JP6926803B2 - Hydraulic oil supply device with flow control valve and flow control valve - Google Patents

Description

The present invention relates to a hydraulic oil supply device including a flow rate control valve and a flow rate control valve that control the flow rate by changing the opening degree according to the fluid pressure.

Conventionally, a flow control valve having a bottomed tubular valve body having a pressure receiving surface at the bottom and an annular recess formed on the outer peripheral surface of the side wall and a housing for accommodating the valve body is known (for example). , Patent Documents 1 and 2). This flow rate control valve is used to control the flow rate (flood control) of the hydraulic oil discharged from the mechanical oil pump that is driven according to the rotation speed of the internal combustion engine. Specifically, the hydraulic oil discharged from the mechanical oil pump is distributed to the first oil passage that communicates with the valve opening / closing timing control device, the piston jet, etc., and the second oil passage that communicates with the main gallery, and the flow rate. The control valve controls the flow rate (hydraulic pressure) of the hydraulic oil flowing through the first oil passage and the second oil passage.

The flow control valve described in Patent Documents 1 and 2 forms a communication passage communicating with the pressure receiving surface of the valve body in a part of the housing, and connects the hydraulic oil flowing through the first oil passage or the second oil passage. By acting on the pressure receiving surface through the passage, the valve body is configured to move in the direction orthogonal to the flow direction of the hydraulic oil.

The flow control valve described in Patent Document 1 is arranged on the path of the second oil passage, and two annular recesses (the first series in the document) having different oil passage cross-sectional areas on the side wall of the valve body (spool in the document). A passage (passage, second passage) is provided, and the oil pressure of the second oil passage supplied to the main gallery is changed stepwise according to the rotation speed of the internal combustion engine. As a result, it is possible to set the required flood control according to the rotation speed of the internal combustion engine, so that it is possible to reduce the wasteful work amount of the pump and improve the fuel efficiency.

The flow rate control valve described in Patent Document 2 communicates with a housing having an inflow port and an outflow port on the path between the first oil passage and the second oil passage, respectively, and the inflow port and the outflow port of the first oil passage. It includes a valve body having one annular recess (first recess in the literature) and a second annular recess (second recess in the literature) communicating with the inlet and outlet of the second oil passage. At the initial stage when the rotation speed of the internal combustion engine starts to increase, the oil passage cross-sectional area of the first annular recess communicating with the first oil passage is set to be larger than the oil passage cross-sectional area of the second annular recess communicating with the second oil passage. .. Then, as the rotation speed starts to increase and the valve body moves, the oil passage cross-sectional area of the first annular recess gradually decreases, and the oil passage cross-sectional area of the second annular recess gradually increases. The oil pressure rise slope of the oil passage is made smaller than the oil pressure rise slope of the first oil passage. It is stated that this can reduce the drive loss of the oil pump and suppress the deterioration of fuel efficiency.

Japanese Unexamined Patent Publication No. 2013-092088 Japanese Unexamined Patent Publication No. 2014-101809

The conventional flow rate control valve can optimize the flow rate of the hydraulic oil flowing through the second oil passage communicating with the main gallery and suppress the deterioration of fuel efficiency, but the movement direction of the valve body is the flow of the hydraulic oil. Since it is orthogonal to the direction (oil passage), it is necessary to provide an installation space for the flow control valve around the oil passage. For this reason, it is necessary to separately drill a large hole for the flow control valve in the direction orthogonal to the oil passage, which increases the machining cost and limits the installation space of the flow control valve in an internal combustion engine in which various devices are densely packed. Therefore, the degree of freedom in design is reduced.

Further, since the structure is such that the hydraulic pressure is applied to the pressure receiving surface of the valve body through the communication passage formed in a part of the housing, the responsiveness is deteriorated if the oil passage cross-sectional area of the communication passage is not set appropriately. There is a risk.

Therefore, an inexpensive flow rate control valve having a simple configuration and ensuring responsiveness and a high degree of freedom in design, and a hydraulic oil supply device equipped with this flow rate control valve are desired.

The characteristic configuration of the flow control valve is that it has a pressure receiving surface on which the pressure of the fluid acts, and the linear motion member that can move along the flow direction of the fluid by the pressure acting on the pressure receiving surface and the pressure. A bottomed tubular guide having a urging member for urging the linear motion member and a first bottom portion including a first hole portion and a second hole portion to guide the movement of the linear motion member. A bottomed tubular rotating member having a member and a second bottom portion including a third hole portion and a fourth hole portion and rotating relative to the guide member in conjunction with the movement of the linear motion member. , And the first bottom portion and the second bottom portion are in contact with each other in a state where the first hole portion and the third hole portion are always in communication with each other. The point is that the communication area can be changed by the relative rotation of the rotating member with respect to the guide member.

The flow control valve of this configuration has a linear motion member that moves along the flow direction of the fluid by acting on the pressure receiving surface with a fluid pressure that exceeds the urging force of the urging member, and a bottomed tubular shape that guides the linear motion member. The guide member is provided with a bottomed tubular rotating member that rotates relative to the guide member in conjunction with the movement of the linear motion member. That is, since the linear motion member moves along the flow path direction and the rotating member is rotated in conjunction with the movement of the linear motion member, the valve body that moves in the direction orthogonal to the flow path is not provided. .. Therefore, the flow control valve can be arranged coaxially with the flow path, and it is not necessary to make a large hole in the direction orthogonal to the flow path. As a result, the installation space for the flow control valve can be secured only by enlarging the hole in the flow path. Therefore, the processing cost can be reduced, and the degree of freedom in design can be increased without requiring a large space around the flow path.

