JP2012007543A - Hydraulic pressure control apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic pressure control apparatus that can control a hydraulic pressure according to an engine operating state or an oil temperature without the need of OSV.SOLUTION: The hydraulic control apparatus includes: a pump 1 that is driven by the rotation of an engine and that discharges an oil; a valve opening and closing timing control device 2; a first flow passage 11A that connects the pump 1 with the valve opening and closing timing control device 2; a second flow passage 13 that branches from the first flow passage 11A and supplies the oil to a predetermined part 8 other than the valve opening and closing timing control device; a flow area adjustment part 3 that is disposed in the second flow passage 13 and that increases the flow passage area of the second flow passage 13 by the increases of the hydraulic pressure at an upside of the flow passage and decreases the flow passage area by the decrease of the hydraulic pressure; and a temperature-sensing control part 4 that is variable depending on a temperature condition and that controls an operation for reducing the flow area out of the operations of the flow area adjustment part 3 when the temperature of the oil exceeds a preset one.

Description

  The present invention relates to a hydraulic control device that controls the hydraulic pressure of oil that is discharged from a pump driven by the rotation of an engine and supplied to each part of the engine.

  In the engine, appropriate hydraulic pressure and oil amount differ for each part of the engine depending on the operating state of the engine and the oil temperature. For example, since the oil temperature immediately after starting the engine is generally low, its viscosity is high and the oil pressure is relatively high. Further, it is generally unnecessary to operate the valve timing control device immediately after the engine is started. For this reason, if oil is supplied to the valve timing control device immediately after the engine is started, the pump does unnecessary work. Therefore, immediately after the engine is started, oil should be preferentially supplied to a predetermined portion other than the valve timing control device, that is, the main gallery, so as not to unnecessarily increase the work volume of the pump.

  In addition, since the valve opening / closing timing control device has a slight gap between the parts, when the oil temperature rises excessively and the oil viscosity becomes considerably low, oil leaks out (bleeds out) from this minute gap. )Sometimes. If oil leaks (exudes), the hydraulic pressure cannot be efficiently applied to the valve opening / closing timing control device, and the displacement of the relative rotation phase by the valve opening / closing timing control device may not be performed quickly. In such a state, in order to obtain the effect by the control of the valve opening / closing timing control device, the pump must be actively operated, and conversely, the fuel consumption of the engine may be deteriorated.

  Conventionally, as described in Patent Literature 1, a pump that is driven by engine rotation to discharge oil (in the literature, “oil pump”), and a driving-side rotary member that rotates synchronously with the crankshaft (in literature, “external” Rotor ”), and a driven-side rotating member (in the literature,“ internal rotor ”) that is arranged coaxially with the driving-side rotating member and rotates synchronously with the camshaft, Hydraulic control including a valve opening / closing timing control device that controls the valve opening / closing timing by displacing the rotation phase by supplying or discharging oil, and an engine lubricating device that lubricates the main gallery using oil supplied by a pump. There was a device.

  The invention described in Patent Document 1 branches the flow path downstream of the pump into a flow path to the valve opening / closing timing control device and a flow path to the engine lubrication device, and a priority valve is provided at the branch portion. The priority valve can be controlled by switching a dedicated OSV (oil switching valve, “open / close valve” in the literature), and the flow path to the main gallery can be narrowed down. As a result, the hydraulic pressure and oil amount to the valve opening / closing timing control device and the hydraulic pressure and oil amount to the main gallery are adjusted according to the operating state of the engine and the oil temperature without providing an electric pump or the like that assists the pump. It is possible to control.

JP 2009-299573 A

  However, the invention described in Patent Document 1 needs to be equipped with OSV to control the priority valve, and there is a possibility that it may lead to an increase in cost due to the necessity of other cord arrangement, oil passage formation, and the like.

  An object of the present invention is to provide a hydraulic control device that does not require a dedicated OSV and can perform hydraulic control according to the operating state of the engine and the oil temperature.

  The first characteristic configuration of the hydraulic control device according to the present invention includes a pump that is driven by engine rotation to discharge oil, a drive-side rotating member that rotates synchronously with a crankshaft, and a coaxial with the drive-side rotating member. A valve opening / closing timing control device that has a driven side rotating member that is arranged and rotates synchronously with the camshaft, and that displaces a relative rotational phase of the driven side rotating member with respect to the driving side rotating member by supplying or discharging oil; A first flow path communicating the pump and the valve opening / closing timing control device; a second flow path branched from the first flow path and supplying oil to a predetermined portion other than the valve opening / closing timing control device; A flow path area adjusting unit that is provided in two flow paths, increases the flow area of the second flow path by increasing the hydraulic pressure on the upper side of the flow path, and decreases the flow path area by decreasing the hydraulic pressure; And a temperature-sensitive control unit that regulates an operation of reducing the flow channel area among operations of the flow channel area adjustment unit when the oil temperature is higher than a predetermined set temperature, and It is in the point with.

  According to this configuration, the flow channel area adjusting unit adjusts the flow channel area of the second flow channel by the hydraulic pressure on the upper side of the flow channel than the flow channel area adjusting unit, that is, the hydraulic pressure of the oil flowing through the second flow channel. It is adjustable. In addition, the flow channel area adjusting unit operates to increase the flow channel area when the hydraulic pressure increases, and to decrease the flow channel area when the hydraulic pressure decreases. Therefore, when the hydraulic pressure is increased immediately after the engine is started, the second flow path is opened by the flow path area adjusting unit, and the oil is preferentially supplied to a predetermined portion other than the valve opening / closing timing control device, that is, the main gallery. As a result, unnecessary work of the pump for the valve timing control device can be reduced.

