 of the present embodiment. The forward check valve V21 opens when the hydraulic oil pressure in theclosed oil passage 101 is greater than the hydraulic oil pressure in the closed oil passage 102. Specifically, as shown in FIG. 2A, the forward check valve V21 is such that the difference between the oil pressure of the oil closing passage 101 and the oil pressure of the oil closing passage 102 is such that the threshold value Th1 is set in the positive direction. If exceeded, the valve is opened. The negative check valve V22 opens when the hydraulic oil pressure in the closed oil passage 102 is greater than the hydraulic oil pressure in the closed oil passage 101. Specifically, as shown in FIG. 2B, the negative check valve V22 is configured such that the difference between the oil pressure of the oil closing passage 101 and the oil pressure of the oil closing passage 102 causes the threshold Th2 to be negative. If exceeded, the valve is opened. As shown in FIG. 2, when the threshold value Th1 is away in the positive direction and the threshold value Th2 is away in the negative direction from the reference position where the differential pressure is 0 (zero), the forward direction check valve A hydraulic pressure range is generated in which neither V21 nor the negative check valve V22 is opened.
図2は、本実施形態の双方向逆止弁V2の開弁油圧しきい値の一例を示すグラフである。正方向逆止弁V21は、閉油路101の作動油の油圧が、閉油路102の作動油の油圧に比べて大きい場合に、開弁する。具体的には、図2(a)に示すように、正方向逆止弁V21は、閉油路101の油圧と、閉油路102の油圧との差が、しきい値Th1を正方向に超える場合に、開弁する。また、負方向逆止弁V22は、閉油路102の作動油の油圧が、閉油路101の作動油の油圧に比べて大きい場合に開弁する。具体的には、図2(b)に示すように、負方向逆止弁V22は、閉油路101の油圧と、閉油路102の油圧との差が、しきい値Th2を負方向に超える場合に、開弁する。図2に示すように、差圧が0(ゼロ)である基準位置から、しきい値Th1が正方向に、しきい値Th2が負方向にそれぞれ離れている場合には、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない油圧範囲が生じる。 As shown in FIG. 2, the bidirectional check valve V2 may have a hydraulic range in which neither the positive direction check valve V21 nor the negative direction check valve V22 is opened.
FIG. 2 is a graph showing an example of the valve opening hydraulic pressure threshold value of the bidirectional check valve V2 of the present embodiment. The forward check valve V21 opens when the hydraulic oil pressure in the
ここで、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない油圧範囲が無い場合、つまり閉油路101と閉油路102とに差圧が生じている場合には、一方の逆止弁が開弁する構成である場合について説明する。一例として、しきい値Th1と、しきい値Th2とがいずれも0(ゼロ)である場合について説明する。上述したように、プライマリプーリPP及びセカンダリプーリSPには、ベルトVTから、プーリ幅を広げる方向に働く力が加えられている。この力が加えられることにより、プライマリプーリPP及びセカンダリプーリSPのプーリ幅が変化すると、閉油路10の各部における作動油の
圧力が変化する。
プライマリプーリPPからセカンダリプーリSPに、つまり正方向に作動油が移動しようとする場合には、閉油路102の油圧に対して、閉油路101の油圧が高まる。ここで、正方向逆止弁V21が開弁するしきい値Th1が0(ゼロ)であると、閉油路102の油圧に対して、閉油路101の油圧が高まると、ただちに開弁する。
また、セカンダリプーリSPからプライマリプーリPPに、つまり負方向に作動油が移動しようとする場合には、閉油路101の油圧に対して、閉油路102の油圧が高まる。ここで、負方向逆止弁V22が開弁するしきい値Th2が0(ゼロ)であると、閉油路101の油圧に対して、閉油路102の油圧が高まると、ただちに開弁する。
つまり、しきい値Th1と、しきい値Th2とがいずれも0(ゼロ)である場合には、双方向逆止弁V2は、作動油の移動を抑止しない。この場合、例えば、作動油の移動方向とは逆方向に補助ポンプP2を回転させることにより、プライマリプーリPPとセカンダリプーリSPとの間の作動油の移動を抑止することができる。しかしながら、補助ポンプP2を、作動油の移動を抑止するために動作させると、補助ポンプP2を駆動するエネルギーの消費が生じる。 Here, when there is no hydraulic range where neither the positive direction check valve V21 nor the negative direction check valve V22 opens, that is, when a differential pressure is generated between the oil closedpath 101 and the oil closed path 102. Will describe a case where one check valve is configured to open. As an example, a case will be described in which the threshold value Th1 and the threshold value Th2 are both 0 (zero). As described above, the primary pulley PP and the secondary pulley SP are applied with a force acting in the direction of increasing the pulley width from the belt VT. By applying this force, when the pulley widths of the primary pulley PP and the secondary pulley SP change, the pressure of the hydraulic oil in each part of the oil closing path 10 changes.
When the hydraulic oil is going to move from the primary pulley PP to the secondary pulley SP, that is, in the positive direction, the hydraulic pressure of the closedoil passage 101 is higher than the hydraulic pressure of the closed oil passage 102. Here, when the threshold value Th1 at which the forward check valve V21 opens is 0 (zero), the valve is immediately opened when the oil pressure in the oil closing passage 101 increases with respect to the oil pressure in the oil closing passage 102. .
Further, when the hydraulic oil is about to move from the secondary pulley SP to the primary pulley PP, that is, in the negative direction, the hydraulic pressure of the closedoil passage 102 is higher than the hydraulic pressure of the closed oil passage 101. Here, when the threshold value Th2 for opening the negative check valve V22 is 0 (zero), the valve is immediately opened when the oil pressure in the oil closing passage 102 is increased with respect to the oil pressure in the oil closing passage 101. .
That is, when both the threshold value Th1 and the threshold value Th2 are 0 (zero), the bidirectional check valve V2 does not inhibit the movement of the hydraulic oil. In this case, for example, the movement of the hydraulic oil between the primary pulley PP and the secondary pulley SP can be suppressed by rotating the auxiliary pump P2 in the direction opposite to the moving direction of the hydraulic oil. However, if the auxiliary pump P2 is operated in order to suppress the movement of the hydraulic oil, consumption of energy for driving the auxiliary pump P2 occurs.
圧力が変化する。
プライマリプーリPPからセカンダリプーリSPに、つまり正方向に作動油が移動しようとする場合には、閉油路102の油圧に対して、閉油路101の油圧が高まる。ここで、正方向逆止弁V21が開弁するしきい値Th1が0(ゼロ)であると、閉油路102の油圧に対して、閉油路101の油圧が高まると、ただちに開弁する。
また、セカンダリプーリSPからプライマリプーリPPに、つまり負方向に作動油が移動しようとする場合には、閉油路101の油圧に対して、閉油路102の油圧が高まる。ここで、負方向逆止弁V22が開弁するしきい値Th2が0(ゼロ)であると、閉油路101の油圧に対して、閉油路102の油圧が高まると、ただちに開弁する。
つまり、しきい値Th1と、しきい値Th2とがいずれも0(ゼロ)である場合には、双方向逆止弁V2は、作動油の移動を抑止しない。この場合、例えば、作動油の移動方向とは逆方向に補助ポンプP2を回転させることにより、プライマリプーリPPとセカンダリプーリSPとの間の作動油の移動を抑止することができる。しかしながら、補助ポンプP2を、作動油の移動を抑止するために動作させると、補助ポンプP2を駆動するエネルギーの消費が生じる。 Here, when there is no hydraulic range where neither the positive direction check valve V21 nor the negative direction check valve V22 opens, that is, when a differential pressure is generated between the oil closed
When the hydraulic oil is going to move from the primary pulley PP to the secondary pulley SP, that is, in the positive direction, the hydraulic pressure of the closed
Further, when the hydraulic oil is about to move from the secondary pulley SP to the primary pulley PP, that is, in the negative direction, the hydraulic pressure of the closed
That is, when both the threshold value Th1 and the threshold value Th2 are 0 (zero), the bidirectional check valve V2 does not inhibit the movement of the hydraulic oil. In this case, for example, the movement of the hydraulic oil between the primary pulley PP and the secondary pulley SP can be suppressed by rotating the auxiliary pump P2 in the direction opposite to the moving direction of the hydraulic oil. However, if the auxiliary pump P2 is operated in order to suppress the movement of the hydraulic oil, consumption of energy for driving the auxiliary pump P2 occurs.
一方、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない油圧範囲を有する場合には、双方向逆止弁V2によって作動油の移動を抑止することができる。したがって、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない油圧範囲を有する場合には、作動油の移動を抑止するためのエネルギー消費を低減することができる。さらに、ベルトVTからプライマリプーリPP及びセカンダリプーリSPに力が加わったとしても、正方向逆止弁V21と、負方向逆止弁V22とがいずれも開弁しない値にして、各しきい値を設定すれば、上述のエネルギー消費をさらに抑止することができる。
On the other hand, when the positive direction check valve V21 and the negative direction check valve V22 have a hydraulic pressure range in which neither of them opens, the movement of the hydraulic oil can be suppressed by the bidirectional check valve V2. Therefore, when the positive direction check valve V21 and the negative direction check valve V22 have a hydraulic pressure range in which neither of them opens, it is possible to reduce energy consumption for suppressing the movement of the hydraulic oil. Further, even when force is applied from the belt VT to the primary pulley PP and the secondary pulley SP, the threshold values are set so that neither the positive check valve V21 nor the negative check valve V22 is opened. If set, the above-described energy consumption can be further suppressed.
なお、双方向逆止弁V2は、車載油圧供給装置1において必須ではない。例えば、補助ポンプP2を、作動油の移動を抑止するために動作させる構成の場合には、車載油圧供給装置1は、双方向逆止弁V2を備えていなくてもよい。
In addition, the bidirectional check valve V2 is not essential in the in-vehicle hydraulic pressure supply device 1. For example, in the case of the configuration in which the auxiliary pump P2 is operated to suppress the movement of the hydraulic oil, the in-vehicle hydraulic pressure supply device 1 may not include the bidirectional check valve V2.
[油圧供給部40について]
[About hydraulic pressure supply unit 40]
油圧供給部40は、オイルパンOPと、主ポンプP1と、油圧センサPS1と、逆止弁V1と、逆止弁V3とを備えており、主ポンプP1によって加圧された作動油を閉油路10に供給する。
主ポンプP1は、油路501と、油路601との間に設けられており、オイルパンOPに貯留されている作動油を、油路501を介して吸い上げ、油路601に吐出する。つまり、主ポンプP1は、図中の矢印C方向に作動油を移動させる。以下の説明において、主ポンプP1が電動ポンプである例について説明するが、これに限られない。主ポンプP1は、制御ユニット30による制御に基づいて動作する。
逆止弁V3は、油路601と、油路602との間に設けられており、作動油を、図中の矢印C方向に通過させ、図中の矢印D方向に通過させない。この逆止弁V3により、主ポンプP1が停止しても、油路602の内部の作動油の油圧が保たれる。
油圧センサPS1は、油路602と、油路603との間に設けられており、油路602の内部の作動油の油圧を検出する。油圧センサPS1は、検出した圧力を制御ユニット30に出力する。 The hydraulicpressure supply unit 40 includes an oil pan OP, a main pump P1, a hydraulic pressure sensor PS1, a check valve V1, and a check valve V3, and closes hydraulic oil pressurized by the main pump P1. Supply to path 10.
The main pump P <b> 1 is provided between theoil passage 501 and the oil passage 601, sucks up the hydraulic oil stored in the oil pan OP through the oil passage 501, and discharges it to the oil passage 601. That is, the main pump P1 moves the hydraulic oil in the direction of arrow C in the drawing. In the following description, an example in which the main pump P1 is an electric pump will be described, but the present invention is not limited to this. The main pump P1 operates based on control by the control unit 30.