Further, in this configuration, the first hole portion of the guide member and the third hole portion of the rotating member are always communicated with each other, and the second hole portion of the guide member and the fourth hole portion of the rotating member are connected to each other. The communication area can be changed by the relative rotation of. As a result, the small flow rate mode in which the first hole and the third hole only communicate with each other and the communication area between the second hole and the fourth hole are gradually increased to gently increase the gradient of the fluid pressure. It is possible to set a flow rate gradual increase mode and a large flow rate mode in which all the holes communicate with each other. Since these modes are set by applying fluid pressure to the pressure receiving surface of the linear motion member that moves along the flow direction of the fluid, it is possible to reduce the pressure loss of the fluid and improve the responsiveness of the linear motion member. can.

In this way, it was possible to provide an inexpensive flow control valve with a high degree of freedom in design while ensuring responsiveness with a simple configuration.

Another characteristic configuration is that the linear motion member has an annular flange-shaped portion including the pressure receiving surface and an extending portion extending from the flange-shaped portion, and the extending portion has a through hole portion. Is formed, and a first elongated hole along the flow direction is formed in the first side wall portion extending from the first bottom portion of the guide member, and from the second bottom portion of the rotating member. A second elongated hole inclined with respect to the first elongated hole is formed in the extended second side wall portion, and extends over the through hole portion, the first elongated hole, and the second elongated hole. A pin-shaped member arranged and supported by the through hole portion is provided, and by moving the linear motion member, the pin-shaped member moves while abutting on the edge portion of the second elongated hole, and the rotating member moves. It is at a point where it rotates relative to the guide member.

In this configuration, the linear motion member having the through hole portion in which the pin-shaped member is supported moves along the flow direction of the fluid without rotating relative to the guide member, thereby forming the first elongated hole of the guide member. The pin-shaped member moves along the pin-shaped member, and the pin-shaped member abuts on the second elongated hole of the rotating member that is inclined with respect to the first elongated hole, and the relative rotation of the rotating member with respect to the guide member is realized. As described above, the relative rotation of the rotating member with respect to the guide member is realized only by processing a hole in each member and inserting the pin-shaped member, so that the manufacturing is extremely easy.

Another characteristic configuration is that the linear motion member, the guide member, and the rotating member are all cylindrical and arranged on the same axis, and the pressure receiving surface is the guide member and the rotating member. The guide member and the rotating member are arranged radially outside the guide member so as to be adjacent to the end portion of the guide member, and the end portion of the guide member allows the flow of the fluid to the pressure receiving surface. It is at the point where the passage is formed.

In this configuration, since the linear motion member, the guide member, and the rotating member are all cylindrical and arranged on the same axis, a flow path is formed inside the end of the rotating member in the radial direction. .. At this time, since the pressure receiving surface of the linear motion member is formed on the radial outer side adjacent to the end portions of the guide member and the rotating member and the continuous passage is formed at the end portion of the guide member, the fluid smoothly receives the pressure. It flows in the direction of the surface, and the responsiveness of the linear motion member can be enhanced.

Another characteristic configuration is that the linear motion member, the guide member, and the rotating member are housed in a recess formed on a mating surface between a housing to be mounted and a cover to be mounted on the housing. be.

In this configuration, since the concave portion is formed on the mating surface, it is extremely easy to expand the circumference of the flow path for the flow control valve in accordance with the processing of the flow path.

The characteristic configuration of the first flow control valve is that the pressure receiving surface is arranged on the upstream side in the flow direction, and the first bottom portion and the second bottom portion are arranged on the downstream side in the flow direction. In the initial state before the linear motion member moves, only the first hole portion and the third hole portion communicate with each other, and as the linear motion member moves, the second hole portion and the first hole portion and the first hole portion communicate with each other. In the movement completed state in which the communication of the four holes is started and the movement of the linear motion member is completed, the second hole and the fourth hole are completely communicated with each other.

The first flow control valve has an oil pump driven according to the rotation speed of the engine, a common oil passage to which hydraulic oil is supplied from the oil pump, and a valve opening / closing timing control by branching from the common oil passage. The second oil supply device comprising a first oil passage communicating with at least one of a device, a turbocharger and a piston jet, and a second oil passage branching from the common oil passage and communicating with the main gallery. It is preferable that it is provided in the oil passage.

The first flow rate control valve of this configuration is set to a small flow rate mode in which only the first hole and the third hole communicate with each other in the initial state, and acts on the pressure receiving surface from the oil pump as the engine speed increases. When the discharge pressure is increased and the linear motion member moves, communication between the second hole portion and the fourth hole portion is started, and when the movement of the linear motion member is completed, all the holes are communicated in a large flow rate mode. Set. By providing this first flow control valve in the second oil passage that communicates with the main gallery, the main gallery is in a small flow mode in the low speed range such as when the engine is started, so relatively hydraulic pressure is required compared to the main gallery. It is possible to preferentially apply the oil pressure to the valve opening / closing timing control device or the like. As a result, in the case of the valve opening / closing timing control device, the optimum phase control is quickly executed, and the fuel consumption can be improved. Further, as the engine speed increases, the main gallery shifts to the large flow rate mode, so that the oil pressure required for the main gallery can be secured.

The characteristic configuration of the second flow control valve is that the pressure receiving surface is arranged on the downstream side in the flow direction, and the first bottom portion and the second bottom portion are arranged on the upstream side in the flow direction. In the initial state before the linear motion member moves, the second hole portion and the fourth hole portion are completely in communication with each other, and as the linear motion member moves, the second hole portion and the fourth hole portion and the said The communication area of the fourth hole portion gradually decreases, and in the movement completed state in which the movement of the linear motion member is completed, only the first hole portion and the third hole portion communicate with each other.

It is preferable that the second flow rate control valve is provided in the first oil passage of the hydraulic oil supply device.