  Further, when the oil temperature becomes higher than the set temperature, the operation of reducing the flow channel area among the operations of the flow channel area adjusting unit is regulated by the temperature control unit. That is, the minimum flow rate of the second flow path when the oil temperature becomes higher than the set temperature can be freely defined, and the oil can be preferentially supplied to the main gallery. Therefore, even if the oil viscosity becomes low and oil leakage occurs in the valve opening / closing timing control device, the oil can be supplied to the main gallery in preference to the valve opening / closing timing control device, causing the pump to perform useless work. You can avoid that.

  As described above, with this configuration, it is possible to provide a hydraulic control device that can perform hydraulic control according to the operating state of the engine and the oil temperature without providing a dedicated OSV.

  In a second characteristic configuration of the hydraulic control device according to the present invention, the temperature-sensitive control unit is configured such that when the temperature of the oil becomes higher than the set temperature, the channel area adjusting unit is disposed in the entire second channel. It is in the point which controls by displacing to the state to open.

  With this configuration, when the oil temperature becomes higher than the set temperature, the second flow path is fully opened, so that the oil is supplied to the main gallery to the maximum extent. As a result, the work of the pump with respect to the valve timing control device can be minimized.

  A third characteristic configuration of the hydraulic control device according to the present invention is that the temperature-sensitive control unit includes a thermo wax that expands due to a temperature change.

  As in this configuration, when the temperature-sensitive control unit is displaced by the thermowax, for example, the configuration is not complicated and there are few failures compared to an electrical configuration such as a temperature sensor and an electric actuator. Further, since it depends on the material properties, the displacement is unambiguous to some extent, and the displacement is highly reliable despite the simple configuration.

  According to a fourth characteristic configuration of the hydraulic control device according to the present invention, the flow channel area adjustment unit has a cylindrical shape in which an opening capable of adjusting the flow channel area is provided on an outer peripheral wall, A spool capable of receiving oil in the second flow path, a cup-shaped retainer that slidably holds an end of the spool on the side away from the second flow path, and the spool at the bottom of the retainer An urging member that presses, and the spool includes a pressure receiving portion that allows the pressure of oil flowing in from the opening to act in a protruding direction from the retainer, and the temperature-sensitive control portion includes the spool of the bottom portion. Is in the point acting on the opposite surface.

  According to this configuration, the spool includes the opening capable of adjusting the flow passage area of the second flow passage, and the oil in the second flow passage flowing into the cylindrical shape of the spool from the opening acts on the pressure receiving portion. When the hydraulic pressure acting on the pressure receiving portion increases, the spool is urged from the retainer in the protruding direction. Since the retainer slidably holds the end of the spool on the side away from the second flow path, as the hydraulic pressure of the second flow path increases, the spool moves in the protruding direction from the retainer, that is, in the second flow path. Protrusively. That is, for example, when the opening is configured to open the second flow path as the spool protrudes from the second flow path, the flow area of the second flow path is adjusted by the oil pressure itself of the oil flowing through the second flow path. Is possible.

  Further, since the temperature-sensitive control unit is configured to act on the surface of the retainer opposite to the spool, when the oil temperature becomes higher than a predetermined temperature, the temperature-sensitive control unit is displaced and the retainer Is brought closer to the second flow path. As a result, the operation of retracting the spool from the second flow path is restricted by the retainer, and the operating range of the spool is limited. As a result, the flow area of the second flow path due to the opening is not reduced below a certain value, and the flow rate of the second flow path can be secured above a certain value.

  In this way, appropriate hydraulic control is possible simply by providing the flow path area adjusting portion with a spool, retainer, and biasing member having a simple shape.

  A fifth characteristic configuration of the hydraulic control device according to the present invention is that the temperature-sensitive control unit is displaced according to the temperature of oil in the second flow path.

  In this configuration, the temperature sensing control unit that adjusts the flow channel area of the second flow channel is configured to be displaced based on the oil temperature of the second flow channel itself. Therefore, it is possible to control the hydraulic pressure appropriately.

These are figures which show the whole structure of the hydraulic control apparatus which concerns on this invention. These are sectional drawings which show the state of the hydraulic control apparatus immediately after an engine is started in the state where oil temperature is lower than 1st temperature T1. These are sectional views showing the state of the hydraulic control device when the oil temperature is between the first temperature T1 and the second temperature T2 and the engine speed is low. These are sectional drawings which show the state of the hydraulic control apparatus in the middle of the oil temperature being the temperature between 1st temperature T1 and 2nd temperature T2, and the engine speed increasing. These are figures which show the state of a hydraulic-control apparatus when oil temperature is the temperature between 1st temperature T1 and 2nd temperature T2, and the rotation speed of an engine is high. These are figures which show the state of a hydraulic control apparatus when oil temperature is higher than 2nd temperature T2. These are figures which show the relationship between oil temperature and whether it is the state which can operate | move the flow-path area adjustment part. (A) is a figure which shows the relationship between an engine speed when oil temperature is the temperature between 1st temperature T1 and 2nd temperature T2, and the oil pressure of each part, (b) is oil temperature. It is a figure which shows the relationship between an engine speed when it is lower than 1st temperature T1, or when it is higher than 2nd temperature T2, and the hydraulic pressure of each part.