The check valve V3 is provided between theoil passage 601 and the oil passage 602, and allows hydraulic oil to pass in the direction of arrow C in the drawing and not in the direction of arrow D in the drawing. The check valve V3 maintains the hydraulic pressure of the hydraulic oil inside the oil passage 602 even when the main pump P1 is stopped.
The oil pressure sensor PS1 is provided between theoil passage 602 and the oil passage 603, and detects the hydraulic pressure of the hydraulic oil inside the oil passage 602. The hydraulic sensor PS1 outputs the detected pressure to the control unit 30.
主ポンプP1は、油路501と、油路601との間に設けられており、オイルパンOPに貯留されている作動油を、油路501を介して吸い上げ、油路601に吐出する。つまり、主ポンプP1は、図中の矢印C方向に作動油を移動させる。以下の説明において、主ポンプP1が電動ポンプである例について説明するが、これに限られない。主ポンプP1は、制御ユニット30による制御に基づいて動作する。
逆止弁V3は、油路601と、油路602との間に設けられており、作動油を、図中の矢印C方向に通過させ、図中の矢印D方向に通過させない。この逆止弁V3により、主ポンプP1が停止しても、油路602の内部の作動油の油圧が保たれる。
油圧センサPS1は、油路602と、油路603との間に設けられており、油路602の内部の作動油の油圧を検出する。油圧センサPS1は、検出した圧力を制御ユニット30に出力する。 The hydraulic
The main pump P <b> 1 is provided between the
The check valve V3 is provided between the
The oil pressure sensor PS1 is provided between the
逆止弁V1は、油路603と、閉油路10との間に設けられている。逆止弁V1は、逆止弁V11と、逆止弁V12とを備えている。逆止弁V11を、第一の逆止弁とも記載する。逆止弁V12を、第二の逆止弁とも記載する。
逆止弁V11は、油路603と、閉油路101との間に設けられており、作動油を、図中の矢印C1方向に通過させ、図中の矢印D1方向に通過させない。逆止弁V12は、油路603と、閉油路103との間に設けられており、作動油を、図中の矢印C2方向に通過させ、図中の矢印D2方向に通過させない。
なお、逆止弁V11は、油路603と、閉油路102との間に設けられていてもよい。
また、逆止弁V12は、油路603と、閉油路104との間に設けられていてもよい。
逆止弁V1は、主ポンプP1によって加圧された作動油を閉油路10に供給するとともに、閉油路10から油路603側に作動油が流れ込むことを抑止する。この逆止弁V1により、閉油路10の内部の作動油の油圧が、所定値以上に保たれる。 The check valve V <b> 1 is provided between theoil passage 603 and the oil closing passage 10. The check valve V1 includes a check valve V11 and a check valve V12. The check valve V11 is also referred to as a first check valve. The check valve V12 is also referred to as a second check valve.
The check valve V11 is provided between theoil passage 603 and the closed oil passage 101, and allows hydraulic oil to pass in the direction of arrow C1 in the drawing and not in the direction of arrow D1 in the drawing. The check valve V12 is provided between the oil passage 603 and the oil closing passage 103, and allows hydraulic oil to pass in the direction of arrow C2 in the drawing and not in the direction of arrow D2 in the drawing.
The check valve V <b> 11 may be provided between theoil passage 603 and the oil closing passage 102.
Further, the check valve V12 may be provided between theoil passage 603 and the oil closing passage 104.
The check valve V1 supplies the hydraulic oil pressurized by the main pump P1 to theclosed oil passage 10 and suppresses the hydraulic oil from flowing from the closed oil passage 10 to the oil passage 603 side. By this check valve V1, the hydraulic pressure of the hydraulic oil inside the closed oil passage 10 is maintained at a predetermined value or more.
逆止弁V11は、油路603と、閉油路101との間に設けられており、作動油を、図中の矢印C1方向に通過させ、図中の矢印D1方向に通過させない。逆止弁V12は、油路603と、閉油路103との間に設けられており、作動油を、図中の矢印C2方向に通過させ、図中の矢印D2方向に通過させない。
なお、逆止弁V11は、油路603と、閉油路102との間に設けられていてもよい。
また、逆止弁V12は、油路603と、閉油路104との間に設けられていてもよい。
逆止弁V1は、主ポンプP1によって加圧された作動油を閉油路10に供給するとともに、閉油路10から油路603側に作動油が流れ込むことを抑止する。この逆止弁V1により、閉油路10の内部の作動油の油圧が、所定値以上に保たれる。 The check valve V <b> 1 is provided between the
The check valve V11 is provided between the
The check valve V <b> 11 may be provided between the
Further, the check valve V12 may be provided between the
The check valve V1 supplies the hydraulic oil pressurized by the main pump P1 to the
なお、油圧供給部40は、アキュムレータACCを備えていてもよい。アキュムレータACCは、主ポンプP1が発生させた油圧が付された作動油を蓄える。油圧供給部40は、アキュムレータACCを備えることにより、主ポンプP1の動作による油圧の脈動やサージを低減することができる。また、油圧供給部40は、アキュムレータACCを備えることにより、主ポンプP1が停止している状態において作動油に圧力を付すことができる。
The hydraulic pressure supply unit 40 may include an accumulator ACC. The accumulator ACC stores hydraulic oil to which hydraulic pressure generated by the main pump P1 is attached. By providing the accumulator ACC, the hydraulic pressure supply unit 40 can reduce hydraulic pulsation and surge due to the operation of the main pump P1. Further, the hydraulic pressure supply unit 40 includes the accumulator ACC, and can apply pressure to the hydraulic oil in a state where the main pump P1 is stopped.
また、油圧供給部40は、逆止弁V4を備えていてもよい。この逆止弁V4は、油路603の内部の油圧がリリーフ圧を超える場合に、油路603の内部の作動油の一部を、油路502を介してオイルパンOPに排油する。つまり、逆止弁V4は、リリーフ弁として機能してもよい。油圧供給部40は、リリーフ弁を備えることにより、油路603の内部の油圧の異常上昇時に作動油を排油して、油圧を下げることができる。
なお、このリリーフ弁は、油路603の内部の作動油の油圧が、元圧の設定範囲よりも十分に高い場合に開弁する。換言すれば、このリリーフ弁は、元圧の設定範囲では開弁しない。つまり、このリリーフ弁は、油路603の内部の作動油の油圧が異常上昇した場合に開弁する。 The hydraulicpressure supply unit 40 may include a check valve V4. This check valve V4 discharges part of the hydraulic oil inside the oil passage 603 to the oil pan OP via the oil passage 502 when the oil pressure inside the oil passage 603 exceeds the relief pressure. That is, the check valve V4 may function as a relief valve. By providing the relief valve, the hydraulic pressure supply unit 40 can drain the hydraulic oil and reduce the hydraulic pressure when the hydraulic pressure inside the oil passage 603 rises abnormally.
This relief valve opens when the hydraulic pressure of the hydraulic oil inside theoil passage 603 is sufficiently higher than the set range of the original pressure. In other words, the relief valve does not open in the set range of the original pressure. That is, this relief valve opens when the hydraulic pressure of the hydraulic oil inside the oil passage 603 rises abnormally.
なお、このリリーフ弁は、油路603の内部の作動油の油圧が、元圧の設定範囲よりも十分に高い場合に開弁する。換言すれば、このリリーフ弁は、元圧の設定範囲では開弁しない。つまり、このリリーフ弁は、油路603の内部の作動油の油圧が異常上昇した場合に開弁する。 The hydraulic
This relief valve opens when the hydraulic pressure of the hydraulic oil inside the
なお、この逆止弁V4は、閉油路10に供給される作動油の油圧を、元圧の設定範囲内に調整するための圧力コントロール弁として機能してもよい。油圧供給部40は、圧力コントロール弁を備えることにより、主ポンプP1による油圧制御を精密に行わなくても、閉油路10に供給される作動油の油圧を、元圧の設定範囲内に調整することができる。
The check valve V4 may function as a pressure control valve for adjusting the hydraulic pressure of the hydraulic oil supplied to the closed oil passage 10 within the original pressure setting range. By providing a pressure control valve, the hydraulic pressure supply unit 40 adjusts the hydraulic pressure of the hydraulic oil supplied to the closed oil passage 10 within the set range of the original pressure without precisely controlling the hydraulic pressure by the main pump P1. can do.
[制御ユニット30について]
次に、図3を参照して、制御ユニット30の機能構成について説明する。
図3は、本実施形態の制御ユニット30の機能構成の一例を示すブロック図である。制御ユニット30は、制御部301と、主ポンプ駆動回路302と、補助ポンプ駆動回路303とを備えている。制御ユニット30は、その入力側が、上位ユニット2と、油圧センサPS1と、位置検出センサ201と、油圧センサPS2とに接続されている。また、制御ユニット30は、その出力側が、主ポンプP1と、補助ポンプP2とに接続されている。 [About the control unit 30]
Next, the functional configuration of thecontrol unit 30 will be described with reference to FIG.
FIG. 3 is a block diagram illustrating an example of a functional configuration of thecontrol unit 30 of the present embodiment. The control unit 30 includes a control unit 301, a main pump drive circuit 302, and an auxiliary pump drive circuit 303. The input side of the control unit 30 is connected to the host unit 2, the hydraulic sensor PS1, the position detection sensor 201, and the hydraulic sensor PS2. Moreover, the output side of the control unit 30 is connected to the main pump P1 and the auxiliary pump P2.
次に、図3を参照して、制御ユニット30の機能構成について説明する。
図3は、本実施形態の制御ユニット30の機能構成の一例を示すブロック図である。制御ユニット30は、制御部301と、主ポンプ駆動回路302と、補助ポンプ駆動回路303とを備えている。制御ユニット30は、その入力側が、上位ユニット2と、油圧センサPS1と、位置検出センサ201と、油圧センサPS2とに接続されている。また、制御ユニット30は、その出力側が、主ポンプP1と、補助ポンプP2とに接続されている。 [About the control unit 30]
Next, the functional configuration of the
FIG. 3 is a block diagram illustrating an example of a functional configuration of the
制御ユニット30は、無段階変速装置3の変速指令を、上位ユニット2から取得する。この変速指令には、変速比の目標値と、変速に要する時間の目標値とが含まれている。「変速比の目標値」を、「目標変速比」とも記載する。「変速に要する時間の目標値」を、「目標変速時間」とも記載する。
また、制御ユニット30は、油圧センサPS1が検出した油路602の内部の作動油の油圧を示す情報を、油圧センサPS1から取得する。「油圧センサPS1が検出した油圧」を、「元圧実測値」とも記載する。「元圧実測値を示す情報」を、「元圧情報」とも記載する。
また、制御ユニット30は、位置検出センサ201が検出した可動側プーリの幅方向の位置を示す情報を、位置検出センサ201から取得する。「位置検出センサ201が出力する可動側プーリの幅方向の位置を示す情報」を、単に「位置情報」とも記載する。
また、制御ユニット30は、油圧センサPS2が検出した閉油路10の内部の作動油の油圧を示す情報を、油圧センサPS2から取得する。「油圧センサPS2が検出した油圧」を、「閉油路油圧実測値」とも記載する。「油圧センサPS2が出力する閉油路油圧実測値を示す情報」を、「閉油路油圧情報」とも記載する。 Thecontrol unit 30 acquires a shift command for the continuously variable transmission 3 from the host unit 2. This shift command includes a target value for the gear ratio and a target value for the time required for the shift. “Target speed ratio value” is also referred to as “target speed ratio”. The “target value of time required for shifting” is also referred to as “target shifting time”.
In addition, thecontrol unit 30 acquires information indicating the hydraulic pressure of the hydraulic oil inside the oil passage 602 detected by the hydraulic sensor PS1 from the hydraulic sensor PS1. “Hydraulic pressure detected by the hydraulic pressure sensor PS1” is also referred to as “original pressure actual measurement value”. “Information indicating actual measured actual pressure” is also referred to as “original pressure information”.
