JPWO2017033888A1 - In-vehicle hydraulic supply system - Google Patents

Abstract

The in-vehicle hydraulic pressure supply device is an in-vehicle hydraulic pressure supply device for a continuously variable transmission that changes a reduction ratio by controlling a pulley width, and a closed oil path provided between a primary pulley and a secondary pulley; A check valve provided between the closed oil passage and the main pump that supplies hydraulic pressure, and hydraulic fluid in the closed oil passage that is supplied with hydraulic pressure supplied from the main pump via the check valve Based on the auxiliary pump that moves from one of the pulley and the secondary pulley to the other, the pulley width detection unit that detects the pulley width state, the input shift command, and the pulley width state that the pulley width detection unit detects , 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 positive or negative direction of the hydraulic oil. Determining a moving speed of the direction, and a control unit that controls driving an auxiliary pump by the determined moving direction and the moving speed.

Description

  The present invention relates to an in-vehicle hydraulic pressure supply device.

  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.

JP 2005-180561 A

  In the on-vehicle hydraulic pressure supply apparatus 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.

  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 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 a pulley width state that is detected by the pulley width detector Accordingly, 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 hydraulic oil is moved in the positive direction. 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.

  According to one aspect of the present invention, an in-vehicle hydraulic pressure supply device capable of reducing consumed energy is provided.

It is a block diagram which shows an example of a structure of the vehicle-mounted hydraulic pressure supply apparatus of 1st Embodiment. It is a graph which shows an example of the valve opening hydraulic pressure threshold value of the bidirectional | two-way check valve of this embodiment. It is a block diagram which shows an example of a function structure of the control unit of this embodiment. It is a flowchart which shows an example of the flow of control of the main pump of this embodiment. It is a flowchart which shows an example of the flow of control of the auxiliary pump of this embodiment. It is a flowchart which shows an example of the flow of the failure detection process of this embodiment. It is a block diagram which shows an example of a structure of the vehicle-mounted hydraulic pressure supply apparatus of 2nd Embodiment. It is a block diagram which shows an example of a structure of the vehicle-mounted hydraulic pressure supply apparatus of the modification of 2nd Embodiment. It is a block diagram which shows an example of a structure of the vehicle-mounted hydraulic pressure supply apparatus of 3rd Embodiment. It is a block diagram which shows an example of a structure of the vehicle-mounted hydraulic pressure supply apparatus of the modification of 3rd Embodiment.

  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.

[First Embodiment]
An in-vehicle hydraulic pressure 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.

[Outline of continuously variable transmission 3]
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. 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.

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.

  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 due to 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 original pressure is about 4 to 5 [Mpa] in the example of the present embodiment. That is, the hydraulic oil pressurized to about 4 to 5 [Mpa] is supplied to the primary pulley PP and the secondary pulley SP.

[Configuration of In-vehicle Hydraulic Supply Device 1]
Next, the configuration of the in-vehicle hydraulic pressure 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.

The pulley 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 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. 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.

  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.

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. 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.

  The hydraulic 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.

[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 figure, that is, in the positive direction, and not in the direction of arrow B1 in the figure, 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.

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 closed 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.

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 path 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 closed oil 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 closed oil 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.

  On the other hand, when the positive direction check valve V21 and the negative direction check valve V22 have a hydraulic range in which neither of them opens, the bidirectional check valve V2 can suppress the movement of the hydraulic oil. 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. 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.

[About hydraulic pressure supply unit 40]

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. Supply to path 10.
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. 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 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. 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 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 set range of the original pressure. 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.

[About the control unit 30]
Next, the functional configuration of the control unit 30 will be described with reference to FIG.
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. Moreover, 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”.
In addition, 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”.
Further, the 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.

[Control of main pump P1]
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. 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.

  The main pump control unit 311 acquires the original pressure information from the hydraulic sensor PS1 (step S30). This source pressure information indicates the actual measured actual pressure value detected by the hydraulic sensor PS1.

  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).

  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.

  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.

[Control of auxiliary pump P2]
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). 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.

  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).

  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).

Here, whether 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. 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 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.

  Next, the auxiliary pump control unit 312 drives the auxiliary pump P2 based on the rotation direction and number of rotations 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.

  Returning to FIG. 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).

[Failure detection processing]
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).
Next, 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).
Next, 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. 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 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).

  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.

  In addition, the auxiliary pump control unit 312 may control the auxiliary pump P2 based on the oil closing passage hydraulic pressure detected by the hydraulic pressure 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.

As described above, 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. 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 hydraulic pressure 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.

  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.

Further, in the on-vehicle hydraulic pressure 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.

Moreover, 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. 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 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. 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.

  Moreover, the vehicle-mounted hydraulic pressure supply apparatus 1 of this embodiment is provided with two check valves V1 of 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.

[Second Embodiment]
With reference to FIG. 7, an in-vehicle hydraulic pressure 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.

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.

  Further, the main pump P1A of the present 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.

  By configuring in this way, the in-vehicle hydraulic pressure supply device 1A can control the pulley width more precisely than in the first embodiment.

  Note that the in-vehicle hydraulic pressure supply device 1A may include the 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.

[Modification of Second Embodiment]
With reference to FIG. 8, an in-vehicle hydraulic pressure 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 hydraulic pressure 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.

  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.

  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.

[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 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.

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. 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 the closed 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.

Here, it is assumed that the upper 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.

  On the other hand, it is assumed that the upper unit 2 outputs a gear shift command for rapidly changing the pulley width. 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.

  In other words, the on-vehicle hydraulic pressure supply device 1C includes the bypass oil passage BP1 and the bypass valve VBP1, so that both improvement in controllability of the pulley width and improvement in control speed of the pulley width can be achieved.

[Modification of Third Embodiment]
With reference to FIG. 10, an in-vehicle hydraulic pressure 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 hydraulic pressure 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.

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. 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.

  Further, the in-vehicle hydraulic pressure supply device 1D includes the bypass oil passage BP2 and the auxiliary pump P3, so that the hydraulic oil discharge capacity can be shared between the auxiliary pump P2 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.

Further, since 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. .
In other words, 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. 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. .

  In addition, each embodiment described above and its modification examples can be combined as appropriate within a range that does not contradict each other.

  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)

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 for moving the hydraulic oil 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: 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. 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. 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. 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. 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. 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. 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. 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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