  An embodiment in which the present invention is applied as a hydraulic control device for an automobile engine will be described with reference to FIGS. In the present embodiment, the valve opening / closing timing control device will be described as a valve opening / closing timing control device on the intake valve side.

1. Overall Configuration As shown in FIG. 1, the hydraulic control device includes an oil pump 1 as a “pump” driven by the rotation of the engine as an “engine”, and a valve opening / closing timing for displacing the relative rotational phase by supplying or discharging oil. And a control device 2. The valve opening / closing timing control device 2 operates by supplying and discharging oil under the control of an OCV (oil control valve) 5. The oil pump 1 and the OCV 5 are connected by a discharge oil passage 11A as a “first flow passage”, and the valve opening / closing timing control device 2 and the OCV 5 are connected by an advance passage 12A and a retard oil passage 12B. From the discharge oil passage 11A, a lubricating oil passage 13 is branched as a “second flow passage” for supplying oil to the main gallery 8 as “a predetermined portion other than the valve opening / closing timing control device”. The lubricating oil passage 13 is provided with a flow passage area adjusting section 3 that adjusts the flow passage area. Each oil passage is formed in an engine cylinder case or the like.

2. Oil pump The oil pump 1 is mechanically driven by the transmission of the rotational driving force of the crankshaft to discharge oil. As shown in FIG. 1, the oil pump 1 sucks the oil stored in the oil pan 1a and discharges the oil to the discharge oil passage 11A. An oil filter 6 is disposed in the discharge oil passage 11A and filters small dust and sludge that has not been filtered by the oil strainer. The oil filtered by the oil filter 6 is supplied to the valve opening / closing timing control device 2 and the main gallery 8. The main gallery 8 indicates the entire sliding member such as a piston, a cylinder, a crankshaft bearing, etc. (not shown).

  The oil discharged from the valve opening / closing timing control device 2 is returned to the oil pan 1a via the OCV 5 and the return oil passage 11B. The oil supplied to the main gallery 8 is collected in the oil pan 1a through covers (not shown). Further, oil leaked from the valve opening / closing timing control device 2 is also collected in the oil pan 1a through the covers.

3. Valve opening / closing timing control device [Overview]
As shown in FIG. 1, the valve opening / closing timing control device 2 is disposed on a coaxial core X with respect to a housing 21 as a “drive-side rotating member” that rotates synchronously with a crankshaft of an engine (not shown). And an internal rotor 22 as a “driven rotation member” that rotates in synchronization with the camshaft 101. As shown in FIG. 2, the valve opening / closing timing control device 2 can restrain the relative rotational phase of the internal rotor 22 relative to the housing 21 to the most retarded angle phase by restraining the relative rotational movement of the internal rotor 22 relative to the housing 21. A lock mechanism 27 is provided.

[Housing and internal rotor]
As shown in FIG. 1, the internal rotor 22 is assembled at the tip of the camshaft 101. The housing 21 includes a front plate 21a opposite to the side to which the camshaft 101 is connected, an external rotor 21b integrally provided with a timing sprocket 21d, a rear plate 21c on the side to which the camshaft 101 is connected, It has. The external rotor 21b is externally mounted on the internal rotor 22, and is sandwiched between the front plate 21a and the rear plate 21c, and the front plate 21a, the external rotor 21b, and the rear plate 21c are fastened by bolts.

  When the crankshaft is rotationally driven, the rotational driving force is transmitted to the timing sprocket 21d via the power transmission member 102, and the housing 21 is rotationally driven in the rotational direction S shown in FIG. As the housing 21 rotates, the internal rotor 22 rotates in the rotational direction S to rotate the camshaft 101, and the cam provided on the camshaft 101 pushes down the intake valve of the engine to open it.

  As shown in FIG. 2, three fluid pressure chambers 24 are formed by the outer rotor 21 b and the inner rotor 22. A plurality of vanes 22 a projecting radially outward are formed on the inner rotor 22 so as to be positioned in the fluid pressure chamber 24 and spaced apart from each other along the rotational direction S. The fluid pressure chamber 24 is partitioned into an advance chamber 24a and a retard chamber 24b along the rotation direction S by a vane 22a.

  As shown in FIGS. 1 and 2, an advance chamber communication passage 25 is formed in the internal rotor 22 and the camshaft 101 so as to communicate with each advance chamber 24a. Further, a retard chamber communication passage 26 is formed in the internal rotor 22 and the camshaft 101 so as to communicate with each retard chamber 24b. As shown in FIG. 1, the advance chamber communication passage 25 is connected to the advance oil passage 12 </ b> A communicating with the OCV 5. The retard chamber communication passage 26 is connected to the retard oil passage 12B that communicates with the OCV 5.

  As shown in FIG. 1, a torsion spring 23 is provided across the inner rotor 22 and the front plate 21a. The torsion spring 23 biases the internal rotor 22 toward the advance side so as to resist the average displacement force in the retard direction based on the cam torque fluctuation. Thereby, it is possible to smoothly and quickly displace the relative rotation phase in the advance direction S1 described later.

[Lock mechanism]
The lock mechanism 27 restrains the relative rotation phase to the most retarded angle phase by holding the housing 21 and the internal rotor 22 at a predetermined relative position in a situation where the oil pressure of the oil is not stable immediately after the engine is started. As a result, it is possible to start the engine properly, and the internal rotor 22 does not flutter due to the displacement force based on the cam torque fluctuation at the time of engine start or idling operation.