Further, thecontrol unit 30 acquires information indicating the position in the width direction of the movable pulley detected by the position detection sensor 201 from the position detection sensor 201. “Information indicating the position in the width direction of the movable pulley output from the position detection sensor 201” is also simply referred to as “position information”.
Further, thecontrol unit 30 acquires information indicating the hydraulic pressure of the hydraulic oil inside the closed oil passage 10 detected by the hydraulic sensor PS2 from the hydraulic sensor PS2. The “hydraulic pressure detected by the hydraulic pressure sensor PS2” is also referred to as “actually measured oil pressure on the closed path”. “Information indicating the actual oil pressure value of the closed oil path output from the oil pressure sensor PS2” is also referred to as “oil pressure information of the oil path”.
また、制御ユニット30は、油圧センサPS1が検出した油路602の内部の作動油の油圧を示す情報を、油圧センサPS1から取得する。「油圧センサPS1が検出した油圧」を、「元圧実測値」とも記載する。「元圧実測値を示す情報」を、「元圧情報」とも記載する。
また、制御ユニット30は、位置検出センサ201が検出した可動側プーリの幅方向の位置を示す情報を、位置検出センサ201から取得する。「位置検出センサ201が出力する可動側プーリの幅方向の位置を示す情報」を、単に「位置情報」とも記載する。
また、制御ユニット30は、油圧センサPS2が検出した閉油路10の内部の作動油の油圧を示す情報を、油圧センサPS2から取得する。「油圧センサPS2が検出した油圧」を、「閉油路油圧実測値」とも記載する。「油圧センサPS2が出力する閉油路油圧実測値を示す情報」を、「閉油路油圧情報」とも記載する。 The
In addition, the
Further, the
Further, the
制御部301は、CPU(Central Processing Unit)を備えており、主ポンプ制御部311と、補助ポンプ制御部312と、故障検出部313とを、その機能部として備えている。
The control unit 301 includes a CPU (Central Processing Unit), and includes a main pump control unit 311, an auxiliary pump control unit 312, and a failure detection unit 313 as functional units.
[主ポンプP1の制御]
主ポンプ制御部311は、上位ユニット2から取得した変速指令と、油圧センサPS1から取得した元圧情報とに基づいて、主ポンプP1の制御を行なう。図4を参照して、制御部301による主ポンプP1の制御について説明する。 [Control of main pump P1]
The mainpump control unit 311 controls the main pump P1 based on the shift command acquired from the host unit 2 and the original pressure information acquired from the hydraulic sensor PS1. With reference to FIG. 4, the control of the main pump P1 by the control unit 301 will be described.
主ポンプ制御部311は、上位ユニット2から取得した変速指令と、油圧センサPS1から取得した元圧情報とに基づいて、主ポンプP1の制御を行なう。図4を参照して、制御部301による主ポンプP1の制御について説明する。 [Control of main pump P1]
The main
図4は、本実施形態の主ポンプP1の制御の流れの一例を示す流れ図である。主ポンプ制御部311は、上位ユニット2からの変速指令の有無を判定し(ステップS10)、変速指令ありと判定した場合(ステップS10;YES)には、処理をステップS20に進める。主ポンプ制御部311は、変速指令なしと判定した場合(ステップS10;NO)には、処理をステップS10に戻して、変速指令を待つ。
FIG. 4 is a flowchart showing an example of a control flow of the main pump P1 of the present embodiment. The main pump control unit 311 determines whether or not there is a shift command from the host unit 2 (step S10). If it is determined that there is a shift command (step S10; YES), the process proceeds to step S20. If it is determined that there is no shift command (step S10; NO), the main pump control unit 311 returns the process to step S10 and waits for the shift command.
主ポンプ制御部311は、油路602の内部の作動油の目標圧力を算出する(ステップS20)。この油路602の内部の作動油の目標圧力を、元圧目標値とも記載する。ここで、元圧目標値は、変速指令に含まれる目標変速比や目標変速時間などによって予め定められている。例えば、現在の変速比と目標変速比との差が比較的大きい場合や、目標変速時間が比較的短い場合には、元圧目標値が高めに定められている。すなわち、プーリ幅を大きく変化させる場合や、プーリ幅を速やかに変化させる場合には、元圧目標値が高めに定められている。主ポンプ制御部311は、この予め定められている元圧目標値の条件と、変速指令に含まれる目標変速比や目標変速時間とに基づいて、元圧目標値を算出する。
The main pump control unit 311 calculates the target pressure of the hydraulic oil inside the oil passage 602 (step S20). The target pressure of hydraulic oil inside the oil passage 602 is also referred to as a source pressure target value. Here, the original pressure target value is determined in advance by a target speed ratio, a target speed change time, etc. included in the speed change command. For example, when the difference between the current speed change ratio and the target speed change ratio is relatively large, or when the target speed change time is relatively short, the original pressure target value is set higher. That is, when the pulley width is changed greatly or when the pulley width is changed quickly, the original pressure target value is set to be high. The main pump control unit 311 calculates the source pressure target value based on the predetermined source pressure target value condition and the target gear ratio and target shift time included in the shift command.
主ポンプ制御部311は、油圧センサPS1から元圧情報を取得する(ステップS30)。この元圧情報は、油圧センサPS1が検出した元圧実測値を示している。
The main pump control unit 311 acquires the original pressure information from the hydraulic pressure sensor PS1 (step S30). This source pressure information indicates the actual measured actual pressure value detected by the hydraulic sensor PS1.
次に、主ポンプ制御部311は、ステップS20で算出した元圧目標値と、ステップS30で取得した元圧情報が示す元圧実測値とを比較する(ステップS40)。主ポンプ制御部311は、元圧実測値が元圧目標値に到達していないと判定した場合(ステップS40;NO)には、主ポンプP1を駆動し(ステップS50)、処理をステップS30に戻す。主ポンプ制御部311は、元圧実測値が元圧目標値に到達していると判定した場合(ステップS40;YES)には、主ポンプP1を停止する(ステップS60)。
Next, the main pump control unit 311 compares the original pressure target value calculated in Step S20 with the actual measured actual pressure indicated by the original pressure information acquired in Step S30 (Step S40). If the main pump control unit 311 determines that the actual measured pressure value has not reached the target target pressure value (step S40; NO), the main pump P1 is driven (step S50), and the process proceeds to step S30. return. When the main pump control unit 311 determines that the actual measured actual pressure value has reached the original target pressure value (step S40; YES), the main pump control unit 311 stops the main pump P1 (step S60).
具体的には、図3に示すように、主ポンプ制御部311は、主ポンプ駆動回路302に、主ポンプP1の駆動信号sig1を出力する。主ポンプ駆動回路302は、インバータなどの電流出力回路を備えており、駆動信号sig1に基づいて、駆動電流I1を主ポンプP1に対して出力する。主ポンプP1は、駆動電流I1が供給されると、図1に示す矢印C方向に作動油を吐出する。また、主ポンプP1は、駆動電流I1の供給が停止されると、作動油の吐出を停止する。
Specifically, as shown in FIG. 3, the main pump control unit 311 outputs a drive signal sig1 of the main pump P1 to the main pump drive circuit 302. The main pump drive circuit 302 includes a current output circuit such as an inverter, and outputs a drive current I1 to the main pump P1 based on the drive signal sig1. When the drive current I1 is supplied, the main pump P1 discharges hydraulic oil in the direction of arrow C shown in FIG. Further, the main pump P1 stops discharging the hydraulic oil when the supply of the drive current I1 is stopped.
なお、主ポンプ制御部311は、上位ユニット2が出力する変速指令を待たずに、油圧センサPS1から取得した元圧情報に基づいて、主ポンプP1の駆動制御を行なってもよい。すなわち、上述したステップS10は、省略されてもよい。
The main pump control unit 311 may perform drive control of the main pump P1 based on the original pressure information acquired from the hydraulic sensor PS1 without waiting for a shift command output from the host unit 2. That is, step S10 described above may be omitted.
[補助ポンプP2の制御]
補助ポンプ制御部312は、変速指令と、位置情報とに基づいて、補助ポンプP2の駆動制御を行なう。図5を参照して補助ポンプ制御部312による補助ポンプP2の制御について説明する。 [Control of auxiliary pump P2]
The auxiliarypump control unit 312 performs drive control of the auxiliary pump P2 based on the shift command and the position information. The control of the auxiliary pump P2 by the auxiliary pump control unit 312 will be described with reference to FIG.
補助ポンプ制御部312は、変速指令と、位置情報とに基づいて、補助ポンプP2の駆動制御を行なう。図5を参照して補助ポンプ制御部312による補助ポンプP2の制御について説明する。 [Control of auxiliary pump P2]
The auxiliary
図5は、本実施形態の補助ポンプP2の制御の流れの一例を示す流れ図である。補助ポンプ制御部312は、上位ユニット2からの変速指令の有無を判定し(ステップS100)、変速指令ありと判定した場合(ステップS100;YES)には、処理をステップS110に進める。補助ポンプ制御部312は、変速指令なしと判定した場合(ステップS100;NO)には、処理をステップS100に戻して、変速指令を待つ。
FIG. 5 is a flowchart showing an example of a control flow of the auxiliary pump P2 of the present embodiment. The auxiliary pump control unit 312 determines whether or not there is a shift command from the host unit 2 (step S100). If it is determined that there is a shift command (step S100; YES), the process proceeds to step S110. If the auxiliary pump control unit 312 determines that there is no shift command (step S100; NO), the process returns to step S100 and waits for a shift command.
補助ポンプ制御部312は、位置検出センサ201から、位置情報を取得する(ステップS110)。ここでは、位置検出センサ201は、セカンダリプーリSPのプーリ幅を検出するものであって、セカンダリプーリSPのプーリ幅を示す位置情報を出力するものとして説明する。以下の説明においては、位置検出センサ201が出力する位置情報を、「セカンダリプーリSPの現在幅」、又は単に「現在幅」とも記載する。つまり、ステップS110において、補助ポンプ制御部312は、位置検出センサ201から、セカンダリプーリSPの現在幅を取得する。
The auxiliary pump control unit 312 acquires position information from the position detection sensor 201 (step S110). Here, the position detection sensor 201 is described as detecting the pulley width of the secondary pulley SP and outputting position information indicating the pulley width of the secondary pulley SP. In the following description, the position information output by the position detection sensor 201 is also referred to as “current width of secondary pulley SP” or simply “current width”. That is, in step S110, the auxiliary pump control unit 312 acquires the current width of the secondary pulley SP from the position detection sensor 201.
補助ポンプ制御部312は、ステップS100で取得した変速指令に含まれる目標変速比に基づいて、セカンダリプーリSPの目標幅を算出する(ステップS120)。
The auxiliary pump control unit 312 calculates the target width of the secondary pulley SP based on the target speed ratio included in the speed change command acquired in Step S100 (Step S120).
次に、補助ポンプ制御部312は、ステップS110で取得したセカンダリプーリSPの現在幅と、ステップS120で算出した目標幅とに基づいて、セカンダリプーリSPの変化幅を算出する。また、補助ポンプ制御部312は、算出したセカンダリプーリSPの変化幅と、ステップS100で取得した変速指令に含まれる目標変速時間とに基づいて、補助ポンプP2の回転方向と回転数とを算出する(ステップS130)。
Next, the auxiliary pump control unit 312 calculates the change width of the secondary pulley SP based on the current width of the secondary pulley SP acquired in step S110 and the target width calculated in step S120. Further, the auxiliary pump control unit 312 calculates the rotation direction and the rotation speed of the auxiliary pump P2 based on the calculated change width of the secondary pulley SP and the target shift time included in the shift command acquired in step S100. (Step S130).