The second flow rate control valve of this configuration is set to a large flow rate mode in which all the holes communicate with each other in the initial state, and the discharge pressure acting on the pressure receiving surface from the oil pump increases as the engine speed increases. The movement of the linear motion member reduces the communication area between the second hole and the fourth hole, and the small flow mode in which only the first hole and the third hole communicate with each other when the linear motion member is completely moved. Is set to. By providing this second flow rate control valve in the first oil passage that communicates with the valve opening / closing timing control device, etc., the valve opening / closing timing control device, etc. is in the large flow rate mode in the low speed range such as when the engine is started, so that the valve opening / closing time control valve is opened / closed. It is possible to reliably apply the oil pressure to the timing control device and the like. In addition, as the engine speed increases, the valve opening / closing timing control device, etc. shifts to the small flow rate mode, so while ensuring the flood control required for the valve opening / closing timing control device, etc., the oil pressure required for the main gallery can be obtained. It can be secured with priority.

Further, as another characteristic configuration of the hydraulic oil supply device, the first flow rate control valve is provided in the second oil passage, and the second flow control valve is provided in the first oil passage. It is preferable that the oil is used.

In this configuration, the first flow rate control valve is provided in the second oil passage communicating with the main gallery, and the second flow rate control valve is provided in the first oil passage communicating with the valve opening / closing timing control device and the like. In the low speed range such as when the engine is started, the main gallery is in the small flow mode and the valve opening / closing timing control device is in the large flow mode. It is possible to preferentially act on the oil pressure. As a result, in the case of the valve opening / closing timing control device, the optimum phase control is quickly executed, and the fuel consumption can be improved. In addition, as the engine speed increases, the valve opening / closing timing control device, etc. shifts to the small flow rate mode, while the main gallery shifts to the large flow rate mode. At the same time, it is possible to preferentially secure the flood control required in the main gallery.

It is a schematic diagram which attached the flow rate control valve which concerns on 1st Embodiment to an internal combustion engine. It is sectional drawing of the flow rate control valve before the linear motion member moves. It is a bottom view of the linear motion member and the rotary member before the linear motion member moves. It is sectional drawing of the flow rate control valve after the linear motion member moved. It is a bottom view of the linear motion member and the rotary member after the linear motion member has moved. It is an exploded perspective view of the flow rate control valve. It is a relationship diagram of the rotation speed and the oil pressure which concerns on 1st Embodiment. It is a schematic diagram which attached the flow rate control valve which concerns on 2nd Embodiment to an internal combustion engine. It is a relationship diagram of the rotation speed and the oil pressure which concerns on 2nd Embodiment. It is a schematic diagram which attached the flow rate control valve which concerns on 3rd Embodiment to an internal combustion engine. It is a relationship diagram of the rotation speed and the oil pressure which concerns on 3rd Embodiment. It is a bottom view of the linear motion member and the rotary member which concerns on other embodiment. It is sectional drawing of the flow rate control valve which concerns on other embodiment.

Hereinafter, embodiments of the flow control valve according to the present invention will be described with reference to the drawings. In this embodiment, an example in which the flow control valve V is incorporated in the hydraulic oil supply device 10 installed in the engine E will be described. However, the present invention is not limited to the following embodiments, and various modifications can be made without departing from the gist thereof.

FIG. 1 shows a block diagram schematically showing a configuration of a supply destination of hydraulic oil (an example of a fluid) by the hydraulic oil supply device 10 and the hydraulic oil supply device 10 according to the first embodiment. As shown in FIG. 1, the hydraulic oil supply device 10 includes an oil pump 11, an oil filter 12, a relief valve 13, a common oil passage 14, a first oil passage 15, a second oil passage 16, and a flow control valve V. There is.

In FIG. 1, in addition to the hydraulic oil supply device 10, the valve opening / closing timing control device 1, the turbocharger 3, and the piston jet 4 to which the hydraulic oil flowing through the first oil passage 15 is supplied, and the valve opening / closing timing control device 1 are shown. The oil control valve 5 that switches the supply destination of the hydraulic oil, the ECU 6 (engine control unit) that controls the switching of the oil control valve 5, the oil pan 7 that stores the hydraulic oil, and the operation that circulates through the second oil passage 16. The main gallery 2 to which the oil is supplied is represented, and these constitute the engine E.

The oil pump 11 pumps hydraulic oil from the oil pan 7 and discharges the hydraulic oil to the common oil passage 14, and the hydraulic oil flows through the common oil passage 14 by this discharge pressure. The rotating shaft of the oil pump 11 is connected and fixed to the crankshaft (not shown) of the engine E, and is mechanically driven by the rotational driving force of the crankshaft. An oil filter 12 is arranged in the middle of the common oil passage 14, and small dust and sludge in the hydraulic oil that have not been filtered by the oil strainer are filtered. The relief valve 13 is provided to open the valve when the discharge pressure of the hydraulic oil from the oil pump 11 exceeds a predetermined value, and to prevent the hydraulic oil having a predetermined pressure value or more from flowing through the common oil passage 14. There is.

The common oil passage 14 branches at a branch point 17, from which the first oil passage 15 and the second oil passage 16 extend. The hydraulic oil flowing through the second oil passage 16 flows into the flow rate control valve V. The flow rate control valve V is provided to change the distribution ratio of the hydraulic oil flowing through the common oil passage 14 to the first oil passage 15 and the second oil passage 16 according to the rotation speed of the oil pump 11. .. The details of the flow rate control valve V will be described later.

The common oil passage 14 branches on the upstream side of the branch point 17 to supply hydraulic oil to each of the turbocharger 3 and the piston jet 4. Further, the common oil passage 14 branches at the branch point 17 and supplies hydraulic oil to the valve opening / closing timing control device 1 via the first oil passage 15. Since the structures and operations of the valve opening / closing timing control device 1, the turbocharger 3, and the piston jet 4 are known, detailed description thereof will be omitted. In the present embodiment, the valve opening / closing timing control device 1, the turbocharger 3, and the piston jet 4 are mentioned, but the present invention is not limited to these, and the turbocharger 3 and the piston jet 4 are branched on the downstream side of the branch point 17. You may. Further, it is not necessary that one vehicle is provided with all of the valve opening / closing timing control device 1, the turbocharger 3, and the piston jet 4, and at least one of the above three may be provided.