  As shown in FIG. 2, the lock mechanism 27 includes two plate-like lock members 27 a, a lock groove 27 b, and a lock mechanism communication path 28. The lock groove 27b is formed on the outer peripheral surface of the inner rotor 22, and has a certain width in the relative rotation direction. The lock member 27a is disposed in a housing portion formed in the external rotor 21b, and can be moved in and out in the radial direction with respect to the lock groove 27b. The lock member 27a is constantly urged by a spring toward the radially inner side, that is, the lock groove 27b side. The lock mechanism communication path 28 connects the lock groove 27 b and the advance chamber communication path 25. Accordingly, when oil is supplied to the advance chamber 24a, oil is also supplied to the lock groove 27b, and when oil is discharged from the advance chamber 24a, the oil is also discharged from the lock groove 27b.

  When oil is discharged from the lock groove 27b, each lock member 27a can protrude into the lock groove 27b. As shown in FIG. 2, when both the lock members 27a enter the lock grooves 27b, the lock members 27a are simultaneously locked to both ends in the circumferential direction of the lock grooves 27b. As a result, the relative rotational movement of the inner rotor 22 with respect to the housing 21 is restricted, and the relative rotational phase is restricted to the most retarded phase. When oil is supplied to the lock groove 27b, as shown in FIG. 3, both lock members 27a are retracted from the lock groove 27b to release the restriction on the relative rotation phase, and the internal rotor 22 is relatively rotatable. Hereinafter, a state in which the lock mechanism 27 restrains the relative rotation phase to the most retarded phase is referred to as a “lock state”. A state in which the locked state is released is referred to as a “lock released state”.

[OCV]
The OCV 5 is an electromagnetic control type, and can control the supply and discharge of oil to the advance chamber communication passage 25 and the retard chamber communication passage 26 and the supply amount holding. The OCV 5 is configured as a spool type, and operates based on control of the amount of power supplied by the ECU 7 (engine control unit). By OCV5, oil supply to the advance oil passage 12A, oil discharge from the retard oil passage 12B, oil discharge from the advance oil passage 12A, oil supply to the retard oil passage 12B, advance oil passage 12A and retard Control such as oil supply / discharge interruption to the square oil passage 12B is possible. Control for supplying oil to the advance oil passage 12A and discharging oil from the retard oil passage 12B is "advance control". When the advance angle control is performed, the vane 22a moves relative to the external rotor 21b in the advance direction S1, and the relative rotation phase is displaced toward the advance side. Control for discharging oil from the advance oil passage 12A and supplying oil to the retard oil passage 12B is "retard control". When the retard control is performed, the vane 22a relatively rotates in the retard direction S2 with respect to the external rotor 21b, and the relative rotation phase is displaced to the retard side. If the control for shutting off the oil supply / discharge to the advance oil passage 12A and the retard oil passage 12B is performed, the anti-rotation phase can be maintained at an arbitrary phase.

  Note that the advance angle control is enabled when the OCV 5 is supplied with power, and the retard angle control is enabled when the power supply to the OCV 5 is stopped. Moreover, OCV5 sets an opening degree by adjusting the duty ratio of the electric power supplied to an electromagnetic solenoid. Thereby, fine adjustment of the supply and discharge amount of oil is possible.

  In this way, by controlling the OCV 5, oil is supplied to, discharged from, or held in the advance angle chamber 24a and the retard angle chamber 24b, and the oil pressure of the oil acts on the vane 22a. In this way, the relative rotational phase is displaced in the advance angle direction or the retard angle direction, or held at an arbitrary phase.

5). Operation of the valve opening / closing timing control device The operation of the valve opening / closing timing control device 2 will be described with reference to FIGS. With the above-described configuration, the internal rotor 22 can smoothly rotate relative to the housing 21 around the axis X within a certain range. A certain range in which the housing 21 and the internal rotor 22 can move relative to each other, that is, a phase difference between the most advanced angle phase and the most retarded angle phase corresponds to a range in which the vane 22 a can be displaced inside the fluid pressure chamber 24. . It is to be noted that the retardation angle chamber 24b has the largest volume in the most retarded phase, and the advance angle chamber 24a has the largest volume in the most advanced angle phase.

  Although not shown, a crank angle sensor that detects the rotation angle of the crankshaft of the engine and a camshaft angle sensor that detects the rotation angle of the camshaft 101 are provided. The ECU 7 detects the relative rotation phase from the detection results of the crank angle sensor and the camshaft angle sensor, and determines which phase the relative rotation phase is in. Further, the ECU 7 is formed with a signal system for acquiring ignition key ON / OFF information, information from an oil temperature sensor for detecting the oil temperature, and the like. Further, in the memory of the ECU 7, control information on the optimum relative rotational phase corresponding to the operating state of the engine is stored. The ECU 7 controls the relative rotation phase from the information on the operation state (engine rotation speed, cooling water temperature, etc.) and the control information described above.

  Before the engine is started, as shown in FIG. When an ignition key (not shown) is turned on, cranking is started, and the engine is started in a state where the relative rotational phase is constrained to the most retarded phase. And it transfers to idling driving | operation and a catalyst warm-up is started. When the catalyst warm-up is completed and an accelerator (not shown) is depressed, power is supplied to the OCV 5 and the advance angle control is performed to displace the relative rotation phase in the advance direction S1. As a result, oil is supplied to the advance chamber 24a and oil is also supplied to the lock groove 27b. As shown in FIG. 3, the lock member 27a is retracted from the lock groove 27b to be unlocked. In the unlocked state, the relative rotational phase is freely displaceable, and is displaced to the states shown in FIGS. 4 and 5 in accordance with the oil supply to the advance chamber 24a. Thereafter, the relative rotation phase is displaced between the most advanced angle phase and the most retarded angle phase in accordance with the engine load, the rotation speed, and the like.

