JP2013096295A - Oil supply device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply device which supplies oil to a hydraulic pressure control section and a lubricating section of an engine.SOLUTION: A pressure control valve 20 is provided to a branch oil path 3 which diverges from a main oil passage 2 that supplies oil of an oil pump P to the hydraulic pressure control section Ea and the lubricating section Eb. The pressure control valve 20 is provided with a valve element 22 on a valve body 21 in a slidable manner and is composed of a first spring 25 by which the valve element 22 activates the biasing force from the actuation starting point to the termination of the actuation and a second spring 26 by which the valve element 22 activates the biasing force from the middle of an open changing range to the termination of the actuation.

Description

  The present invention relates to an oil supply device, and more specifically, includes an oil passage system that supplies oil from an oil pump driven by an engine to a hydraulic control unit that controls the engine and a lubrication unit of the engine, and hydraulic control The present invention relates to an improvement in an oil supply device that controls oil pressure supplied to a lubricating part and a lubricating part by a control valve.

  As an oil supply device configured as described above, Patent Document 1 includes a priority valve (variable booster valve) to which oil is supplied from a discharge oil passage of an oil pump, and one of the two output ports of the priority valve is provided. A configuration in which a valve timing control device is connected and an engine lubrication device is connected to the other is shown. In the configuration of this Patent Document 1, the priority valve includes a valve body biased by a spring, and as the pressure of the oil supplied from the oil pump increases, the valve body is first actuated by the operation of the valve body. After that, when the oil pressure increases (when a predetermined value is reached), the oil supply to the engine lubricating device is started.

JP 2009-299573 A

  Consider an oil passage system that supplies oil from an oil pump driven by an engine to a valve opening / closing timing control device (specific example of an engine hydraulic control unit) and to a piston jet (specific example of an engine lubrication system). The hydraulic oil to be supplied to the valve timing control device requires a predetermined oil pressure even when the engine rotates at a relatively low speed. For this reason, an oil pump is used that can supply the required oil pressure even when the engine is rotating at a low speed.

  The piston jet is required to supply oil at the required oil pressure with the engine speed increased to some extent. Therefore, when the basic design of the oil supply device is performed to supply the oil with the required oil pressure to the valve timing control device when the engine rotates at a low speed, the piston jet is operated. For this reason, when the desired engine rotation speed is reached, the oil pressure may be excessively increased, and energy for driving the oil pump may be wasted.

  On the other hand, in Patent Document 1, the priority valve (variable booster valve) supplies oil to a valve opening / closing timing control device that requires a low oil pressure and an engine lubrication device that requires a higher oil pressure. Oil is not supplied until the required oil pressure is reached for each device. Therefore, similar to the above-mentioned problem, when the engine speed required to operate the engine lubrication device is reached, the oil pressure may increase too much, and the energy for driving the oil pump There was room for improvement from the viewpoint of wasted consumption.

  An object of the present invention is to provide an oil pump driven by an engine, to supply oil at an oil pressure required by the hydraulic control unit of the engine when the engine rotates at a low speed, and to increase the rotational speed of the engine. In this case, an oil supply device that supplies oil at an oil pressure required by the lubricating oil portion of the engine without excessively increasing the oil pressure is rationally configured.

  A feature of the present invention is that it includes an oil pump driven by an engine, and includes a main oil passage that supplies oil from the oil pump to a hydraulic control unit that controls the engine and a lubrication unit of the engine. A branch oil passage that branches from the passage, a pressure control valve that controls oil pressure acting on the main oil passage is provided in the branch oil passage, and the pressure control valve is a passage through which oil in the branch oil passage flows. A valve body having a space; a valve body that adjusts an amount of oil flowing in the flow path space by changing a flow path cross-sectional area of the flow path space by sliding movement within the valve body; and the flow path cross-sectional area. An urging mechanism that applies an urging force to the valve body in a direction to reduce it, and an oil pressure that acts on the branch oil passage is applied to the valve body from a direction opposite to the direction in which the urging force of the urging mechanism acts. The oil pressure acting part The valve body is configured to correspond to a limit area for maintaining the flow path cross-sectional area at a set value on the valve body closing side of the slide movement area, and a slide movement amount on the valve body opening side of the slide movement area. The valve body is configured to be operable to a change region where the flow path cross-sectional area changes, and the urging mechanism extends from the operation start end on the valve body closing side to the operation end on the valve body open side of the slide movement region. At least two springs: a first spring that applies a biasing force to the first spring and a second spring that applies a biasing force from the middle of the change region to the end of operation.