An oil control valve 5 is arranged at the end of the first oil passage 15 on the valve opening / closing timing control device 1 side. The oil control valve 5 is an electromagnetic control type, and can control the supply, discharge, and supply / discharge cutoff of hydraulic oil to the advance angle oil passage 1a and the retard angle oil passage 1b of the valve opening / closing timing control device 1. The oil control valve 5 is configured as a spool type, drives a solenoid by controlling the amount of power supplied by the ECU 6, and switches the position of the spool connected to the solenoid. Specifically, by switching the position of the spool, the oil is supplied to the advance angle oil passage 1a and the hydraulic oil is discharged from the retard angle oil passage 1b, and the hydraulic oil is discharged from the advance angle oil passage 1a and the retard angle oil passage 1b. It is possible to control switching to three types of operations: supply of hydraulic oil to the advance oil passage 1a and cutoff of hydraulic oil supply / discharge to the advance angle oil passage 1a and retard angle oil passage 1b.

The common oil passage 14 branches at the branch point 17 and supplies hydraulic oil to the main gallery 2 via the second oil passage 16 provided with the flow rate control valve V. The main gallery 2 includes the entire sliding member such as a piston, a cylinder, and a crankshaft bearing (not shown). Since these operate at high speed as the rotation of the engine E increases, a large amount of hydraulic oil is required for cooling and lubrication as the rotation of the engine E increases. Further, the main gallery 2 shall also include other devices provided in the vehicle and driven by flood control.

[Structure of flow control valve]
Next, the flow rate control valve V will be described in detail with reference to FIGS. 1 to 6.

As shown in FIGS. 1 to 6, the flow control valve V is a mating surface of the engine block Eb (an example of a housing) to be mounted and the timing chain cover Ea (an example of a cover) mounted on the engine block Eb. It is housed in the recess 21 formed in 20. As a result, it is extremely easy to process the recess 21 for the flow control valve V. In the present embodiment, the recess 21 is formed in the engine block Eb, but the recess 21 may be formed in the timing chain cover Ea. Further, the housing and cover are not limited to the engine block Eb and the timing chain cover Ea, and may be a cylinder head cover, a crank cover, or the like.

The flow control valve V includes a linear motion member 31, a compression coil spring S (an example of an urging member) that urges the linear motion member 31, a guide member 32 that guides the movement of the linear motion member 31, and a linear motion member. It includes a rotating member 33 that rotates in conjunction with the movement of 31, a rod-shaped guide pin 34 (an example of a pin-shaped member), and a rod-shaped regulation pin 35. The linear motion member 31, the guide member 32, and the rotating member 33 are all cylindrical and have the same axis X (flow direction of hydraulic oil), and are directed from the outer side in the radial direction to the inner side in the radial direction. They are arranged in the order of the levers.

The linear motion member 31 extends from the flange-shaped portion 31A including the annular pressure receiving surface 31a on which the hydraulic pressure (fluid pressure) acts, and the inner peripheral side of the flange-shaped portion 31A in a cylindrical shape along the axis X direction. It has a cylindrical portion 31B (an example of an extension portion) that has been formed (see FIG. 6). In other words, the pressure receiving surface 31a is composed of one annular surface of the brim-shaped portion 31A in which the end portion of the tubular portion 31B is projected radially outward in an annular shape. When the hydraulic pressure acting on the pressure receiving surface 31a exceeds the urging force of the compression coil spring S, the linear motion member 31 moves toward the downstream side in the flow direction of the hydraulic oil. The gap between the outer peripheral surface of the flange-shaped portion 31A and the inner wall of the recess 21 is set to a minute clearance so that hydraulic oil does not easily leak. A pair of through-holes 31b facing each other are formed in a circular shape in the tubular portion 31B, and both ends of a single guide pin 34 are supported and fixed to the pair of through-holes 31b (FIG. FIG. 6).
The through hole portion 31b is not limited to a circular shape as long as it is configured to have a shape that matches the outer shape of the guide pin 34, and may be configured in a rectangular shape or the like. Further, the method of fixing the guide pin 34 to the through hole portion 31b may be press-fitting, fusion or the like, or a retaining member may be attached to the end of the guide pin 34, and is not particularly limited. Further, the guide pins 34 may be divided and configured, and the pair of guide pins 34 may be fixed to the pair of through-hole portions 31b.

The compression coil spring S urges the linear motion member 31 in a direction that opposes the flood pressure acting on the pressure receiving surface 31a. The compression coil spring S is arranged along the outer circumference of the tubular portion 31B of the linear motion member 31, and is the other annular ring of the flange-shaped portion 31A of the linear motion member 31 on the side opposite to the pressure receiving surface 31a. It is in contact with the surface. A through hole 9 communicating with the outside is formed in the engine block Eb, and this through hole 9 functions as a back pressure release hole through which air in the accommodation space of the compression coil spring S is discharged. Further, the through hole 9 also has a function of discharging hydraulic oil leaked from a gap between the outer peripheral surface of the flange-shaped portion 31A and the inner wall of the recess 21. The compression coil spring S is set to an urging force that causes the linear motion member 31 to move when the design hydraulic pressure or higher is reached.

The guide member 32 has a bottomed tubular shape arranged radially inside the linear motion member 31, and has a first bottom portion 32A and a first cylindrical portion 32B extending cylindrically from the first bottom portion 32A. (Example of the first side wall portion) and (see FIG. 6). The first bottom portion 32A includes a first hole portion 32a located at the center and a plurality of second hole portions 32b (four locations at equal intervals in the present embodiment) located around the first hole portion 32a (4 locations at equal intervals in the present embodiment). (See FIG. 3). The first hole portion 32a and the second hole portion 32b are each formed in a circular shape, and the oil passage cross-sectional area of the first hole portion 32a is set to be smaller than the oil passage cross-sectional area of one second hole portion 32b. ing. The center of the first hole portion 32a is on the shaft core X, and the centers of the plurality of second hole portions 32b are arranged equidistantly from the shaft core X and are located on the same circumference.
Further, the hole diameter of each of the second hole portions 32b in the present embodiment is set so that the angle formed by the tangents passing through the shaft core X is 45 degrees or more (45 degrees in the present embodiment).