  Since the idling operation is performed before the engine is stopped, the relative rotation phase becomes the most retarded phase. At this time, at least the retard-side lock member 27a enters the lock groove 27b. When the ignition key is turned OFF, the internal rotor 22 flutters due to the cam torque variation, and the lock member 27a on the advance side also enters the lock groove 27b to be locked. Therefore, the next engine start can be suitably performed.

6). As shown in FIG. 2, the flow path area adjusting unit 3 is connected to the spool sliding part 35 orthogonal to the lubricating oil path 13 and the spool sliding part 35, and the spool sliding part 35. In contrast, a retainer accommodating portion 36 formed on the opposite side of the lubricating oil passage 13 is provided. The spool sliding portion 35 is provided with a spool 31 that is slidable along the shape of the spool sliding portion 35 and that can be withdrawn from and retracted from the lubricating oil passage 13. The retainer accommodating portion 36 is provided with a retainer 32 that can slide along the shape of the retainer accommodating portion 36.

  The spool 31 is a cylindrical member, and has a flange portion 31c projecting radially outward on the outer periphery of one end. Four cylindrical openings 31a as "openings" that penetrate the wall in a direction perpendicular to the sliding direction of the spool 31 are formed in the circumferential direction at equal intervals. . The outer diameter of the wall portion of the spool 31 is substantially equal to the inner diameter of the spool sliding portion 35.

  The retainer 32 is a cylindrical cup-shaped member having a wall portion raised in the vertical direction from the outer periphery of the bottom portion 32a. The outer diameter of the wall portion of the retainer 32 is substantially equal to the inner diameter of the retainer housing portion 36. The inner diameter of the wall portion of the retainer 32 is substantially equal to the outer diameter of the flange portion 31c. The retainer 32 is externally mounted on the spool 31 so that the flange 31c side of the spool 31 is inserted and held. A spring 34 as an “urging member” is interposed between the wall portion of the spool 31 and the wall portion of the retainer 32, and the C ring 33 is fitted into a groove formed on the inner peripheral surface of the wall portion of the retainer 32. Thus, the spring 34 is sandwiched between the lower surface of the C-ring 33 and the upper surface of the flange portion 31c.

  Thereby, the spool 31 and the retainer 32 can slide relative to each other. Also, the bottom surface 31d is pressed against the inner bottom surface 32b by the spring 34, and the spool 31 and the retainer 32 are urged in directions that are not separated from each other. That is, the spool 31 is urged in the direction of retreating from the lubricating oil passage 13. Hereinafter, the direction in which the spool 31 retreats from the lubricating oil passage 13 is referred to as a “retraction direction”, and the direction in which the spool 31 protrudes into the lubricating oil passage 13 is referred to as a “protruding direction”.

  In a state where the spool 31, the retainer 32, and the spring 34 are assembled to each other, the spool sliding portion 35 and the retainer accommodating portion 36 are arranged so that the opening portion 31a always communicates at least the upstream side and the downstream side of the lubricating oil passage 13. It is arranged. Since the oil in the lubricating oil passage 13 enters the inside of the spool 31 from the opening 31a, the oil pressure of the lubricating oil passage 13 acts on the spool 31 and the retainer 32.

  In the engine stopped state, that is, in the initial state, both the spool 31 and the retainer 32 are retracted from the lubricating oil passage 13 by their own weight as in the state shown in FIG.

  Of the spool 31, the opening 31 a, the tip 31 b, and the bottom surface 31 d receive hydraulic pressure in a direction in which the spool 31 is retracted. Since the opening 31a receives pressure both in the protruding direction and in the retracting direction, the action of the hydraulic pressure is canceled out. The spool 31 has a force (hereinafter referred to as “force Fs”) calculated by “[hydraulic pressure of the lubricating oil passage 13] × [area of the flange portion 31d−area of the tip portion 31b]” in the protruding direction, and a spring 34. The retraction direction biasing force (hereinafter referred to as “biasing force Fsp”) is received. Of the bottom surface 31d, a portion corresponding to an area larger than the area of the tip portion 31b corresponds to the “pressure receiving portion” according to the present invention. When the oil pressure of the lubricating oil passage 13 increases and the force Fs exceeds the urging force Fsp, the spool 31 starts to move in the protruding direction.

  In the state shown in FIG. 3 in which the spool 31 is at the maximum and the bottom surface 31d is in contact with the inner bottom surface 32b, the tip 31b is in contact with the end surface of the spool sliding portion 35 opposite to the retainer accommodating portion 36 in FIG. It can be displaced between states.

  The opening 31a is made smaller than the flow passage cross section of the lubricating oil passage 13, and when all of the opening 31a faces the lubricating oil passage 13, the lubricating oil passage 13 is fully opened. When the spool 31 is in the most retracted state from the lubricating oil passage 13, the flow passage area of the lubricating oil passage 13 is most restricted. When the spool 31 protrudes with respect to the lubricating oil passage 13 and changes from the state of FIG. 3 to the state of FIG. 4, the flow passage area of the lubricating oil passage 13 increases. Although not shown, when the spool 31 further protrudes and the lower end position of the paper surface of the opening 31a matches the lower end position of the lubricating oil passage 13, the lubricating oil passage 13 is fully opened. Even if the spool 31 further protrudes into the lubricating oil passage 13, the opening 31a does not restrict the lubricating oil passage 13, and the fully open state of the lubricating oil passage 13 is maintained. When the spool 31 protrudes most into the lubricating oil passage 13, the upper end position of the paper surface of the opening 31 a substantially matches the upper end position of the lubricating oil passage 13.