  According to this configuration, when the oil pressure supplied from the oil pump is low (the engine rotates at a low speed) and the valve body is in the restricted area of the slide movement area, the oil pressure acting on the main oil passage is the engine speed. It rises at a set ratio. Next, when the oil pressure rises (engine speed increases) and the valve body slides to reach the change area, the flow passage cross-sectional area increases, so the oil pressure acting on the main oil passage is The engine speed increases (slowly increases) at a ratio lower than the set ratio described above. Thereafter, in a state where the rotational speed of the engine further increases and the urging force of the first spring and the second spring acts on the valve body, the oil pressure acting on the main oil passage is set to a set ratio ( It does not need to match the set ratio described above). In other words, even when the rotational speed of the engine increases according to the set characteristic line, it is possible to increase the oil pressure acting on the main oil passage at the initial required characteristic to obtain a low oil pressure, Next, it is possible to obtain a high oil pressure by gradually increasing the required pressure and then increasing the required characteristics, and it is possible to suppress the engine speed when obtaining this high oil pressure.

An example of the specific configuration of the present invention is shown in FIG. 1, the movement form of the valve body 22 with the increase in the rotational speed of the engine E is shown in FIG. 3, and the change in the oil pressure supplied to the main oil passage is shown in FIG. ing. In this specific configuration, in a state where the engine E is rotating at a low speed (R0 to R1) and the valve element 22 is in the restricted region (FIG. 3A), along the first boosting straight line L1 with the origin “0” as a base point. Increase oil pressure. As the rotational speed of the engine E increases, the oil pressure further increases and reaches the change area where the valve element 22 opens the flow path space 21a. Of this change area, only the urging force of the first spring acts. In the region (FIG. 3C, R1 to R2), the oil pressure is increased along the second boosting straight line L2 that is more gently inclined than the first boosting straight line L1. Further, in the second change region (FIG. 3D, R3 to R4) in which the urging force of the first spring 25 and the second spring 26 acts in the change region, the rotational speed of the engine E increases. The oil pressure is increased along the fourth boosting straight line L4 that is steeper than the straight line L2. As a result, in the region where the rotational speed of the engine E is R1 to R4, the oil pressure with respect to the rotational speed exists in a region lower than the straight line obtained by extending the first boosting straight line L1, and the oil pressure acting on the oil pump P is reduced. Thus, the oil pump P is not wastefully driven in the work reduction area W shown in FIG.
Therefore, when the engine oil pressure controller supplies the oil pressure required by the engine oil pressure controller when the engine rotates at a low speed and the engine speed increases, the engine lubricating oil does not increase excessively. An oil supply device for supplying oil of an oil pressure required by the section is configured.

  According to the present invention, when the valve body is displaced toward the valve body opening side in the change region, the second spring applies an initial tension to the position where the urging force is applied by contacting the valve body. It may be provided in the state.

  According to this, since the second spring is provided with an initial tension applied by the restraining member, the oil pressure acting on the valve body is increased at the initial stage when the valve body is in contact with the second spring. However, the movement of the valve body can be suppressed, and the work reduction area is expanded to further suppress the wasteful driving of the oil pump.

  According to the present invention, the restraining member forms a contact portion with which the second spring abuts at one end, and prevents movement in the slide movement direction against the urging force of the second spring. When the valve body slides to the middle of the change region due to an increase in oil pressure, the valve body is moved to the valve body side. After the contact portion comes into contact, the valve body may be slidably supported with respect to the valve body so that the valve body can move integrally with the valve body.

  According to this, the second spring is disposed between the contact portion of the restraining member and the valve body side, and the initial tension is applied to the second spring by bringing the engagement portion of the restraining member into contact with the valve body side. It becomes possible to prepare in the state. Thereafter, after the valve body comes into contact with the restraining member due to an increase in oil pressure, the urging force of the second spring is applied to the valve body by sliding the valve body and the restraining member integrally. It is also possible.

  In the present invention, the pressure control valve slidably accommodates the valve body in a cylindrical internal space formed in the valve body, and the valve body is in the flow path space in the restricted region. It is also possible to have a configuration in which oil flows through an auxiliary flow path formed on the outer periphery of the valve body in a state where the valve is closed.

  According to this, in the state where the valve body is in the restricted region, it becomes possible for oil to flow in the auxiliary flow path formed annularly on the outer periphery of the valve body. For example, a groove or a through hole is formed in the valve body to assist A simple configuration is sufficient as compared with the configuration for forming the flow path.