ここで、プーリ幅が広がるのか、狭まるのかは、閉油路10の内部の作動油の移動方向によって決まる。つまり、プーリ幅の変化の方向は、補助ポンプP2の回転方向によって決まる。補助ポンプ制御部312は、セカンダリプーリSPの現在幅が、目標幅よりも狭い場合には、プーリ幅を広げる方向に補助ポンプP2の回転方向を定める。また、補助ポンプ制御部312は、セカンダリプーリSPの現在幅が、目標幅よりも広い場合には、プーリ幅を狭める方向に補助ポンプP2の回転方向を定める。
また、プーリ幅の変化速度は、閉油路10の内部の作動油の移動速度によって、すなわち、補助ポンプP2の回転速度によって決まる。補助ポンプ制御部312は、プーリ幅の目標変速時間が短い場合には、長い場合に比べて補助ポンプP2がより高速に回転するように回転数を定める。 Here, whether the pulley width is widened or narrowed depends on the moving direction of the hydraulic oil inside theclosed oil passage 10. That is, the direction of change of the pulley width is determined by the rotation direction of the auxiliary pump P2. When the current width of the secondary pulley SP is narrower than the target width, the auxiliary pump control unit 312 determines the rotation direction of the auxiliary pump P2 in the direction of increasing the pulley width. In addition, when the current width of the secondary pulley SP is wider than the target width, the auxiliary pump control unit 312 determines the rotation direction of the auxiliary pump P2 in the direction of narrowing the pulley width.
Further, the pulley width changing speed is determined by the moving speed of the hydraulic oil inside theclosed oil passage 10, that is, the rotational speed of the auxiliary pump P2. The auxiliary pump control unit 312 determines the rotation speed so that the auxiliary pump P2 rotates at a higher speed when the target speed change time of the pulley width is shorter than when it is longer.
また、プーリ幅の変化速度は、閉油路10の内部の作動油の移動速度によって、すなわち、補助ポンプP2の回転速度によって決まる。補助ポンプ制御部312は、プーリ幅の目標変速時間が短い場合には、長い場合に比べて補助ポンプP2がより高速に回転するように回転数を定める。 Here, whether the pulley width is widened or narrowed depends on the moving direction of the hydraulic oil inside the
Further, the pulley width changing speed is determined by the moving speed of the hydraulic oil inside the
次に、補助ポンプ制御部312は、ステップS130で算出した補助ポンプP2の回転方向及び回転数に基づいて、補助ポンプP2を駆動する(ステップS140)。具体的には、図3に示すように、補助ポンプ制御部312は、補助ポンプ駆動回路303に、補助ポンプP2の駆動信号sig2を出力する。補助ポンプ駆動回路303は、インバータなどの電流出力回路を備えており、駆動信号sig2に基づいて、駆動電流I2を補助ポンプP2に対して出力する。補助ポンプP2は、駆動電流I2が供給されると、駆動電流I2に基づく回転方向及び回転数によって作動油を正方向又は負方向に移動させる。
Next, the auxiliary pump control unit 312 drives the auxiliary pump P2 based on the rotation direction and the rotation speed of the auxiliary pump P2 calculated in step S130 (step S140). Specifically, as shown in FIG. 3, the auxiliary pump control unit 312 outputs a drive signal sig <b> 2 of the auxiliary pump P <b> 2 to the auxiliary pump drive circuit 303. The auxiliary pump drive circuit 303 includes a current output circuit such as an inverter, and outputs a drive current I2 to the auxiliary pump P2 based on the drive signal sig2. When the drive current I2 is supplied, the auxiliary pump P2 moves the hydraulic oil in the positive direction or the negative direction depending on the rotation direction and the rotation speed based on the drive current I2.
図5に戻り、補助ポンプ制御部312は、位置検出センサ201から、位置情報を取得し(ステップS150)、プーリ幅が目標幅に到達したか否かを判定する(ステップS160)。補助ポンプ制御部312は、プーリ幅が目標幅に到達していないと判定した場合(ステップS160;NO)には、処理をステップS140に戻し、補助ポンプP2の駆動を継続する。一方、補助ポンプ制御部312は、プーリ幅が目標幅に到達したと判定した場合(ステップS160;YES)には、補助ポンプP2の駆動を停止する(ステップS170)。この際に、故障検出部313は、故障検知処理(ステップS210~ステップS250)を行う。
5, the auxiliary pump control unit 312 acquires position information from the position detection sensor 201 (step S150), and determines whether or not the pulley width has reached the target width (step S160). When determining that the pulley width has not reached the target width (step S160; NO), the auxiliary pump control unit 312 returns the process to step S140 and continues driving the auxiliary pump P2. On the other hand, when it is determined that the pulley width has reached the target width (step S160; YES), the auxiliary pump control unit 312 stops driving the auxiliary pump P2 (step S170). At this time, the failure detection unit 313 performs failure detection processing (steps S210 to S250).
[故障検知処理]
図6は、本実施形態の故障検出処理の流れの一例を示す流れ図である。故障検出部313は、ステップS150で補助ポンプ制御部312が取得した位置情報に基づいて、セカンダリプーリSPのプーリ幅の変化の速度を算出する(ステップS210)。
次に、故障検出部313は、油圧センサPS2から、閉油路10の油圧を示す閉油路油圧情報を取得する(ステップS220)。
次に、故障検出部313は、ステップS210で算出したプーリ幅の変化速度と、ステップS220で取得した閉油路油圧情報とに基づいて、プーリ幅の変化速度と閉油路油圧との関係が適切であるか否かを判定する(ステップS230)。ここで、プーリ幅の変化速度と、閉油路油圧との間には、所定の関係がある。具体的には、プーリ幅の変化速度が速い場合には、閉油路油圧は、高い値になる。また、プーリ幅の変化速度が遅い場合には、閉油路油圧は、低い値になる。したがって、プーリ幅の変化速度が比較的遅いにもかかわらず、閉油路油圧が基準値よりも高い場合には、閉油路10の詰まりや、位置検出センサ201の誤動作などの故障が発生している可能性があると判定することができる。
故障検出部313は、プーリ幅の変化速度と閉油路油圧との関係が適切であると判定した場合(ステップS230;YES)には、上位ユニット2に対して「故障無し」を通知する(ステップS240)。一方、故障検出部313は、プーリ幅の変化速度と閉油路油圧との関係が適切でないと判定した場合(ステップS230;NO)には、上位ユニット2に対して「故障あり」を通知する(ステップS250)。 [Failure detection processing]
FIG. 6 is a flowchart illustrating an example of the flow of failure detection processing according to the present embodiment. Thefailure detection unit 313 calculates the speed of change of the pulley width of the secondary pulley SP based on the position information acquired by the auxiliary pump control unit 312 in step S150 (step S210).
Next, thefailure detection unit 313 acquires closed-path hydraulic pressure information indicating the hydraulic pressure of the closed-path 10 from the hydraulic pressure sensor PS2 (step S220).
Next, thefailure detection unit 313 determines that the relationship between the change speed of the pulley width and the oil pressure of the closed path is based on the speed of change of the pulley width calculated in step S210 and the oil pressure information of the closed oil path acquired in step S220. It is determined whether or not it is appropriate (step S230). Here, there is a predetermined relationship between the change speed of the pulley width and the oil pressure of the closed passage. Specifically, when the change speed of the pulley width is fast, the oil closing passage hydraulic pressure becomes a high value. In addition, when the change speed of the pulley width is low, the oil pressure in the closed oil passage becomes a low value. Therefore, when the oil pressure of the closed oil passage is higher than the reference value even though the changing speed of the pulley width is relatively slow, a failure such as clogging of the oil passage 10 or malfunction of the position detection sensor 201 occurs. It can be determined that there is a possibility of being.
If thefailure detection unit 313 determines that the relationship between the change speed of the pulley width and the oil pressure in the closed oil passage is appropriate (step S230; YES), the failure detection unit 313 notifies the upper unit 2 of “no failure” ( Step S240). On the other hand, if the failure detection unit 313 determines that the relationship between the change speed of the pulley width and the oil pressure in the closed passage is not appropriate (step S230; NO), the failure detection unit 313 notifies the upper unit 2 of “There is a failure”. (Step S250).
図6は、本実施形態の故障検出処理の流れの一例を示す流れ図である。故障検出部313は、ステップS150で補助ポンプ制御部312が取得した位置情報に基づいて、セカンダリプーリSPのプーリ幅の変化の速度を算出する(ステップS210)。
次に、故障検出部313は、油圧センサPS2から、閉油路10の油圧を示す閉油路油圧情報を取得する(ステップS220)。
次に、故障検出部313は、ステップS210で算出したプーリ幅の変化速度と、ステップS220で取得した閉油路油圧情報とに基づいて、プーリ幅の変化速度と閉油路油圧との関係が適切であるか否かを判定する(ステップS230)。ここで、プーリ幅の変化速度と、閉油路油圧との間には、所定の関係がある。具体的には、プーリ幅の変化速度が速い場合には、閉油路油圧は、高い値になる。また、プーリ幅の変化速度が遅い場合には、閉油路油圧は、低い値になる。したがって、プーリ幅の変化速度が比較的遅いにもかかわらず、閉油路油圧が基準値よりも高い場合には、閉油路10の詰まりや、位置検出センサ201の誤動作などの故障が発生している可能性があると判定することができる。
故障検出部313は、プーリ幅の変化速度と閉油路油圧との関係が適切であると判定した場合(ステップS230;YES)には、上位ユニット2に対して「故障無し」を通知する(ステップS240)。一方、故障検出部313は、プーリ幅の変化速度と閉油路油圧との関係が適切でないと判定した場合(ステップS230;NO)には、上位ユニット2に対して「故障あり」を通知する(ステップS250)。 [Failure detection processing]
FIG. 6 is a flowchart illustrating an example of the flow of failure detection processing according to the present embodiment. The
Next, the
Next, the
If the
上位ユニット2は、故障ありと通知された場合には、車載油圧供給装置1や、無段階変速装置3が正常に動作しないと判定して、例えば、変速比を変化させずに固定する制御などの故障発生時制御を行なうことができる。
When the host unit 2 is notified that there is a failure, it determines that the in-vehicle hydraulic pressure supply device 1 or the continuously variable transmission 3 does not operate normally, for example, a control for fixing without changing the gear ratio, etc. It is possible to control when a failure occurs.
なお、補助ポンプ制御部312は、油圧センサPS2が検出する閉油路油圧に基づいて、補助ポンプP2を制御してもよい。具体的には、油圧センサPS2が位置検出センサ201よりも壊れにくい場合がある。この場合には、位置検出センサ201の検出値と、油圧センサPS2の検出値との関係が適切ではない場合、すなわち、故障検出部313が故障ありと判定した場合に、油圧センサPS2の検出値を信頼して制御してもよい。この場合、補助ポンプ制御部312は、故障検出部313が故障ありと判定した場合に、油圧センサPS2が検出する閉油路油圧に基づいて、補助ポンプP2を制御する。このように構成することにより、車載油圧供給装置1は、位置検出センサ201に故障が生じた場合であっても、変速比を変化させることができる。
In addition, the auxiliary pump control unit 312 may control the auxiliary pump P2 based on the oil pressure of the closed passage detected by the hydraulic sensor PS2. Specifically, the hydraulic pressure sensor PS2 may be more difficult to break than the position detection sensor 201. In this case, when the relationship between the detection value of the position detection sensor 201 and the detection value of the hydraulic sensor PS2 is not appropriate, that is, when the failure detection unit 313 determines that there is a failure, the detection value of the hydraulic sensor PS2 May be controlled with confidence. In this case, when the failure detection unit 313 determines that there is a failure, the auxiliary pump control unit 312 controls the auxiliary pump P2 based on the closed-path hydraulic pressure detected by the hydraulic sensor PS2. With this configuration, the in-vehicle hydraulic pressure supply device 1 can change the gear ratio even when the position detection sensor 201 has a failure.