The first cylindrical portion 32B is formed with a pair of round holes 32c facing each other at the end opposite to the first bottom portion 32A and a pair of first elongated holes 32d facing each other near the center in the extending direction. (See FIG. 6). A pair of regulation pins 35 longer than the depth of the round holes 32c are fixed to the pair of round holes 32c so that both ends project from the round holes 32c, respectively, and the radial outer side of these regulation pins 35 is a linear motion member. By abutting on the inner peripheral side of the flange-shaped portion 31A of 31, the movement of the linear motion member 31 due to the urging force of the compression coil spring S is restricted (see FIG. 2). Further, the portion of the regulation pin 35 that protrudes inward in the radial direction of the first cylindrical portion 32B abuts on the open end portion of the rotating member 33, so that the first bottom portion 32A of the guide member 32 and the rotating member 33 become the first. The movement of the rotating member 33 in the axis X direction is restricted so as to maintain the contact state with the bottom portion 33A. The round holes 32c are not limited to a circular shape, may be formed into a rectangular shape, or the like, and the number is not limited as long as the round holes 32c are formed in a shape suitable for the outer shape of the regulation pin 35. For example, instead of the pair of regulation pins 35, a single regulation pin 35 penetrating the pair of round holes 32c may be used. Further, the method of fixing the regulation pin 35 to the round hole 32c may be press-fitting, fusion or the like, or a retaining member may be attached to the end of the regulation pin 35, and is not particularly limited.

The pair of first elongated holes 32d formed in the first cylindrical portion 32B extend in parallel with the axis X direction (flow direction of hydraulic oil). A guide pin 34 supported by a through hole portion 31b of the linear motion member 31 is inserted through the pair of first elongated holes 32d. In the initial state before the linear motion member 31 is hydraulically moved, the guide pin 34 is in contact with one end 32da of the pair of first elongated holes 32d (state in FIG. 2), and after the linear motion member 31 is moved. In the movement completed state, the guide pin 34 comes into contact with the other end 32db of the pair of first elongated holes 32d (state of FIG. 4). Here, one end 32da of the first elongated hole 32d is an end on the side far from the first bottom 32A, and the other end 32db is an end on the side closer to the first bottom 32A. From the initial state of FIG. 2 to the movement completion state of FIG. 4, the guide pin 34 is slidably contacted with the side sides of the pair of first elongated holes 32d, so that the movement of the linear motion member 31 is guided by the guide member 32. , The linear motion member 31 moves in the direction along the axis X without rotating relative to the guide member 32.

At the end of the first cylindrical portion 32B opposite to the first bottom portion 32A and farther from the first bottom portion 32A than the round hole 32c, a plurality of protruding portions 32e (protruding along the axis X) In this embodiment, four locations are formed at equal intervals (see FIG. 6). The plurality of protrusions 32e come into contact with the timing chain cover Ea, and the first bottom 32A comes into close contact with the bottom step 21a of the recess 21 of the engine block Eb, thereby restricting the movement of the guide member 32 in the axis X direction. Has been done. Between these plurality of protrusions 32e, a communication passage 18 that allows the flow of hydraulic oil to the pressure receiving surface 31a of the linear motion member 31 is formed (see FIGS. 1 to 2).

The rotating member 33 is configured in a bottomed tubular shape arranged radially inside the guide member 32, and extends cylindrically from the outer peripheral side of the second bottom portion 33A and the second bottom portion 33A. It has a cylindrical portion 33B (an example of a second side wall portion) (see FIG. 6). The internal space surrounded by the second bottom portion 33A and the second cylindrical portion 33B constitutes the second oil passage 16. The second bottom portion 33A includes a third hole portion 33a located at the center and a plurality of fourth hole portions 33b (four locations at equal intervals in the present embodiment) located around the third hole portion 33a (4 locations at equal intervals in the present embodiment). (See FIG. 3). The center of the third hole portion 33a is on the shaft core X, and the centers of the plurality of fourth hole portions 33b are arranged equidistantly from the shaft core X and are located on the same circumference. Further, the hole diameter of each of the fourth hole portions 33b in the present embodiment is set so that the angle formed by the tangents passing through the shaft core X is 45 degrees or more (45 degrees in the present embodiment). As described above, the portion of the regulation pin 35 protruding inward in the radial direction comes into contact with the open end of the rotating member 33, so that the first bottom portion 32A of the guide member 32 and the second bottom portion 33A of the rotating member 33 are brought into contact with each other. The contact state of is maintained. Further, the open end of the rotating member 33 is separated from the timing chain cover Ea by the regulation pin 35, and the communication passage 18 that allows the hydraulic oil to flow to the pressure receiving surface 31a of the linear motion member 31 by the separated space. Is not blocked (see FIG. 2).

The third hole portion 33a and the fourth hole portion 33b are each formed in a circular shape, and the oil passage cross-sectional area of the third hole portion 33a is set to be smaller than the oil passage cross-sectional area of one fourth hole portion 33b. (See Fig. 3). The third hole portion 33a has the same oil passage cross-sectional area and the same center position as the first hole portion 32a of the guide member 32, and the first hole portion 32a and the third hole portion 33a are always in communication with each other. ing. Further, the fourth hole portion 33b has the same oil passage cross-sectional area as the second hole portion 32b of the guide member 32, and the center of the fourth hole portion 33b is relative to the center of the second hole portion 32b. They are located on the same circumference and are out of phase by 45 degrees.