It is a hydraulic circuit diagram of an oil supply apparatus. It is sectional drawing of a pressure control valve. It is a figure which shows the displacement of the valve body of a pressure control valve continuously. It is a graph which shows the relationship between the rotational speed of an engine, and the oil pressure controlled by a control valve. It is a disassembled perspective view of a pressure control valve.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[Basic configuration]
As shown in FIG. 1, a main oil passage 2 that supplies oil from an oil pump P driven by the engine E to a hydraulic control unit Ea of the engine E and a lubrication unit Eb of the engine E via an oil filter 1. And a branch oil passage 3 branched from the main oil passage 2, a relief valve 4 is provided in the main oil passage 2, and a pressure control valve 20 is provided in the branch oil passage 3 to constitute an oil supply device. Yes.

  This oil supply device is configured such that the oil pump P sucks and sends out oil (lubricating oil) of the oil pan of the engine E, and the hydraulic control unit Ea supplies the valve opening / closing timing control device 5 and the oil supplied thereto. And an electromagnetic control valve 6 for controlling the motor. Further, the lubricating part Eb is constituted by a piston jet 7 for lubricating the piston of the engine E, and T / supplies oil to the bearing part of the turbocharger in parallel with an oil passage system that supplies oil to the piston jet. A C bearing portion 8 is provided. Further, a main gallery 9 is connected to the downstream side of the pressure control valve 20 in the branch oil passage 3, and the main gallery 9 supplies oil to a crankshaft or the like of the engine E.

  The oil supplied to the control valve 6, the piston jet 7, the T / C bearing portion 8, and the main gallery 9 is collected in the drain and finally collected in the oil pan of the engine E.

  Although the structure of the valve opening / closing timing control device 5 is not shown in the drawing, it is provided at the end of a valve shaft (not shown) in order to control the opening / closing timing of at least one of the intake valve and the exhaust valve of the engine E. The opening / closing timing is changed by supplying and discharging oil through the control valve 6. The control valve is operated by a control signal from the ECU 10 that controls the engine E.

(Pressure control valve)
As shown in FIGS. 2 and 5, the pressure control valve 20 includes a valve main body 21 having a flow passage space 21 a through which oil from the branch oil passage 3 flows, and a flow passage by sliding relative to the valve main body 21. A valve body 22 that adjusts the amount of oil flowing in the flow path space by changing the cross-sectional area of the space 21 a and a cap body 23 that closes the open end of the valve body 21 are provided. The valve main body 21 is provided with an urging mechanism S that applies an urging force to the valve body 22 in the direction of reducing the flow path cross-sectional area.

  A branch oil passage 3 having a circular cross section is formed with respect to the housing 19, and a valve body 21 is provided in a state where the branch oil passage 3 is fitted in the housing 19 so as to be inserted in the middle of the branch oil passage 3. Oil flows from the left side to the right side in FIG.

  The urging mechanism S applies a urging force to the valve body 22 in the sliding movement region from the operation start end on the valve body closing side (the side closing the branch oil passage 3 and the upper side in FIG. 2) to the operation end on the valve body opening side. The first spring 25 is made up, and the valve body 22 is composed of a second spring 26 that applies a biasing force from the middle of the change region to the end of operation. The first spring 25 and the second spring 26 are compression-coil-type ones arranged on the coaxial core, and the second spring 26 is provided in a state in which an initial tension is applied while being compressed by a restraining member 27. It has been. The restraining member 27 is formed with an abutting portion 27a that abuts against the second spring 26 at one end portion and a hole-like portion 27b in which the first spring is disposed in a penetrating state, and projects outwardly at the other end portion. An engaging portion 27c is formed.

  The restraining member 27 is formed in a size that can be accommodated in the valve body 22, and the engagement portion 27 c is brought into contact with the end portion of the valve body 21, thereby preventing the movement by the urging force of the second spring 26, After the valve body 22 moves and comes into contact with the increase in pressure, the second spring 26 is compressed so that it can move integrally with the valve body 22 in the sliding movement direction.

  The biasing mechanism S may be configured by combining three or more springs in addition to the combination of the first spring 25, the second spring 26, and the two springs. By configuring the urging mechanism S by combining three or more springs in this way, oil can be efficiently supplied to three or more devices that require different oil pressures without wastefully driving the engine E. Can be performed. Further, when a plurality of springs are used as the urging mechanism, those having different spring constants may be used.