以上説明したように、本実施形態の車載油圧供給装置1は、圧力コントロール弁等の作動油を排油する機構を備えることなく、元圧を制御する。仮に、圧力コントロール弁等の作動油を排油する機構を備えている構成であるとすると、主ポンプP1によって元圧以上に加圧された作動油を、圧力制御のためにオイルパン等に排油する。このような圧力コントロール弁を備える構成では、元圧以上に作動油を加圧するため、主ポンプP1が大型のものになる。また、このような構成の場合、いったん元圧以上に加圧した作動油を、その圧力を利用することなく排油するため、主ポンプP1の消費エネルギーの一部が無駄になる。
本実施形態の車載油圧供給装置1によれば、作動油を排油することなく元圧を制御するため、主ポンプP1を小型化することができるとともに、主ポンプP1の消費エネルギーを低減することができる。なお、車載油圧供給装置1は、油圧センサPS1による圧力フィードバックによって主ポンプP1を駆動するため、元圧を精密に制御することができる。 As described above, the in-vehicle hydraulicpressure supply device 1 of the present embodiment controls the original pressure without providing a mechanism for draining hydraulic oil such as a pressure control valve. Assuming that the mechanism is provided with a mechanism for draining hydraulic oil such as a pressure control valve, the hydraulic oil pressurized by the main pump P1 to a pressure higher than the original pressure is discharged to an oil pan or the like for pressure control. Oil. In the configuration including such a pressure control valve, the hydraulic pump is pressurized to a pressure higher than the original pressure, so that the main pump P1 is large. Further, in the case of such a configuration, the hydraulic oil once pressurized to the original pressure or higher is discharged without using the pressure, so that a part of the energy consumed by the main pump P1 is wasted.
According to the in-vehicle hydraulicpressure supply device 1 of the present embodiment, the main pump P1 can be reduced in size and the energy consumption of the main pump P1 can be reduced because the main pressure is controlled without draining the hydraulic oil. Can do. In addition, since the vehicle-mounted hydraulic pressure supply device 1 drives the main pump P1 by pressure feedback by the hydraulic pressure sensor PS1, it is possible to precisely control the original pressure.
本実施形態の車載油圧供給装置1によれば、作動油を排油することなく元圧を制御するため、主ポンプP1を小型化することができるとともに、主ポンプP1の消費エネルギーを低減することができる。なお、車載油圧供給装置1は、油圧センサPS1による圧力フィードバックによって主ポンプP1を駆動するため、元圧を精密に制御することができる。 As described above, the in-vehicle hydraulic
According to the in-vehicle hydraulic
また、油圧供給部40から閉油路10に供給された油圧が低下した場合には、主ポンプP1を駆動することにより、低下した分の油圧を補う。したがって、閉油路10から作動油を排油する構成の場合には、排油される度に閉油路10の油圧が低下し、低下した分の油圧を補うために、主ポンプP1が駆動される。一方、本実施形態の車載油圧供給装置1は、閉油路10から作動油を排油する機構を備えていない。したがって、車載油圧供給装置1によれば、主ポンプP1の駆動頻度を低減することができるため、主ポンプP1の消費エネルギーを低減することができる。
Further, when the hydraulic pressure supplied from the hydraulic pressure supply unit 40 to the closed oil passage 10 decreases, the reduced hydraulic pressure is compensated by driving the main pump P1. Therefore, in the case of the configuration in which the hydraulic oil is drained from the closed oil passage 10, the oil pressure of the oil closing passage 10 decreases each time the oil is discharged, and the main pump P1 is driven to compensate for the reduced oil pressure. Is done. On the other hand, the in-vehicle hydraulic pressure supply device 1 of the present embodiment does not include a mechanism that drains hydraulic oil from the closed oil passage 10. Therefore, according to the in-vehicle hydraulic pressure supply device 1, since the driving frequency of the main pump P1 can be reduced, the energy consumption of the main pump P1 can be reduced.
また、本実施形態の車載油圧供給装置1は、閉油路10と、主ポンプP1との間に逆止弁V1が設けられている。この逆止弁V1は、閉油路10の作動油が油圧供給部40に逆流することを抑止する。このため、車載油圧供給装置1によれば、油圧供給部40側の油圧が、閉油路10内の油圧よりも低くなった場合でも、閉油路10内の油圧の低下を抑止することができる。これにより、車載油圧供給装置1は、主ポンプP1が動作していなくても、閉油路10内の油圧を維持することができる。つまり、車載油圧供給装置1は、逆止弁V1を備えることにより、主ポンプP1の駆動頻度を低減することができるため、主
ポンプP1の消費エネルギーを低減することができる。 Further, in the on-vehicle hydraulicpressure supply device 1 of the present embodiment, a check valve V1 is provided between the oil closing passage 10 and the main pump P1. The check valve V <b> 1 prevents the hydraulic oil in the closed oil passage 10 from flowing back to the hydraulic pressure supply unit 40. For this reason, according to the in-vehicle hydraulic pressure supply device 1, even when the hydraulic pressure on the hydraulic pressure supply unit 40 side becomes lower than the hydraulic pressure in the closed oil passage 10, it is possible to suppress a decrease in the hydraulic pressure in the closed oil passage 10. it can. Thereby, the vehicle-mounted hydraulic pressure supply device 1 can maintain the hydraulic pressure in the closed oil passage 10 even when the main pump P1 is not operating. That is, the vehicle-mounted hydraulic pressure supply device 1 can reduce the driving frequency of the main pump P1 by providing the check valve V1, and therefore can reduce the energy consumption of the main pump P1.
ポンプP1の消費エネルギーを低減することができる。 Further, in the on-vehicle hydraulic
また、本実施形態の車載油圧供給装置1は、プライマリプーリPPとセカンダリプーリSPとの間の作動油の移動を、閉油路10から作動油を排油することなく、補助ポンプP2によって作動油の圧力を制御することにより行う。ここで、仮に、圧力コントロール弁等により閉油路10から作動油を排油することによって、作動油の圧力を制御する構成であるとすると、圧力制御のために作動油をオイルパン等に排油する。このような圧力コントロール弁を備える構成では、作動油の移動に必要な圧力以上に作動油を加圧するため、補助ポンプP2が大型のものになる。また、このような構成の場合、いったん加圧した作動油を、その圧力を利用することなく排油するため、補助ポンプP2の消費エネルギーの一部が無駄になる。
本実施形態の車載油圧供給装置1によれば、作動油を排油することなくプライマリプーリPPとセカンダリプーリSPとの間の作動油の移動を制御する。このため車載油圧供給装置1によれば、補助ポンプP2を小型化することができるとともに、補助ポンプP2の消費エネルギーを低減することができる。なお、車載油圧供給装置1は、入力される変速指令と、プーリ幅検出部20によるプーリ幅の状態の検出結果とに基づいて、補助ポンプP2を駆動するため、プーリ幅を精密に制御することができる。 Moreover, the vehicle-mounted hydraulicpressure supply device 1 of the present embodiment allows the hydraulic oil to move between the primary pulley PP and the secondary pulley SP without the hydraulic oil being drained from the closed oil passage 10 by the auxiliary pump P2. This is done by controlling the pressure. Here, assuming that the pressure of the hydraulic oil is controlled by draining the hydraulic oil from the closed oil passage 10 by a pressure control valve or the like, the hydraulic oil is discharged to an oil pan or the like for pressure control. Oil. In the configuration including such a pressure control valve, the auxiliary pump P2 becomes large because the hydraulic oil is pressurized beyond the pressure necessary for the movement of the hydraulic oil. Further, in such a configuration, the hydraulic oil once pressurized is drained without using the pressure, and thus a part of the energy consumed by the auxiliary pump P2 is wasted.
According to the in-vehicle hydraulicpressure supply device 1 of the present embodiment, the movement of hydraulic oil between the primary pulley PP and the secondary pulley SP is controlled without draining the hydraulic oil. For this reason, according to the vehicle-mounted hydraulic pressure supply device 1, the auxiliary pump P2 can be reduced in size, and the energy consumption of the auxiliary pump P2 can be reduced. The in-vehicle hydraulic pressure supply device 1 drives the auxiliary pump P2 on the basis of the input shift command and the detection result of the pulley width state by the pulley width detector 20, and therefore precisely controls the pulley width. Can do.
本実施形態の車載油圧供給装置1によれば、作動油を排油することなくプライマリプーリPPとセカンダリプーリSPとの間の作動油の移動を制御する。このため車載油圧供給装置1によれば、補助ポンプP2を小型化することができるとともに、補助ポンプP2の消費エネルギーを低減することができる。なお、車載油圧供給装置1は、入力される変速指令と、プーリ幅検出部20によるプーリ幅の状態の検出結果とに基づいて、補助ポンプP2を駆動するため、プーリ幅を精密に制御することができる。 Moreover, the vehicle-mounted hydraulic
According to the in-vehicle hydraulic
また、本実施形態の車載油圧供給装置1は、第一の逆止弁及び第二の逆止弁の、2つの逆止弁V1を備えている。具体的には、車載油圧供給装置1は、プライマリプーリPPと補助ポンプP2との間の閉油路10に対して、逆止弁V11を備えている。また、車載油圧供給装置1は、セカンダリプーリSPと補助ポンプP2との間の閉油路10に対して、主ポンプP1からの油圧を供給する逆止弁V12を備えている。つまり、車載油圧供給装置1は、補助ポンプP2と2つのプーリとの間に、それぞれ元圧を供給する機構を備えている。このため、車載油圧供給装置1は、補助ポンプP2と2つのプーリとの間に、均一な元圧を加えることができるため、プーリ幅を精密に制御することができる。
Moreover, the vehicle-mounted hydraulic pressure supply device 1 of the present embodiment includes two check valves V1, that is, a first check valve and a second check valve. Specifically, the in-vehicle hydraulic pressure supply device 1 includes a check valve V11 with respect to the oil closing passage 10 between the primary pulley PP and the auxiliary pump P2. Moreover, the vehicle-mounted hydraulic pressure supply device 1 includes a check valve V12 that supplies hydraulic pressure from the main pump P1 to the closed oil passage 10 between the secondary pulley SP and the auxiliary pump P2. That is, the in-vehicle hydraulic pressure supply device 1 includes a mechanism for supplying a source pressure between the auxiliary pump P2 and the two pulleys. For this reason, since the vehicle-mounted hydraulic pressure supply device 1 can apply a uniform source pressure between the auxiliary pump P2 and the two pulleys, the pulley width can be precisely controlled.
[第2実施形態]
図7を参照して、第2実施形態に係る車載油圧供給装置1Aについて説明する。図7は、第2実施形態の車載油圧供給装置1Aの構成の一例を示すブロック図である。なお、本実施形態の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Aは、主ポンプP1Aが正逆転することにより、元圧を可変することができる点において、第1実施形態と異なる。 [Second Embodiment]
With reference to FIG. 7, an in-vehicle hydraulicpressure supply apparatus 1A according to the second embodiment will be described. FIG. 7 is a block diagram illustrating an example of a configuration of the in-vehicle hydraulic pressure supply device 1A according to the second embodiment. In the description of the present embodiment, the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted. The in-vehicle hydraulic pressure supply device 1A of the present embodiment is different from the first embodiment in that the main pressure can be varied by forward and reverse rotation of the main pump P1A.