In the second cylindrical portion 33B, a pair of second elongated holes 33d inclined with respect to the direction along the axis X are formed near the center in the extending direction (see FIG. 6). That is, the pair of second elongated holes 33d is inclined with respect to the pair of first elongated holes 32d of the guide member 32. A guide pin 34 supported by a through hole portion 31b of the linear motion member 31 is inserted through the pair of second elongated holes 33d.
That is, the guide pin 34 is fixed to the linear motion member 31 in a state of penetrating the guide member 32 and the rotating member 33 in the radial direction. As a result, when the linear motion member 31 moves linearly along the first elongated hole 32d by flood control, the guide pin 34 also moves linearly without rotating. At this time, as described above, since the second elongated hole 33d is inclined with respect to the first elongated hole 32d, the guide pin 34 is in sliding contact with the side side (edge) of the pair of second elongated holes 33d. In this state, the rotating member 33 rotates about the axis X as it moves from one end 32da to the other end 32db. In the initial state before the linear motion member 31 moves, the guide pin 34 is in contact with one end 33da of the pair of second elongated holes 33d (state of FIG. 2, see FIG. 6), and the linear motion member 31 has moved. In the later movement completion state, the guide pin 34 comes into contact with the other end 33db of the pair of second elongated holes 33d (state of FIG. 4, see FIG. 6). At this time, the first elongated hole 32d of the guide member 32 extends in parallel with the shaft core X direction (flow direction of hydraulic oil), and the second elongated hole 33d of the rotating member 33 is inclined with respect to the first elongated hole 32d. Therefore, the guide member 32 does not rotate relative to the linear motion member 31, while the rotating member 33 rotates relative to the guide member 32 and the linear motion member 31.

Further, in the present embodiment, when the guide pin 34 moves from one end 33da of the second elongated hole 33d to the other end 33db, the angle at which the rotating member 33 rotates about the axis X is the two adjacent fourth. The center of the hole 33b is set to be half of the angle (90 degrees in this embodiment) formed with respect to the shaft core X, that is, 45 degrees. As a result, when the guide pin 34 supported by the linear motion member 31 moves inside the second elongated hole 33d while being guided by the first elongated hole 32d of the guide member 32, the state of FIG. 3 changes to the state of FIG. Become. That is, in the initial state before the linear motion member 31 moves, only the first hole portion 32a and the third hole portion 33a always communicate with each other, and the second hole portion 32b and the fourth hole portion 33b communicate with each other. It is a small flow mode that does not communicate. This is because the first hole portion 32a and the third hole portion 33a have the same center position (axis core X) and the same oil passage cross-sectional area, so that they overlap each other. The hole diameter of the fourth hole 33b is set so that the angle formed by the tangents passing through the shaft core X is 45 degrees or more, and the relative phase between the center of the second hole 32b and the center of the fourth hole 33b is displaced by 45 degrees. This is because the second hole portion 32b and the fourth hole portion 33b do not overlap with each other.
In the state where the linear motion member 31 is moving, the communication area between the second hole portion 32b of the guide member 32 and the fourth hole portion 33b of the rotating member 33 is increased so as to shift from the state of FIG. 3 to the state of FIG. It becomes a flow rate gradual increase mode that gradually increases. In the movement completed state after the linear motion member 31 has moved (the state in which the rotating member 33 has rotated 45 degrees with respect to the guide member 32), all the holes 32a, 32b, 33a, 33b have all the holes 32a, 32b, 33a, 33b as shown in FIG. It becomes a large flow rate mode that communicates perfectly.

In this way, the guide pin 34 is arranged over the through hole portion 31b of the linear motion member 31, the first elongated hole 32d of the guide member 32, and the second elongated hole 33d of the rotating member 33, and the second length. Since the hole 33d is inclined with respect to the first elongated hole 32d, the rotating member 33 rotates relative to the guide member 32 as the linear motion member 31 moves, and the second hole portion 32b and the fourth hole The area facing the portion 33b gradually increases. As a result, in addition to the small flow mode in which only the first hole portion 32a and the third hole portion 33a always communicate with each other and the communication between the first hole portion 32a and the third hole portion 33a, the second hole portion 32b and the fourth hole portion A flow rate gradual increase mode in which the communication area with 33b gradually increases and the flow rate of the hydraulic oil flowing through the second oil passage 16 gradually increases, and a large flow rate in which all the holes 32a, 32b, 33a, 33b communicate completely. The mode can be set. Since these modes are set by applying a hydraulic pressure to the pressure receiving surface 31a of the linear motion member 31 that moves along the flow direction of the hydraulic oil, the pressure loss of the hydraulic oil is reduced and the responsiveness of the linear motion member is improved. Can be enhanced. Moreover, since the pressure receiving surface 31a of the linear motion member 31 is provided between the plurality of protrusions 32e of the guide member 32 and adjacent to the communication passage 18 formed at the open end of the rotating member 33, the operation is performed. Oil pressure loss is extremely small.

Further, in the present embodiment, the linear motion member 31, the guide member 32, and the rotary member 33 are arranged on the same axis X, and the rotary member 33 is moved with respect to the guide member 32 in conjunction with the movement of the linear motion member 31. Since it is configured to rotate relative to each other, the flow control valve V can be arranged in the coaxial direction with the second oil passage 16. As a result, it is not necessary to drill a large hole in the direction orthogonal to the second oil passage 16, and the installation space for the flow control valve V can be increased only by enlarging the hole of the second oil passage 16 formed in the engine block Eb. Can be secured. Therefore, the processing cost can be reduced, and the degree of freedom in design can be increased without requiring a large space around the second oil passage 16. Moreover, the relative rotation of the rotating member 33 with respect to the guide member 32 is realized only by drilling holes in the members 31, 32, 33 and inserting the guide pin 34, so that the manufacturing is extremely easy.