  Further, as the restraining member 27, a member having a function of restraining the second spring 26 may be used as the restraining member 27, such as a flexible thread-like material that holds the second spring 26 in a compressed state. . In particular, the constraining member 27 may be configured so that the position of the abutting member that abuts the second spring 26 can be adjusted in a screw manner. With this configuration, the initial tension of the spring can be adjusted. .

  The valve main body 21 is formed with a cylindrical internal space that slidably accommodates the valve body 22 and a pair of through holes 21b having a circular cross section in a posture orthogonal to the sliding direction of the valve body 22. The pair of through holes 21b are arranged at positions connecting the branch oil passage 3 and the flow passage space 21a. Inside the valve body 21, oil pressure acting from the through hole 21 b is applied to the pressure receiving surface 22 a of the valve body 22, and the valve body 22 is slid in the opening direction so that the oil pressure acting oil passage 21 c (of the oil pressure acting portion) An example) is formed.

  The cap body 23 has a configuration in which the cap body 23 is connected to the valve body 21 by a screw portion, and a drain hole 23a is formed in the bottom wall.

  The valve body 22 is a cylindrical member having a pressure receiving surface 22a formed at the protruding end, a protrusion 22b is formed at the center of the pressure receiving surface 22a, and an annular auxiliary flow path 22c is formed on the outer periphery. Has been. A housing space for the urging mechanism S is formed inside the valve body 22, and a first contact surface 22d on which the urging force of the first spring 25 acts is formed on the lower surface side of the pressure receiving surface 22a. A second abutting surface 22e on which the urging force of the second spring acts is formed inside 22.

  In particular, the flow passage cross-sectional area of the auxiliary flow passage 22c is set to an extremely small value as compared with the flow passage cross-sectional area of the through hole 21b of the valve body 21, and the amount of oil flowing through the branch oil passage 3 is limited. The oil pressure in the passage 2 is increased. The auxiliary flow path 22c may be configured by forming a through hole in the valve body 22. Further, the auxiliary flow path 22c may be formed in a bypass shape in the housing 19 so that the upstream side and the downstream side of the pressure control valve 20 in the branch oil path 3 communicate with each other.

  The first spring 25 is disposed at a position sandwiched between the first contact surface 22 d of the valve body 22 and the bottom wall of the cap body 23. The engaging portion 27c of the restraining member 27 is disposed at a position where the engaging portion 27c abuts against the end surface 21d of the valve body 21, and the lower surface of the abutting portion 27a of the restraining member 27 and the bottom wall of the cap body 23 with the second spring 26 compressed. The initial tension is applied to the second spring 26 by being arranged at a position sandwiched between the two springs 26.

[Operation form of pressure control valve]
FIG. 3 shows the operating position of the valve element 22 of the pressure control valve 20 according to a change in the rotational speed (the number of revolutions per unit time) of the engine E. The change in the oil pressure in the main oil passage 2 with respect to the rotational speed of the engine E is shown in FIG. This is shown graphically in FIG. In the pressure control valve 20, the projecting portion 22 b of the valve body 22 abuts on the inner surface of the valve body 22 by the urging force of the first spring 25 in a state where the engine E is stopped, and this contact position is the operation of the valve body 22. This is the starting point (FIGS. 2 and 3A). At the start of this operation, a gap is formed between the pressure receiving surface 22a of the valve body 22 and the inner wall of the valve body 21 (inner wall at the upper position of the valve body 21 in FIG. 2), and the branched oil path 3 connected to the main oil path 2 Is in a state where it can act on the pressure receiving surface 22a from the oil pressure acting oil passage 21c.

  When the rotational speed of the engine E increases after the engine E starts, the oil pressure acting on the pressure receiving surface 22a of the valve body 22 rises from the oil pressure acting oil passage 21c and resists the urging force of the first spring 25. Then, the valve body 22 operates to the valve body open side (the lower side in FIGS. 2 and 3) (FIGS. 3A and 3B).

  The region from the operation starting end shown in FIG. 3A to the position where the pressure receiving surface 22a reaches the opening edge of the through hole 21b of the valve body 21 (FIG. 3B) is referred to as a restriction region. In this restricted region, since the valve body 22 closes the flow path space 21a, oil flows into the auxiliary flow path 22c formed on the outer periphery of the valve body 22, and the oil pressure in the main oil path 2 is the rotational speed of the engine E. In accordance with the first boosting straight line L1 starting from the origin “0” (0 to R1 in FIG. 4).