図7を参照して、第2実施形態に係る車載油圧供給装置1Aについて説明する。図7は、第2実施形態の車載油圧供給装置1Aの構成の一例を示すブロック図である。なお、本実施形態の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Aは、主ポンプP1Aが正逆転することにより、元圧を可変することができる点において、第1実施形態と異なる。 [Second Embodiment]
With reference to FIG. 7, an in-vehicle hydraulic
車載油圧供給装置1Aは、油圧供給部40Aを備える。この油圧供給部40Aは、上述した逆止弁V1に代えて、双方向逆止弁V10を備える。この双方向逆止弁V10は、作動油の移動方向に対して並列に配置された2つの逆止弁である、順方向逆止弁V101と、逆方向逆止弁V102とを備える。
順方向逆止弁V101は、作動油を主ポンプP1Aから閉油路10への順方向、つまり図7の矢印C1方向に通過させ、かつ閉油路10から主ポンプP1Aへの逆方向、つまり図7の矢印D1方向に通過させない。
逆方向逆止弁V102は、作動油を逆方向に通過させ、かつ順方向に通過させない。 The in-vehicle hydraulicpressure supply device 1A includes a hydraulic pressure supply unit 40A. The hydraulic pressure supply unit 40A includes a bidirectional check valve V10 instead of the check valve V1 described above. The bidirectional check valve V10 includes a forward check valve V101 and a reverse check valve V102 which are two check valves arranged in parallel with respect to the moving direction of the hydraulic oil.
The forward check valve V101 passes hydraulic oil in the forward direction from the main pump P1A to theclosed oil passage 10, that is, in the direction of the arrow C1 in FIG. 7, and in the reverse direction from the closed oil passage 10 to the main pump P1A, that is, It does not pass in the direction of arrow D1 in FIG.
The reverse direction check valve V102 allows hydraulic oil to pass in the reverse direction and not in the forward direction.
順方向逆止弁V101は、作動油を主ポンプP1Aから閉油路10への順方向、つまり図7の矢印C1方向に通過させ、かつ閉油路10から主ポンプP1Aへの逆方向、つまり図7の矢印D1方向に通過させない。
逆方向逆止弁V102は、作動油を逆方向に通過させ、かつ順方向に通過させない。 The in-vehicle hydraulic
The forward check valve V101 passes hydraulic oil in the forward direction from the main pump P1A to the
The reverse direction check valve V102 allows hydraulic oil to pass in the reverse direction and not in the forward direction.
また、本実施形態の主ポンプP1Aは、正逆転する。主ポンプP1Aは、正転することにより、作動油を図7の矢印C方向に吐出し、逆転することにより、作動油を図7の矢印D方向に吐出する。
Moreover, the main pump P1A of this embodiment performs forward and reverse rotation. The main pump P1A discharges hydraulic oil in the direction of arrow C in FIG. 7 by rotating forward, and discharges hydraulic oil in the direction of arrow D in FIG. 7 by reverse rotation.
このように構成することにより、車載油圧供給装置1Aは、第1実施形態に比べて、プーリ幅の制御をより精密に行うことができる。
With this configuration, the in-vehicle hydraulic pressure supply device 1A can control the pulley width more precisely than in the first embodiment.
なお、車載油圧供給装置1Aは、図7に示すオリフィスORFを備えていてもよい。このオリフィスORFは、油路601から油路502を介してオイルパンOPに作動油を排油する。車載油圧供給装置1Aは、このオリフィスORFを備えることにより、主ポンプP1が所望の元圧以上に加圧した場合に、元圧の上昇を抑制することができる。つまり、車載油圧供給装置1Aは、オリフィスORFを備えることにより、主ポンプP1の制御を緻密に行わなくても、元圧を適正範囲に制御することができる。
Note that the in-vehicle hydraulic pressure supply device 1A may include an orifice ORF shown in FIG. The orifice ORF discharges hydraulic oil from the oil passage 601 through the oil passage 502 to the oil pan OP. By providing this orifice ORF, the in-vehicle hydraulic pressure supply device 1A can suppress an increase in the source pressure when the main pump P1 is pressurized to a desired source pressure or higher. In other words, the in-vehicle hydraulic pressure supply device 1A includes the orifice ORF, so that the original pressure can be controlled within an appropriate range without precisely controlling the main pump P1.
[第2実施形態の変形例]
図8を参照して、第2実施形態の変形例に係る車載油圧供給装置1Bについて説明する。
図8は、第2実施形態の変形例の車載油圧供給装置1Bの構成の一例を示すブロック図である。なお、本変形例の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Bは、双方向逆止弁を2つ備える点において、上述した第2実施形態と異なる。 [Modification of Second Embodiment]
With reference to FIG. 8, an in-vehicle hydraulicpressure supply device 1B according to a modification of the second embodiment will be described.
FIG. 8 is a block diagram illustrating an example of a configuration of an in-vehicle hydraulicpressure supply device 1B according to a modification of the second embodiment. In the description of this modification, the same components as those in the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted. The in-vehicle hydraulic pressure supply device 1B of the present embodiment differs from the second embodiment described above in that it includes two bidirectional check valves.
図8を参照して、第2実施形態の変形例に係る車載油圧供給装置1Bについて説明する。
図8は、第2実施形態の変形例の車載油圧供給装置1Bの構成の一例を示すブロック図である。なお、本変形例の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Bは、双方向逆止弁を2つ備える点において、上述した第2実施形態と異なる。 [Modification of Second Embodiment]
With reference to FIG. 8, an in-vehicle hydraulic
FIG. 8 is a block diagram illustrating an example of a configuration of an in-vehicle hydraulic
車載油圧供給装置1Bは、油圧供給部40Bを備える。この油圧供給部40Bは、双方向逆止弁V10Aを備える。この双方向逆止弁V10Aは、順方向逆止弁及び逆方向逆止弁の組を2組備える。つまり、双方向逆止弁V10Aは、上述した順方向逆止弁V101及び、逆方向逆止弁V102に加え、順方向逆止弁V103及び、逆方向逆止弁V104を備える。
The in-vehicle hydraulic pressure supply device 1B includes a hydraulic pressure supply unit 40B. The hydraulic pressure supply unit 40B includes a bidirectional check valve V10A. This bidirectional check valve V10A includes two sets of a forward check valve and a reverse check valve. That is, the bidirectional check valve V10A includes a forward check valve V103 and a reverse check valve V104 in addition to the forward check valve V101 and the reverse check valve V102 described above.
具体的には、車載油圧供給装置1Bは、プライマリプーリPPと補助ポンプP2との間の閉油路10に対して、順方向逆止弁V103及び、逆方向逆止弁V104を備えている。また、車載油圧供給装置1Bは、セカンダリプーリSPと補助ポンプP2との間の閉油路10に対して、順方向逆止弁V101及び、逆方向逆止弁V102を備えている。つまり、車載油圧供給装置1Bは、補助ポンプP2と2つのプーリとの間に、それぞれ元圧を供給する機構を備えている。このため、車載油圧供給装置1Bは、補助ポンプP2と2つのプーリとの間に、均一な元圧を加えることができるため、プーリ幅を精密に制御することができる。
Specifically, the in-vehicle hydraulic pressure supply device 1B includes a forward check valve V103 and a reverse check valve V104 with respect to the closed oil passage 10 between the primary pulley PP and the auxiliary pump P2. The in-vehicle hydraulic pressure supply device 1B includes a forward check valve V101 and a reverse check valve V102 with respect to the closed oil passage 10 between the secondary pulley SP and the auxiliary pump P2. That is, the in-vehicle hydraulic pressure supply device 1B includes a mechanism for supplying the original pressure between the auxiliary pump P2 and the two pulleys. For this reason, since the vehicle-mounted hydraulic pressure supply device 1B can apply a uniform source pressure between the auxiliary pump P2 and the two pulleys, the pulley width can be precisely controlled.
[第3実施形態]
図9を参照して、第3実施形態に係る車載油圧供給装置1Cについて説明する。
図9は、第3実施形態の車載油圧供給装置1Cの構成の一例を示すブロック図である。なお、本実施形態の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Cは、閉油路10にバイパス油路BP1を備える点において、第1実施形態と異なる。 [Third Embodiment]
With reference to FIG. 9, an in-vehicle hydraulic pressure supply apparatus 1C according to the third embodiment will be described.
FIG. 9 is a block diagram illustrating an example of the configuration of the in-vehicle hydraulic pressure supply device 1C according to the third embodiment. In the description of the present embodiment, the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted. The in-vehicle hydraulic pressure supply device 1C according to the present embodiment is different from the first embodiment in that theclosed oil passage 10 includes a bypass oil passage BP1.
図9を参照して、第3実施形態に係る車載油圧供給装置1Cについて説明する。
図9は、第3実施形態の車載油圧供給装置1Cの構成の一例を示すブロック図である。なお、本実施形態の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Cは、閉油路10にバイパス油路BP1を備える点において、第1実施形態と異なる。 [Third Embodiment]
With reference to FIG. 9, an in-vehicle hydraulic pressure supply apparatus 1C according to the third embodiment will be described.
FIG. 9 is a block diagram illustrating an example of the configuration of the in-vehicle hydraulic pressure supply device 1C according to the third embodiment. In the description of the present embodiment, the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted. The in-vehicle hydraulic pressure supply device 1C according to the present embodiment is different from the first embodiment in that the
バイパス油路BP1は、作動油の移動方向に対して補助ポンプP2と並列に配置され、バイパス弁VBP1と、オリフィスORF2とを備える。
バイパス弁VBP1は、閉油路10内の油圧が所定値未満の場合に作動油を通過させ、油圧が所定値を超える場合に作動油を通過させない。
オリフィスORF2は、バイパス油路BP1を通過する作動油の流量を抑制する。なお、バイパス油路BP1のオリフィスORF2の前後には、オリフィスORF2の詰まりを抑制する、オイルフィルタF1、オイルフィルタF2が設けられていてもよい。 The bypass oil passage BP1 is arranged in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil, and includes a bypass valve VBP1 and an orifice ORF2.
The bypass valve VBP1 allows hydraulic oil to pass when the hydraulic pressure in theclosed oil passage 10 is less than a predetermined value, and does not allow hydraulic oil to pass when the hydraulic pressure exceeds a predetermined value.
The orifice ORF2 suppresses the flow rate of the hydraulic oil that passes through the bypass oil passage BP1. An oil filter F1 and an oil filter F2 that suppress clogging of the orifice ORF2 may be provided before and after the orifice ORF2 of the bypass oil passage BP1.
バイパス弁VBP1は、閉油路10内の油圧が所定値未満の場合に作動油を通過させ、油圧が所定値を超える場合に作動油を通過させない。
オリフィスORF2は、バイパス油路BP1を通過する作動油の流量を抑制する。なお、バイパス油路BP1のオリフィスORF2の前後には、オリフィスORF2の詰まりを抑制する、オイルフィルタF1、オイルフィルタF2が設けられていてもよい。 The bypass oil passage BP1 is arranged in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil, and includes a bypass valve VBP1 and an orifice ORF2.
The bypass valve VBP1 allows hydraulic oil to pass when the hydraulic pressure in the
The orifice ORF2 suppresses the flow rate of the hydraulic oil that passes through the bypass oil passage BP1. An oil filter F1 and an oil filter F2 that suppress clogging of the orifice ORF2 may be provided before and after the orifice ORF2 of the bypass oil passage BP1.