  On the other hand, the retainer 32 has a force (hereinafter referred to as “force Fr”) calculated by “[hydraulic pressure of the lubricating oil passage 13] × [area of the inner bottom surface 32b]” in the retraction direction, and the retraction direction acting on the spool. And an urging force Fsp in the protruding direction that is in a relationship of action and reaction with respect to Fsp. Unless the force (hereinafter referred to as “force Ft”) by the temperature-sensitive control unit 4 is operated, the retainer 32 is pressed against a seating portion 32e, which will be described later, by the force Fr due to the hydraulic pressure of the lubricating oil passage 13 and does not operate. Alternatively, a balance is achieved at a position closer to the protruding direction than the seating portion 32e by the force Fr and the urging force Fsp.

  From the state of FIG. 3 in which the outer bottom surface 32c is in contact with the seating portion 32e by the action of the temperature-sensitive control unit 4, the retainer 32 has a step between the spool sliding portion 35 and the retainer accommodating portion 36. It can be displaced within the range up to the state of FIG. When the force Ft of the temperature sensing control unit 4 acts on the retainer 32, the inner bottom surface 32b comes into contact with the bottom surface 31d, and the spool 31 is pressed by the retainer 32 and displaced in the protruding direction. In the state shown in FIG. 6, the spool 31 is regulated so that the tip end portion 31 b and the flange portion 31 c are sandwiched between the spool sliding portion 35 and the retainer 32 and cannot be displaced. At this time, the lubricating oil passage 13 is fully opened. The outer bottom surface 32c of the bottom portion 32a corresponds to the “surface opposite to the spool” according to the present invention.

  As shown in FIGS. 2 to 6, a plurality of protrusions 31e as spacers are provided on the tip 31b and the bottom 31d of the spool 31, respectively. Thereby, the minimum clearance for oil to enter is formed between the spool sliding portion 35 and the tip portion 31b and between the flange portion 31c and the bottom portion 32a. As a result, the oil smoothly flows into the gaps, and the hydraulic pressure acts on each part with certainty.

  Although not shown, one or more breathing holes communicating with the atmosphere are formed in the vicinity of the step surface between the spool sliding portion 35 and the retainer accommodating portion 36. Therefore, even if oil leaks between the outer surface of the spool 31 and the inner peripheral surface of the retainer 32 or the inner peripheral surface of the retainer accommodating portion 36, the operations of the spool 31 and the retainer 32 are not inhibited. Absent.

(Temperature control unit)
The temperature sensing control unit 4 is accommodated in a temperature sensing accommodation unit 40 that is continuously formed on the side opposite to the lubricating oil passage 13 in the retainer accommodation unit 36. An inflow oil passage 48 communicates the temperature-sensitive housing portion 40 and a portion immediately upstream of the temperature-sensing control portion 4 in the lubricating oil passage 13, and the temperature-sensitive control portion 4 has an oil temperature that is as accurate as the lubricating oil passage 13 exists. Can be detected. In addition, the temperature-sensitive housing portion 40 and the downstream portion of the temperature-sensitive control portion 4 in the lubricating oil passage 13 are communicated with each other through a discharge oil passage 49. The inflow oil passage 48 and the discharge oil passage 49 are flow passages that have a small cross section so as to have a throttling function. As a result, the oil pressure in the lubricating oil passage 32 does not act on the outer bottom surface 32 c of the retainer 32 while circulating the oil in the warm accommodating portion 41.

  The temperature sensitive control unit 4 uses a thermowax 41 that expands due to a temperature change, and is displaced when the oil temperature exceeds a second temperature (for example, 100 to 110 ° C.) as a predetermined temperature. In addition, the step part is formed by making the temperature sensitive accommodating part 41 smaller in diameter than the retainer accommodating part 36, and the above-described seating part 32 e that determines the retraction limit position of the retainer 32 is configured. Since the temperature control unit 4 is a general one, it will not be described in detail.

  The temperature-sensitive control unit 4 includes a displacement part 42, a fixed part 43 fixed to the temperature-sensitive housing part 40, a pressing spring 44, a return spring 45, and a pressing ring slidably inserted into the displacement part 42. 46 and a retaining ring 47 for retaining the pressing ring 46. The thermo wax 41 starts to expand when the oil temperature becomes higher than the second temperature T2. When the thermowax 41 starts to expand, the displacement part 42 is displaced with respect to the fixed part 43 in order to absorb the volume expansion of the thermowax 41, and the entire length of the temperature-sensitive control part 4 becomes long. As a result, a compression force acts on the pressing spring 44, and the urging force of the pressing spring 44 thereby acts on the outer bottom surface 32 c of the retainer 32 via the pressing ring 46. This force is the aforementioned force Ft. As a result, the retainer 32 is pressed in the protruding direction and is engaged with the spool 31 to be displaced together. When the retainer 32 is in the state shown in FIG. 6, the tip of the wall portion comes into contact with the step surface between the spool sliding portion 35 and the retainer accommodating portion 36, and thus cannot be displaced further in the protruding direction.