  Next, when the rotational speed of the engine E further increases, the pressure receiving surface 22a of the valve body 22 is displaced to a position where the through hole 21b of the valve body 21 is opened against the urging force of the first spring 25 ( FIG. 4 (c)).

  Thus, the region where the valve element 22 operates in a state of opening the flow passage space 21a as the oil pressure increases is the change region. In particular, a region in which only the urging force of the first spring 25 acts is referred to as a first change region, and a region in which the urging force of the first spring 25 and the second spring 26 acts is referred to as a second change region. It is called.

  When the valve body 22 is operated in the first change region, the main oil oil enters the state in which the oil pressure in the main oil passage 2 is released to the branch oil passage 3 in order to open a part of the flow passage space 21a of the valve body 21. The oil pressure in the path 2 gradually rises along the second boosting straight line L2 having a gentler slope than the first boosting straight line L1 (R1 to R2 in FIG. 4). Further, when the rotational speed of the engine E reaches R1, it is possible to supply the oil with the oil pressure necessary for the valve opening / closing timing control device 5.

  Next, when the oil pressure rises along the second pressure increase line L2 and the flow path cross-sectional area reaches a suppression point T that suppresses the pressure increase, the oil pressure is set to the origin “0” in proportion to the rotational speed of the engine E. It increases along the third boosting straight line L3 that is a part of the virtual straight line X that is the starting point (R2 to R3 in FIG. 4).

  In the change region, the valve body 22 operates in the opening direction in proportion to the increase in the oil pressure, and the flow path cross-sectional area is increased, but the flow path cross-sectional area determined by the operating position of the valve body 22 and the valve body When the relationship with the area of the pressure receiving surface 22a of 22 reaches a predetermined ratio, a suppression point T at which the oil pressure is suppressed is reached regardless of the displacement of the valve body 22. After reaching the suppression point T, the valve body 22 further operates to reach an action point U ((d) in FIG. 4) where the action of the urging force of the second spring 26 starts.

  A third boosted straight line L3 is linearly formed between the suppression point T and the action point U, and the third boosted straight line L3 is a part of the virtual straight line X starting from the origin “0” as described above. Yes, as the rotational speed of the engine E increases, the oil pressure increases along the third pressure increase line L3. In addition, after the valve body 22 reaches the action point U, the valve body 22 operates in the second change region. In the second change region, the initial tension is applied to the second spring 26, so that the valve body 22 is not displaced even when the oil pressure rises (FIG. 4D). The oil pressure rises according to a fourth boosting straight line L4 that is steeper than the third boosting straight line (R3 to R4 in FIG. 4).

  When the rotational speed of the engine E further increases, the valve element 22 operates against the urging force of the first spring 25 and the second spring 26. For this reason, the oil pressure in the main oil passage 2 is released to the branch oil passage 3, and the oil pressure in the main oil passage 2 gradually rises along the fifth pressure increase line L5 having a gentler slope than the fourth pressure increase line L4 ( R4 to R5 in FIG. In addition, when the rotational speed of the engine E reaches R4, it is possible to supply the oil having the necessary oil pressure to the piston jet 7 and the T / C bearing portion 8.

  When the rotational speed of the engine E further increases and the valve body 22 reaches the end of operation, the operation of the valve body 22 is blocked (e). As a result, the oil pressure is proportional to the rotational speed of the engine E and increases along the sixth boosting straight line L6 that is part of the virtual straight line X starting from the origin “0” (R5 to R6 in FIG. 4).

  Thereafter, when the rotational speed of the engine E further increases, the relief valve 4 described above is opened to reach the relief region L7, the increase in the oil pressure in the main oil passage 2 is restricted, and the oil pump P and the hydraulic equipment are Protected (R6- in FIG. 4).

[Operation / Effect of Embodiment]
With such a configuration, even when the engine E rotates at a low speed, it is possible to supply oil with an increased oil pressure to the main oil passage 2, and when the rotation speed of the engine E increases and reaches R1 It is possible to supply the oil having the required oil pressure to the hydraulic control unit Ea. Further, when the rotational speed of the engine E reaches R4, it becomes possible to supply the oil having the required oil pressure to the lubricating portion Eb.