補助ポンプP2が所定の回転数未満である場合には、閉油路10内の油圧が所定値未満になる。この場合、バイパス弁VBP1は、開弁しており作動油を通過させる。ここで、補助ポンプP2が所定の回転数未満である場合とは、プーリ幅の変化幅が小さい場合、又はプーリ幅の目標変速時間が長い場合である。つまり、補助ポンプP2が所定の回転数未満である場合とは、プーリ幅の変化が緩やかである場合である。
一方、補助ポンプP2が所定の回転数以上である場合には、閉油路10内の油圧が所定値以上になる。この場合、バイパス弁VBP1は、閉弁し作動油を通過させない。ここで、補助ポンプP2が所定の回転数以上である場合とは、プーリ幅の変化幅が大きい場合、又はプーリ幅の目標変速時間が短い場合である。つまり、補助ポンプP2が所定の回転数以上である場合とは、プーリ幅の変化が急激である場合である。 When the auxiliary pump P2 is less than the predetermined number of revolutions, the oil pressure in theclosed oil passage 10 becomes less than a predetermined value. In this case, the bypass valve VBP1 is opened and allows hydraulic oil to pass therethrough. Here, the case where the auxiliary pump P2 is less than the predetermined number of rotations is a case where the change width of the pulley width is small or a target shift time of the pulley width is long. That is, the case where the auxiliary pump P2 is less than the predetermined rotation number is a case where the change in the pulley width is moderate.
On the other hand, when the auxiliary pump P2 is equal to or higher than the predetermined number of revolutions, the hydraulic pressure in theclosed oil passage 10 is equal to or higher than a predetermined value. In this case, the bypass valve VBP1 is closed and does not allow hydraulic oil to pass. Here, the case where the auxiliary pump P2 is equal to or higher than the predetermined number of rotations is a case where the change width of the pulley width is large or a target shift time of the pulley width is short. That is, the case where the auxiliary pump P2 is equal to or higher than the predetermined rotation number is a case where the change in the pulley width is abrupt.
一方、補助ポンプP2が所定の回転数以上である場合には、閉油路10内の油圧が所定値以上になる。この場合、バイパス弁VBP1は、閉弁し作動油を通過させない。ここで、補助ポンプP2が所定の回転数以上である場合とは、プーリ幅の変化幅が大きい場合、又はプーリ幅の目標変速時間が短い場合である。つまり、補助ポンプP2が所定の回転数以上である場合とは、プーリ幅の変化が急激である場合である。 When the auxiliary pump P2 is less than the predetermined number of revolutions, the oil pressure in the
On the other hand, when the auxiliary pump P2 is equal to or higher than the predetermined number of revolutions, the hydraulic pressure in the
ここで、上位ユニット2が、プーリ幅を緩やかに変化させる変速指令を出力したとする。この場合、補助ポンプP2は、緩やかにプーリ幅を変化させるために低速で回転する。この結果、閉油路10内の油圧の上昇は緩やかで、バイパス弁VBP1が閉弁しない。これにより、閉油路10内の作動油は、一方のプーリから他方のプーリへ移動する際に、一部がバイパス油路BP1を経由して再び、補助ポンプP2に流入する。つまり、バイパス弁VBP1が開弁状態であると、補助ポンプP2が作動油を吐出しても、その全量が他方のプーリに移動するのではなく、一部のみが他方のプーリに移動する。したがって、補助
ポンプP2の回転数の制御を緻密に行わなくても、緩やかにプーリ幅を変化させることができる。つまり、車載油圧供給装置1Cは、バイパス油路BP1を備えることにより、プーリ幅の制御性を向上させることができる。 Here, it is assumed that theupper unit 2 outputs a shift command for gently changing the pulley width. In this case, the auxiliary pump P2 rotates at a low speed in order to gently change the pulley width. As a result, the increase in the hydraulic pressure in the oil closing passage 10 is moderate, and the bypass valve VBP1 does not close. As a result, when the hydraulic oil in the closed oil passage 10 moves from one pulley to the other pulley, part of it flows again into the auxiliary pump P2 via the bypass oil passage BP1. That is, when the bypass valve VBP1 is in the open state, even if the auxiliary pump P2 discharges hydraulic oil, the entire amount does not move to the other pulley, but only a part moves to the other pulley. Therefore, the pulley width can be gradually changed without precisely controlling the rotation speed of the auxiliary pump P2. That is, the on-board hydraulic pressure supply device 1C can improve the controllability of the pulley width by including the bypass oil passage BP1.
ポンプP2の回転数の制御を緻密に行わなくても、緩やかにプーリ幅を変化させることができる。つまり、車載油圧供給装置1Cは、バイパス油路BP1を備えることにより、プーリ幅の制御性を向上させることができる。 Here, it is assumed that the
一方、上位ユニット2が、プーリ幅を急激に変化させる変速指令を出力したとする。この場合、補助ポンプP2は、急激にプーリ幅を変化させるために高速で回転する。この結果、閉油路10内の油圧が急激に上昇し、バイパス弁VBP1が閉弁する。これにより、閉油路10内の作動油は、一方のプーリから他方のプーリへ、バイパス油路BP1を経由せずに、補助ポンプP2を経由して移動する。したがって、バイパス弁VBP1が閉弁することにより、作動油の移動速度が速まる。つまり、車載油圧供給装置1Cは、バイパス弁VBP1を備えることにより、プーリ幅の制御速度の向上を図ることができる。
On the other hand, it is assumed that the upper unit 2 outputs a shift command for changing the pulley width abruptly. In this case, the auxiliary pump P2 rotates at a high speed in order to rapidly change the pulley width. As a result, the hydraulic pressure in the oil closing passage 10 increases rapidly, and the bypass valve VBP1 is closed. As a result, the hydraulic oil in the closed oil passage 10 moves from one pulley to the other pulley via the auxiliary pump P2, not via the bypass oil passage BP1. Therefore, when the bypass valve VBP1 is closed, the moving speed of the hydraulic oil is increased. That is, the in-vehicle hydraulic pressure supply device 1 </ b> C can improve the control speed of the pulley width by including the bypass valve VBP <b> 1.
つまり、車載油圧供給装置1Cは、バイパス油路BP1と、バイパス弁VBP1とを備えることにより、プーリ幅の制御性の向上と、プーリ幅の制御速度の向上とを両立させることができる。
That is, the in-vehicle hydraulic pressure supply device 1C includes both the bypass oil passage BP1 and the bypass valve VBP1, thereby making it possible to improve both the controllability of the pulley width and the control speed of the pulley width.
[第3実施形態の変形例]
図10を参照して、第3実施形態の変形例に係る車載油圧供給装置1Dについて説明する。
図10は、第3実施形態の変形例の車載油圧供給装置1Dの構成の一例を示すブロック図である。なお、本実施形態の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Dは、閉油路10にバイパス油路BP2をさらに備える点において、第3実施形態と異なる。 [Modification of Third Embodiment]
With reference to FIG. 10, an in-vehicle hydraulicpressure supply device 1D according to a modification of the third embodiment will be described.
FIG. 10 is a block diagram illustrating an example of a configuration of an in-vehicle hydraulicpressure supply device 1D according to a modification of the third embodiment. In the description of the present embodiment, the same components as those of the other embodiments described above are denoted by the same reference numerals and the description thereof is omitted. The in-vehicle hydraulic pressure supply device 1D of the present embodiment is different from the third embodiment in that the closed oil passage 10 further includes a bypass oil passage BP2.
図10を参照して、第3実施形態の変形例に係る車載油圧供給装置1Dについて説明する。
図10は、第3実施形態の変形例の車載油圧供給装置1Dの構成の一例を示すブロック図である。なお、本実施形態の説明において、上述した他の実施形態と同一の構成については、同一の符号を付してその説明を省略する。本実施形態の車載油圧供給装置1Dは、閉油路10にバイパス油路BP2をさらに備える点において、第3実施形態と異なる。 [Modification of Third Embodiment]
With reference to FIG. 10, an in-vehicle hydraulic
FIG. 10 is a block diagram illustrating an example of a configuration of an in-vehicle hydraulic
バイパス油路BP2は、作動油の移動方向に対して補助ポンプP2と並列に配置され、バイパス弁VBP2と、補助ポンプP3とを備える。
バイパス弁VBP2は、バイパス油路BP2内の油圧が所定値未満の場合にバイパス油路BP2内の作動油の移動を阻止し、バイパス油路BP2内の油圧が所定値を超える場合にバイパス油路BP2内の作動油の移動を可能にする。
補助ポンプP3は、バイパス油路BP2に設けられ、閉油路10内の作動油を、プライマリプーリPP及びセカンダリプーリSPの一方から他方へ移動させる。 The bypass oil passage BP2 is disposed in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil, and includes a bypass valve VBP2 and an auxiliary pump P3.
The bypass valve VBP2 prevents movement of the hydraulic oil in the bypass oil passage BP2 when the oil pressure in the bypass oil passage BP2 is less than a predetermined value, and bypass oil passage when the oil pressure in the bypass oil passage BP2 exceeds a predetermined value. Allows movement of hydraulic oil in BP2.
The auxiliary pump P3 is provided in the bypass oil passage BP2, and moves the hydraulic oil in theclosed oil passage 10 from one of the primary pulley PP and the secondary pulley SP to the other.
バイパス弁VBP2は、バイパス油路BP2内の油圧が所定値未満の場合にバイパス油路BP2内の作動油の移動を阻止し、バイパス油路BP2内の油圧が所定値を超える場合にバイパス油路BP2内の作動油の移動を可能にする。
補助ポンプP3は、バイパス油路BP2に設けられ、閉油路10内の作動油を、プライマリプーリPP及びセカンダリプーリSPの一方から他方へ移動させる。 The bypass oil passage BP2 is disposed in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil, and includes a bypass valve VBP2 and an auxiliary pump P3.
The bypass valve VBP2 prevents movement of the hydraulic oil in the bypass oil passage BP2 when the oil pressure in the bypass oil passage BP2 is less than a predetermined value, and bypass oil passage when the oil pressure in the bypass oil passage BP2 exceeds a predetermined value. Allows movement of hydraulic oil in BP2.
The auxiliary pump P3 is provided in the bypass oil passage BP2, and moves the hydraulic oil in the
車載油圧供給装置1Dは、上位ユニット2が、プーリ幅を急激に変化させる変速指令を出力した場合に、補助ポンプP3を駆動する。この結果、バイパス油路BP2内の油圧が上昇し、バイパス弁VBP2を開弁する。これにより、閉油路10内の作動油は、一方のプーリから他方のプーリへ、バイパス油路BP2及び補助ポンプP3を経由して移動する。したがって、バイパス弁VBP2が開弁することにより、作動油の移動速度が速まる。つまり、車載油圧供給装置1Dは、バイパス油路BP2と補助ポンプP3とを備えることにより、プーリ幅の制御速度の向上を図ることができる。
The in-vehicle hydraulic pressure supply device 1D drives the auxiliary pump P3 when the host unit 2 outputs a shift command that causes the pulley width to change abruptly. As a result, the hydraulic pressure in the bypass oil passage BP2 increases and the bypass valve VBP2 is opened. As a result, the hydraulic oil in the closed oil passage 10 moves from one pulley to the other pulley via the bypass oil passage BP2 and the auxiliary pump P3. Accordingly, the movement speed of the hydraulic oil is increased by opening the bypass valve VBP2. That is, the in-vehicle hydraulic pressure supply apparatus 1D can improve the control speed of the pulley width by including the bypass oil passage BP2 and the auxiliary pump P3.
また、車載油圧供給装置1Dは、バイパス油路BP2と補助ポンプP3とを備えることにより、作動油吐出能力を補助ポンプP2と補助ポンプP3とで分担することができる。したがって、上述した第3実施形態に比べ補助ポンプP2を小型化することができる。また、補助ポンプP2と、補助ポンプP3とについて、部品の共通化を行うことも可能になり、1台の大きなポンプを備える構成に比べて、部品コストを低減することができる。
Moreover, the vehicle-mounted hydraulic pressure supply device 1D can share the hydraulic oil discharge capacity between the auxiliary pump P2 and the auxiliary pump P3 by including the bypass oil passage BP2 and the auxiliary pump P3. Therefore, the auxiliary pump P2 can be downsized as compared with the third embodiment described above. Further, it is possible to share parts for the auxiliary pump P2 and the auxiliary pump P3, and the parts cost can be reduced as compared with a configuration including one large pump.