  Further, a portion of the bottom 32a of the retainer 32 that faces the tip of the displacement portion 42 is recessed into the spool 31 to form a recessed portion 32d. Therefore, even if the temperature rise continues and the entire length of the temperature-sensitive control unit 4 continues to increase, the pressing ring 46 does not displace further, so that the tip of the displacement part 42 enters the recessed part 32d as shown in FIG. The volume expansion of the thermowax 41 is absorbed. Thereby, the expansion failure of the temperature-sensitive control unit 4 due to the inability to expand does not occur.

  When the oil temperature becomes lower than the second temperature T2, the volume expansion of the thermowax 41 starts to decrease, and the displacement portion 42 is displaced to the position before the expansion by the action of the return spring 45.

7). Operation of Hydraulic Control Device The operation of the hydraulic control device will be described with reference to the drawings. “II”, “III”, “IV”, “V”, and “VI” in FIGS. 7 and 8 (a) and (b) are the same as those in FIGS. 2, 3, 4, 5, and 6, respectively. Indicates that it corresponds to a state.

  Immediately after the engine is started, the oil temperature is often lower than the first temperature T1, for example, 55 to 65 ° C. In such a case, the oil viscosity is high and there is little oil leakage. For this reason, although the discharge amount of the oil pump 1 is small, the hydraulic pressure in the discharge oil passage 11A and the lubricating oil passage 13 is high. Therefore, the spool 31 protrudes with respect to the lubricating oil passage 13 by the oil pressure of the lubricating oil passage 13, and is displaced from the initial state as shown in FIG. 3 to the state of FIG. Thereby, the lubricating oil passage 13 is opened, and oil is supplied to the main gallery 8 in preference to the valve opening / closing timing control device 2. As a result, the oil pump 1 does not wastefully work on the valve opening / closing timing control device 2 that does not need to operate immediately after the engine is started.

  When the oil is warmed up to some extent and the oil temperature becomes higher than the first temperature T1, the oil viscosity decreases and the oil pressure decreases. As a result, the spool 31 is retracted from the lubricating oil passage 13 and is in the state shown in FIG. When the accelerator is depressed after the warm-up operation is completed, power is supplied to the OCV 5, and the valve opening / closing timing control device 2 is advanced. The valve opening / closing timing control device 2 requires hydraulic pressure to start stably, but the spool 31 is most retracted from the lubricating oil passage 13, and the flow passage area of the lubricating oil passage 13 is most restricted. . Therefore, oil is preferentially supplied to the valve opening / closing timing control device 2, and the valve opening / closing timing control device 2 starts smoothly.

  FIG. 8B shows the relationship between the oil discharge pressure of the oil pump 1 in the state (II) of FIG. 2, the hydraulic pressure supplied to the valve opening / closing timing control device 2, and the hydraulic pressure supplied to the main gallery 8. Shown in Since the lubricating oil passage 13 is fully opened, both the hydraulic pressure of the main gallery 8 and the hydraulic pressure of the valve opening / closing timing control device 2 follow changes in the oil discharge pressure of the oil pump 1.

  Thereafter, when the engine speed increases and the oil discharge pressure of the oil pump 1 increases, the oil pressure of the lubricating oil passage 13 also increases, and the spool 31 changes from the state shown in FIG. 3 to the state shown in FIG. The state is displaced from the state to the state shown in FIG. 5, and the lubricating oil passage 13 is gradually opened and finally fully opened as shown in FIG. As a result, the engine speed increases and the oil is sufficiently supplied to the main gallery 8 that requires a large amount of lubricating oil. When the engine speed is increasing, the valve opening / closing timing control device 2 also requires hydraulic pressure, but since the discharge pressure of the oil pump 1 is absolutely increased, the valve opening / closing timing control device 2 is also sufficient. Fresh oil is supplied.

  The relationship between the oil discharge pressure of the oil pump 1 at this time, the hydraulic pressure supplied to the valve opening / closing timing control device 2 and the hydraulic pressure supplied to the main gallery 8 is shown in FIG. In the state (III) of FIG. 3, since the lubricating oil passage 13 is throttled, the change rate of the hydraulic pressure of the main gallery 8 is reduced and the change rate of the hydraulic pressure of the valve opening / closing timing control device 2 is increased. When the spool 31 starts to enter the lubricating oil passage 13 (IV) in FIG. 4, the flow passage area of the lubricating oil passage 13 starts to increase, so the rate of change in the hydraulic pressure of the main gallery 8 increases. At the same time, the change rate of the hydraulic pressure of the valve timing control device 2 is reduced. In the state (V) of FIG. 5 in which the spool 31 has entered the lubricating oil passage 13 most, the lubricating oil passage 13 is fully opened, so that the hydraulic pressure of the main gallery 8 and the hydraulic pressure of the valve opening / closing timing control device 2 are Both follow changes in the oil discharge pressure of the oil pump 1.

  Thus, when the oil temperature is lower than the second temperature T2, the spool 31 adjusts the flow passage area of the lubricating oil passage 13 depending only on the hydraulic pressure level of the lubricating oil passage 13.

  When the oil temperature further rises and becomes higher than the second temperature T2 and the oil viscosity becomes excessively low, in the valve opening / closing timing control device 2, oil leakage (exudation) occurs from minute gaps between the constituent members. . However, as shown in FIG. 6, since the temperature sensing control unit 4 operates, the spool 31 is displaced to the most protruding state with respect to the lubricating oil passage 13 via the retainer 32. The spool 31 is restricted to that state by the action of the temperature sensing control unit 4. Thereby, the oil supply amount with respect to the valve opening / closing timing control device 2 can be minimized, and useless work by the oil pump 1 can be suppressed. Thus, when the oil temperature becomes higher than the second temperature T2, the work of the oil pump 1 can be suppressed in preference to the control of the valve opening / closing timing control device 2.