FIG. 7 shows the relationship between the rotation speed of the engine E and the flood pressure of the first oil passage 15 and the second oil passage 16 when the flow control valve V is installed in the second oil passage 16 as shown in FIG. It is shown. That is, as described above, in the flow control valve V, the first bottom portion 32A of the guide member 32 and the second bottom portion 33A of the rotating member 33 are arranged on the downstream side in the hydraulic oil flow direction, and the hydraulic oil flow direction. The pressure receiving surface 31a of the linear motion member 31 is arranged on the upstream side.

In the low rotation region of the engine E, the oil pressure discharged from the oil pump 11 is not sufficiently increased, and the oil pressure acting on the pressure receiving surface 31a of the linear motion member 31 is smaller than the urging force of the compression coil spring S. Only the first hole portion 32a of 32 and the third hole portion 33a of the rotating member 33 communicate with each other (see FIGS. 2 to 3). As a result, the flow rate (hydraulic pressure) of the hydraulic oil distributed to the first oil passage 15 is large, and the flow rate (hydraulic pressure) of the hydraulic oil distributed to the second oil passage 16 is small. As a result, in a low rotation range such as when the engine is started, the oil pressure can be preferentially applied to the valve opening / closing timing control device 1 which requires relatively hydraulic pressure as compared with the main gallery 2. As a result, the optimum phase control of the valve opening / closing timing control device 1 is quickly executed, and the fuel consumption can be improved.

In the medium rotation region of the engine E, the flood pressure acting on the pressure receiving surface 31a of the linear motion member 31 becomes larger than the urging force of the compression coil spring S, and the communication area between the second hole portion 32b and the fourth hole portion 33b gradually increases. The flow rate is gradually increased (the state gradually shifts from FIG. 3 to FIG. 5). As a result, the flow rate of the hydraulic oil distributed to the second oil passage 16 is gradually increased while ensuring the oil pressure required for the valve opening / closing timing control device 1, and the oil pressure required for the main gallery 2 is increased. Can be secured.

In the high rotation region of the engine E, when the movement of the linear motion member 31 is completed, the guide pin 34 becomes the other end 32db of the first elongated hole 32d of the guide member 32 and the second elongated hole 33d of the rotating member 33. A large flow rate mode is set in which the ends 33db are in contact with each other and all the holes 32a, 32b, 33a, 33b communicate with each other (see FIGS. 4 to 5). As a result, as the rotation speed of the engine E increases, the flow rate (hydraulic pressure) of the hydraulic oil supplied to the first oil passage 15 communicating with the valve opening / closing timing control device 1 and the second oil passage 16 communicating with the main gallery 2 ) Increases together. Then, when the rotation speed of the engine E becomes equal to or higher than the predetermined rotation speed and the oil pressure discharged from the oil pump 11 is sufficiently increased, the relief valve 13 opens and is further supplied to the valve opening / closing timing control device 1 and the main gallery 2. The hydraulic pressure of the hydraulic fluid does not rise.

8 to 9 show a second embodiment in which the flow control valve V having the same basic configuration as the first embodiment described above is arranged in the first oil passage 15. In the present embodiment, the flow control valve V is housed in the recess 21 formed in the mating surface 20 of the cylinder head cover Ec and the timing chain cover Ea. In the following, an example in which the flow rate control valve V according to the second embodiment is arranged in the first oil passage 15 communicating with the valve opening / closing timing control device 1, but the valve opening / closing timing control device 1, the piston jet 4 and the turbocharger are shown. The flow rate control valve V according to the second embodiment may be provided in the oil passage communicating with at least one of 3. That is, in addition to the first oil passage 15 communicating with the valve opening / closing timing control device 1, the flow control valve V in the second embodiment may be provided in the oil passage communicating with the piston jet 4, and is not particularly limited.

As shown in FIG. 8, in the second embodiment, the first bottom portion 32A of the guide member 32 and the second bottom portion 33A of the rotating member 33 are arranged on the upstream side in the flow direction of the hydraulic oil as compared with the first embodiment. However, the difference is that the pressure receiving surface 31a of the linear motion member 31 is arranged on the downstream side in the flow direction of the hydraulic oil. That is, the oil pressure of the first oil passage 15 after passing through the flow rate control valve V acts on the pressure receiving surface 31a. Further, in the initial state before the linear motion member 31 moves, as shown in FIGS. 5 and 8, a large flow rate mode in which all the holes 32a, 32b, 33a, 33b communicate with each other is set, and the linear motion member 31 moves. In the later movement completion state, the center of the second hole portion 32b and the center of the fourth hole portion 33b so as to be in a small flow rate mode in which only the first hole portion 32a and the third hole portion 33a are communicated as shown in FIG. It is different from the first embodiment in that the relative phase with and is set.

In the present embodiment, as shown in FIG. 9, in the low rotation region of the engine E, the flood pressure discharged from the oil pump 11 is not sufficiently increased, and the flood pressure acting on the pressure receiving surface 31a of the linear motion member 31 is compressed. Since it is smaller than the urging force of the coil spring S, it is in a large flow rate mode (see FIG. 5) in which all the holes 32a, 32b, 33a, and 33b communicate with each other. As a result, the oil pressure of the hydraulic oil supplied to the first oil passage 15 communicating with the valve opening / closing timing control device 1 and the second oil passage 16 communicating with the main gallery 2 increases.