また、車載油圧供給装置1Dは、バイパス弁VBP2を備えることにより、緩やかにプーリ幅を変化させる場合に、補助ポンプP3を停止することができるため、補助ポンプP3の消費エネルギーを低減することができる。
言い換えると、車載油圧供給装置1Dは、作動油の移動方向に対して補助ポンプP2と並列に配置される第二のバイパス油路と、第二のバイパス油路に設けられ、閉油路10内の作動油を、プライマリプーリPP及びセカンダリプーリSPの一方から他方へ移動させる第二の補助ポンプP3と、第二のバイパス油路内の油圧が所定値未満の場合に第二のバイパス油路内の作動油の移動を阻止し、前記第二のバイパス油路内の油圧が所定値を超える場合に前記第二のバイパス油路内の前記作動油の移動を可能にするバルブとを備えている。 Further, since the on-vehicle hydraulicpressure supply device 1D includes the bypass valve VBP2, when the pulley width is gradually changed, the auxiliary pump P3 can be stopped, so that the energy consumption of the auxiliary pump P3 can be reduced. .
In other words, the in-vehicle hydraulicpressure supply device 1D is provided in the second bypass oil passage and the second bypass oil passage that are arranged in parallel with the auxiliary pump P2 with respect to the moving direction of the hydraulic oil. In the second bypass oil passage when the hydraulic pressure in the second bypass oil passage is less than a predetermined value, and the second auxiliary pump P3 for moving the hydraulic oil from one of the primary pulley PP and the secondary pulley SP to the other A valve that prevents the movement of the hydraulic oil in the second bypass oil passage when the hydraulic pressure in the second bypass oil passage exceeds a predetermined value. .
言い換えると、車載油圧供給装置1Dは、作動油の移動方向に対して補助ポンプP2と並列に配置される第二のバイパス油路と、第二のバイパス油路に設けられ、閉油路10内の作動油を、プライマリプーリPP及びセカンダリプーリSPの一方から他方へ移動させる第二の補助ポンプP3と、第二のバイパス油路内の油圧が所定値未満の場合に第二のバイパス油路内の作動油の移動を阻止し、前記第二のバイパス油路内の油圧が所定値を超える場合に前記第二のバイパス油路内の前記作動油の移動を可能にするバルブとを備えている。 Further, since the on-vehicle hydraulic
In other words, the in-vehicle hydraulic
なお、上記説明した各実施形態及びその変形例は、相互に矛盾しない範囲内において、構成を適宜組み合わせることができる。
It should be noted that the above-described embodiments and modifications thereof can be combined as appropriate within a range that does not contradict each other.
1、1A、1B、1C、1D…車載油圧供給装置、10…閉油路、20…位置センサ(プーリ幅検出部)、30…制御ユニット、301…制御部、302…主ポンプ駆動回路、303…補助ポンプ駆動回路、311…主ポンプ制御部、312…補助ポンプ制御部、313…故障検出部、PP…プライマリプーリ、SP…セカンダリプーリ、PS1、PS2…油圧センサ、P1…主ポンプ、P2…補助ポンプ、V1、V11、V12、V3、V4…逆止弁、ACC…アキュムレータ
DESCRIPTION OF SYMBOLS 1, 1A, 1B, 1C, 1D ... Car-mounted hydraulic pressure supply apparatus, 10 ... Oil-closing path, 20 ... Position sensor (pulley width detection part), 30 ... Control unit, 301 ... Control part, 302 ... Main pump drive circuit, 303 ... Auxiliary pump drive circuit, 311 ... Main pump control unit, 312 ... Auxiliary pump control unit, 313 ... Failure detection unit, PP ... Primary pulley, SP ... Secondary pulley, PS1, PS2 ... Hydraulic sensor, P1 ... Main pump, P2 ... Auxiliary pump, V1, V11, V12, V3, V4 ... check valve, ACC ... accumulator
Claims (9)
- 油圧発生源から供給される油圧が付された作動油によってプーリ幅が可変するプライマリプーリ及びセカンダリプーリの、それぞれのプーリ幅を制御することにより、減速比を可変する無段階変速機の車載油圧供給装置であって、
前記プライマリプーリと、前記セカンダリプーリとの間に設けられた閉油路と、
前記閉油路と、油圧を供給する主ポンプとの間に設けられた逆止弁と、
前記逆止弁を介して前記主ポンプから供給される油圧が付された前記閉油路内の作動油を、前記プライマリプーリ及び前記セカンダリプーリの一方から他方へ移動させる補助ポンプと、
前記プーリ幅の状態を検出するプーリ幅検出部と、
入力される変速指令と、前記プーリ幅検出部が検出する前記プーリ幅の状態とに基づいて、前記プライマリプーリから前記セカンダリプーリに前記作動油を移動させる正方向、及び前記セカンダリプーリから前記プライマリプーリに前記作動油を移動させる負方向のいずれかの移動方向と、前記作動油の前記正方向又は前記負方向への移動速度とを決定し、決定した前記移動方向及び前記移動速度によって前記補助ポンプを駆動制御する制御部と、
を備える、車載油圧供給装置。 In-vehicle hydraulic pressure supply for continuously variable transmissions that change the reduction ratio by controlling the pulley widths of the primary pulley and secondary pulley whose pulley width is variable by hydraulic oil supplied from the hydraulic pressure source A device,
A closed oil path provided between the primary pulley and the secondary pulley;
A check valve provided between the oil closing passage and a main pump supplying hydraulic pressure;
An auxiliary pump that moves hydraulic oil in the closed oil passage, to which hydraulic pressure supplied from the main pump is supplied via the check valve, from one of the primary pulley and the secondary pulley to the other;
A pulley width detector for detecting a state of the pulley width;
Based on the input shift command and the pulley width state detected by the pulley width detector, the forward direction in which the hydraulic oil is moved from the primary pulley to the secondary pulley, and from the secondary pulley to the primary pulley The movement direction of the negative direction in which the hydraulic oil is moved in the direction and the movement speed of the hydraulic oil in the positive direction or the negative direction are determined, and the auxiliary pump is determined according to the determined movement direction and the movement speed. A control unit for controlling the drive,
An on-vehicle hydraulic pressure supply device comprising: - 前記閉油路は、
前記作動油を前記正方向に通過させ、かつ前記負方向に通過させない正方向逆止弁と、
前記作動油を前記負方向に通過させ、かつ前記正方向に通過させない負方向逆止弁とが、
前記作動油の移動方向に対して並列に配置された双方向逆止弁を備える、
請求項1に記載の車載油圧供給装置。 The oil closing path is
A positive check valve that allows the hydraulic oil to pass in the positive direction and not to pass in the negative direction;
A negative check valve that passes the hydraulic oil in the negative direction and does not pass in the positive direction,
A bi-directional check valve disposed in parallel with the moving direction of the hydraulic oil;
The in-vehicle hydraulic pressure supply device according to claim 1. - 前記双方向逆止弁は、
前記正方向逆止弁と、前記負方向逆止弁とがいずれも開弁しない油圧範囲を有する、
請求項2に記載の車載油圧供給装置。 The bidirectional check valve is
A hydraulic range in which neither the positive direction check valve nor the negative direction check valve opens;
The in-vehicle hydraulic pressure supply device according to claim 2. - 前記逆止弁は、
前記プライマリプーリと前記補助ポンプとの間の前記閉油路に対して、前記主ポンプからの油圧を供給する第一の逆止弁と、
前記セカンダリプーリと前記補助ポンプとの間の前記閉油路に対して、前記主ポンプからの油圧を供給する第二の逆止弁とを備える、
請求項1から請求項3のいずれか一項に記載の車載油圧供給装置。 The check valve is
A first check valve for supplying hydraulic pressure from the main pump to the oil closing path between the primary pulley and the auxiliary pump;
A second check valve for supplying hydraulic pressure from the main pump to the closed passage between the secondary pulley and the auxiliary pump;
The in-vehicle hydraulic pressure supply device according to any one of claims 1 to 3. - 前記プーリ幅検出部は、
前記プライマリプーリ又は前記セカンダリプーリのうち少なくとも一方のプーリの幅方向の位置を検出する位置検出センサを備える、
請求項1から請求項4のいずれか一項に記載の車載油圧供給装置。 The pulley width detector
A position detection sensor for detecting a position in a width direction of at least one of the primary pulley and the secondary pulley;
The in-vehicle hydraulic pressure supply device according to any one of claims 1 to 4. - 前記閉油路内の作動油の圧力を検出する油圧センサを備え、
前記制御部は、さらに前記油圧センサが検出する前記圧力に基づいて、前記補助ポンプを駆動制御する、
請求項1から請求項5のいずれか一項に記載の車載油圧供給装置。 A hydraulic sensor for detecting the pressure of the hydraulic oil in the closed oil passage;
The control unit further drives and controls the auxiliary pump based on the pressure detected by the hydraulic sensor.
The in-vehicle hydraulic pressure supply device according to any one of claims 1 to 5. - 前記作動油を前記主ポンプから前記閉油路への順方向に通過させ、かつ前記閉油路から前記主ポンプへの逆方向に通過させない逆止弁と、前記作動油を前記逆方向に通過させ、かつ前記順方向に通過させない逆止弁とが、前記作動油の移動方向に対して並列に配置された双方向逆止弁を、前記逆止弁として備える、
請求項1から請求項6のいずれか一項に記載の車載油圧供給装置。 A check valve that allows the hydraulic oil to pass in the forward direction from the main pump to the closed oil passage, and does not pass in the reverse direction from the closed oil passage to the main pump; and passes the hydraulic oil in the reverse direction And a non-return valve that is not allowed to pass in the forward direction includes a bi-directional check valve arranged in parallel with the moving direction of the hydraulic oil as the check valve.
The in-vehicle hydraulic pressure supply device according to any one of claims 1 to 6. - 前記作動油の移動方向に対して前記補助ポンプと並列に配置され、前記閉油路内の油圧が所定値未満の場合に前記作動油を通過させ、前記油圧が所定値を超える場合に前記作動油を通過させないバイパス油路を備える、
請求項1から請求項7のいずれか一項に記載の車載油圧供給装置。 It is arranged in parallel with the auxiliary pump with respect to the moving direction of the hydraulic oil, and allows the hydraulic oil to pass when the hydraulic pressure in the closed oil passage is less than a predetermined value, and operates when the hydraulic pressure exceeds a predetermined value. Provide with bypass oil passage that does not allow oil to pass through,
The in-vehicle hydraulic pressure supply device according to any one of claims 1 to 7. - 前記作動油の移動方向に対して前記補助ポンプと並列に配置される第二のバイパス油路と、
前記第二のバイパス油路に設けられ、前記閉油路内の作動油を、前記プライマリプーリ及び前記セカンダリプーリの一方から他方へ移動させる第二の補助ポンプと、
前記第二のバイパス油路内の油圧が所定値未満の場合に前記第二のバイパス油路内の前記作動油の移動を阻止し、前記第二のバイパス油路内の油圧が所定値を超える場合に前記第二のバイパス油路内の前記作動油の移動を可能にするバルブとを備える、
請求項8に記載の車載油圧供給装置。 A second bypass oil passage disposed in parallel with the auxiliary pump with respect to the moving direction of the hydraulic oil;
A second auxiliary pump that is provided in the second bypass oil passage and moves hydraulic oil in the closed oil passage from one of the primary pulley and the secondary pulley to the other;
When the hydraulic pressure in the second bypass oil passage is less than a predetermined value, the hydraulic oil in the second bypass oil passage is prevented from moving, and the hydraulic pressure in the second bypass oil passage exceeds a predetermined value. A valve that enables movement of the hydraulic oil in the second bypass oil passage in a case,
The in-vehicle hydraulic pressure supply device according to claim 8.
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CN107949728B (en) | 2020-01-14 |
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