  In particular, for example, when the branch oil passage 3 is not provided with the pressure control valve 20 but is provided with an orifice having a channel cross-sectional area equal to that of the auxiliary channel 22c, the oil pressure is increased along the above-described first pressure increase line L1. To rise. On the other hand, by providing the pressure control valve 20 of the present invention with respect to the branch oil passage 3, in the region where the rotational speed of the engine E is R1 to R4, the oil pressure with respect to the rotational speed is a straight line obtained by extending the first boosted straight line L1. The oil pressure existing in the lower region and acting on the oil pump P is reduced. That is, even when the rotational speed (R1) of the engine E for obtaining the oil pressure required by the hydraulic control unit Ea is set to a relatively low value, the engine E that obtains the oil pressure required by the lubrication unit Eb. It is possible to set the rotational speed of the engine E that requires the most lubrication of the piston of the engine E without causing the disadvantage that the rotational speed (R4) is displaced to the low speed side.

  Therefore, it is not necessary to drive the oil pump P with the oil pressure in the work reduction region W formed on the higher pressure side than the second boost curve L2 to the fourth boost curve L4 and below the first boost line L1. Energy consumption corresponding to the reduction area W can be suppressed. Incidentally, since the amount of oil supplied from the oil pump P is directly proportional to the oil pressure, the oil pressure is reduced by releasing a part of the oil by the pressure control valve 20, and the oil pressure acting on the oil pump P is reduced. Thus, the amount of oil delivered from the oil pump P is reduced, and as a result, energy consumption is suppressed.

  In particular, in the pressure control valve 20 of the present invention, the suppression point T and the action point U can be arbitrarily set at the design stage of the pressure control valve 20, and the setting of the suppression point T and the action point U is possible. The rotational speed (R4) of the engine E that obtains the oil pressure required by the lubricating part Eb can be reduced to a required value, and the stepless driving of the oil pump P can be satisfactorily suppressed.

  INDUSTRIAL APPLICABILITY The present invention can be used for all oil supply devices that supply oil from an oil pump driven by an engine to a hydraulic control unit and a lubrication unit.

2 Main oil path 3 Branch oil path 20 Pressure control valve 21 Valve body 21a Flow path space 21c Oil pressure acting part (oil pressure acting oil path)
22 Valve body 22c Auxiliary flow path 25 1st spring 26 2nd spring 27 Restraining member E Engine Ea Hydraulic control part Eb Lubrication part P Oil pump S Energizing mechanism

Claims (4)

A branch oil that includes an oil pump driven by an engine, includes a main oil passage that supplies oil from the oil pump to a hydraulic control unit that controls the engine and a lubrication unit of the engine, and branches from the main oil passage Provided with a pressure control valve for controlling the oil pressure acting on the main oil passage in the branch oil passage,
The pressure control valve has a valve main body having a flow passage space through which the oil in the branch oil passage flows, and changes the cross-sectional area of the flow passage space by sliding movement within the valve main body to the flow passage space. A valve body that adjusts the amount of flowing oil, an urging mechanism that applies an urging force to the valve body in a direction that reduces the cross-sectional area of the flow path, and an oil pressure that acts on the branch oil passage is applied to the valve body. An oil pressure acting part that acts from the direction opposite to the direction of action of the urging force of the urging mechanism,
The valve body has a restriction area for maintaining the flow path cross-sectional area at a set value on the valve body closing side of the slide movement area, and the flow path breakage corresponding to the slide movement amount on the valve body opening side of the slide movement area. It is configured to operate freely in the change area where the area changes,
The biasing mechanism includes a first spring that applies a biasing force to the valve body from an operation start end on the valve body closing side of the slide movement region to an operation end on the valve body release side, and the middle from the middle of the change region. An oil supply device comprising at least two springs, a second spring for applying a biasing force to the end of operation.   When the valve body is displaced to the valve body opening side in the change region, the second spring is provided in a state where an initial tension is applied by a restraining member at a position where the valve body abuts against the valve body and applies a biasing force. The oil supply apparatus according to claim 1.   The restraining member forms a contact portion with which the second spring comes into contact at one end, and prevents the movement in the sliding direction against the urging force of the second spring. When the valve body slides to the middle of the change region due to an increase in oil pressure, the contact portion is formed on the valve body. 3. The oil supply device according to claim 2, wherein the valve body is slidably supported with respect to the valve body so that the valve body can move integrally with the valve body in contact with the valve body.   The pressure control valve slidably accommodates the valve body with respect to a cylindrical internal space formed in the valve body, and the valve body closes the flow path space in the restriction region. The oil supply device according to any one of claims 1 to 3, wherein the oil supply device has a configuration in which oil flows in an auxiliary flow path formed on an outer periphery of the valve body in a certain state.

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