  The relationship between the oil discharge pressure of the oil at this time, the hydraulic pressure supplied to the valve opening / closing timing control device 2 and the hydraulic pressure supplied to the main gallery 8 is shown in FIG. Since the lubricating oil passage 13 is fully opened, both the hydraulic pressure of the main gallery 8 and the hydraulic pressure of the valve opening / closing timing control device 2 follow changes in the oil discharge pressure of the oil pump 1.

  In summary, as shown in FIG. 7, when the oil temperature is lower than the second temperature T2, the flow path area adjustment unit 3 is operable by the oil pressure of the lubricating oil passage 13, and the oil temperature is When the temperature is higher than 2 temperature T2, the temperature of the lubricating oil passage 13 is restricted by the action of the temperature-sensitive control unit 4, and the oil does not operate regardless of the hydraulic pressure of the lubricating oil passage 13.

8). Other Embodiments (1) In the above-described embodiment, when the oil temperature becomes higher than the second temperature T2, the temperature-sensitive control unit 4 displaces the spool 31 so that the lubricating oil passage 13 is fully opened. However, it is configured to be restricted to that state, but is not limited to this. The degree of squeezing of the lubricating oil passage 13 by the spool 31 may be appropriately set as necessary.
(2) In the above-described embodiment, the second temperature T2 is set to 100 to 110 ° C., and the thermowax 41 is displaced at the temperature. However, the present invention is not limited to this. It is conceivable to change the set value of the second temperature T2 depending on the use mode. In this case, the thermowax 41 to be used should also be changed.
(3) In the above-described embodiment, the opening 31a is set to be smaller than the flow passage cross section of the lubricating oil passage 13, but is not limited thereto. The opening 31 a may be set larger than the cross section of the lubricating oil passage 13 as long as the flow passage area of the lubricating oil passage 13 can be adjusted by the withdrawal and withdrawal of the spool 31. In addition, the cross-sectional shape of each oil passage and the shape of the opening 31a are not limited to a polygonal cross-section, a circular cross-section, and the like as long as they fulfill their respective functions.
(4) In the above-described embodiment, the example in which the valve opening / closing timing control device 2 controls the opening / closing timing of the intake valve has been described. However, the present invention is not limited to this. The valve opening / closing timing control device may control the opening / closing timing of the exhaust valve.

  The present invention is applicable to any engine provided with a valve opening / closing timing control device.

1 Oil pump (pump)
2 Valve opening / closing timing control device 3 Flow path area adjustment unit 4 Temperature sensing control unit 8 Main gallery (predetermined part other than the valve opening / closing timing control device)
11A Discharge oil passage (first passage)
13 Lubricating oil passage (second passage)
21 Housing (drive side rotating member)
22 Internal rotor (driven side rotating member)
31 Spool 31a Opening (Opening)
31d Bottom (pressure receiving part)
32 Retainer 32a Bottom 32c Outer bottom surface (surface opposite to spool)
34 Spring (biasing member)
42 Thermo wax 41
101 Camshaft T2 Second temperature (set temperature)

Claims (5)

A pump that is driven by the rotation of the engine to discharge oil;
A driven-side rotating member that rotates synchronously with the crankshaft; and a driven-side rotating member that is arranged coaxially with the driving-side rotating member and rotates synchronously with the camshaft; and the driven-side rotating member with respect to the driving-side rotating member A valve timing control device for displacing the relative rotational phase of the oil by supplying or discharging oil;
A first flow path communicating the pump and the valve timing control device;
A second flow path that branches from the first flow path and supplies oil to a predetermined portion other than the valve timing control device;
A flow path area adjusting unit that is provided in the second flow path, increases the flow area of the second flow path by increasing the hydraulic pressure on the upper side of the flow path, and decreases the flow path area by decreasing the hydraulic pressure;
A temperature-sensitive control unit that can be displaced according to a temperature condition and regulates an operation of reducing the flow channel area among operations of the flow channel area adjustment unit when the oil temperature is higher than a predetermined set temperature. And a hydraulic control device.   2. The temperature sensing control unit according to claim 1, wherein when the temperature of the oil becomes higher than the set temperature, the flow channel area adjusting unit is displaced and regulated so as to fully open the second flow channel. Hydraulic control device.   The hydraulic control device according to claim 1, wherein the temperature-sensitive control unit includes a thermo wax that expands due to a temperature change. The flow channel area adjusting portion has a cylindrical shape in which an opening capable of adjusting the flow channel area is provided in an outer peripheral wall portion, and a spool capable of receiving the oil of the second flow channel from the opening; A cup-shaped retainer that slidably holds an end of the spool on the side away from the second flow path, and a biasing member that presses the spool against the bottom of the retainer,
The spool includes a pressure receiving portion capable of acting in a protruding direction from the retainer on the pressure of oil flowing from the opening,
4. The hydraulic control device according to claim 1, wherein the temperature-sensitive control unit acts on a surface of the bottom portion opposite to the spool. 5.   5. The hydraulic control device according to claim 1, wherein the temperature-sensitive control unit is displaced according to a temperature of oil in the second flow path.

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