In the medium rotation region of the engine E, the flood pressure acting on the pressure receiving surface 31a of the linear motion member 31 becomes larger than the urging force of the compression coil spring S, and the communication area between the second hole portion 32b and the fourth hole portion 33b gradually decreases. Then, the mode becomes a hydraulic gradient lowering mode in which the hydraulic gradient becomes gentle (the state gradually shifts from FIG. 5 to FIG. 3). As a result, while reducing the ascending gradient of the oil pressure of the first oil passage 15 communicating with the valve opening / closing timing control device 1, the oil pressure of the second oil passage 16 communicating with the main gallery 2 is increased with a large ascending gradient. It is possible to secure the flood control required for the main gallery 2 while securing the flood control to be supplied to the opening / closing timing control device 1. Depending on the urging force of the compression coil spring S, the communication area between the second hole 32b and the fourth hole 33b, and the relationship with the hydraulic pressure of the hydraulic oil, the valve opening / closing timing control device 1 is communicated in the hydraulic gradient lowering mode. It is possible that the flood pressure of the first oil passage 15 is substantially constant.

In the high rotation region of the engine E, when the movement of the linear motion member 31 is completed, the guide pin 34 becomes the other end 32db of the first elongated hole 32d of the guide member 32 and the second elongated hole 33d of the rotating member 33. A small flow rate mode is set in which only the first hole portion 32a of the guide member 32 and the third hole portion 33a of the rotating member 33 communicate with each other by abutting on the end 33db (see FIG. 3). As a result, the oil pressure of the first oil passage 15 communicating with the valve opening / closing timing control device 1 is maintained substantially constant, and the oil pressure of the second oil passage 16 communicating with the main gallery 2 is increased with a large upward gradient. The oil pressure required in the gallery 2 can be secured. Then, when the engine speed becomes equal to or higher than the predetermined speed and the oil pressure discharged from the oil pump 11 is sufficiently increased, the relief valve 13 is opened, and the operation is further supplied to the valve opening / closing timing control device 1 and the main gallery 2. The oil pressure does not rise.

10 to 11 show a third embodiment in which the flow control valves V having the same basic configuration as those of the first and second embodiments described above are arranged in the first oil passage 15 and the second oil passage 16. Has been done.
This embodiment is a combination of the first embodiment and the second embodiment. In the following description, the flow rate control valve V similar to that of the first embodiment will be referred to as the first flow rate control valve V1, and the flow rate control valve V similar to that of the second embodiment will be referred to as the second flow rate control valve V2. In the following, an example in which the second flow rate control valve V2 is arranged in the first oil passage 15 communicating with the valve opening / closing timing control device 1, but the valve opening / closing timing control device 1, the piston jet 4 and the turbocharger 3 will be described. A second flow control valve V2 may be provided in the oil passage communicating with at least one. That is, in addition to the first oil passage 15 communicating with the valve opening / closing timing control device 1, the second flow control valve V2 may be provided in the oil passage communicating with the piston jet 4, and is not particularly limited.

As shown in FIG. 11, in the low rotation region of the engine E, the oil pressure discharged from the oil pump 11 is not sufficiently increased, and the oil pressure acting on the pressure receiving surface 31a of the linear motion member 31 is attached to the compression coil spring S. Smaller than the power. Therefore, the first flow rate control valve V1 is in a small flow rate mode in which only the first hole 32a of the guide member 32 and the third hole 33a of the rotating member 33 communicate with each other (see FIGS. 2 to 3). ). On the other hand, the second flow rate control valve V2 has a large flow rate mode (see FIG. 5) in which all the holes 32a, 32b, 33a, 33b communicate with each other. As a result, the amount of oil (hydraulic pressure) distributed to the first oil passage 15 is large, and the amount of oil (hydraulic pressure) distributed to the second oil passage 16 is small. As a result, in a low rotation range such as when the engine is started, the oil pressure can be preferentially applied to the valve opening / closing timing control device 1 which requires relatively hydraulic pressure as compared with the main gallery 2.

In the medium rotation region of the engine E, the flood pressure acting on the pressure receiving surface 31a of the linear motion member 31 becomes larger than the urging force of the compression coil spring S. Therefore, in the first flow rate control valve V1, the flow rate gradual increase mode in which the communication area between the second hole portion 32b and the fourth hole portion 33b gradually increases, and in the second flow rate control valve V2, the second hole portion 32b The hydraulic gradient lowering mode is set in which the communication area between the and the fourth hole 33b is gradually reduced and the hydraulic gradient becomes gentle. As a result, while gradually increasing the oil pressure of the second oil passage 16 communicating with the main gallery 2, the rising gradient of the oil pressure of the first oil passage 15 communicating with the valve opening / closing timing control device 1 is reduced, which is necessary for the main gallery 2. It is possible to secure the required oil pressure.

In the high rotation region of the engine E, when the movement of the linear motion member 31 is completed, the guide pin 34 becomes the other end 32db of the first elongated hole 32d of the guide member 32 and the second elongated hole 33d of the rotating member 33. It abuts on the end 33db. Therefore, the first flow rate control valve V1 has a large flow rate mode in which all the holes 32a, 32b, 33a, 33b communicate with each other (see FIGS. 4 to 5), and the second flow control valve V2 has a guide member. It is a small flow rate mode in which only the first hole portion 32a of 32 and the third hole portion 33a of the rotating member 33 communicate with each other (see FIG. 3). As a result, the oil pressure of the first oil passage 15 communicating with the valve opening / closing timing control device 1 is maintained substantially constant, and the oil pressure of the second oil passage 16 communicating with the main gallery 2 is increased with a large upward gradient. The oil pressure required in the gallery 2 can be secured. Then, when the engine speed becomes equal to or higher than the predetermined speed and the oil pressure discharged from the oil pump 11 is sufficiently increased, the relief valve 13 is opened, and the operation is further supplied to the valve opening / closing timing control device 1 and the main gallery 2. The oil pressure does not rise.

[Other Embodiments]
(1) In the above-described embodiment, the second hole portion 32b and the fourth hole portion 33b formed in the first bottom portion 32A of the guide member 32 and the second bottom portion 33A of the rotating member 33 are formed of round holes. As shown in 12, it may be composed of a triangular hole having an apex on the center side. At this time, the central angle of each triangular hole is set to (360 degrees / total number of holes of the second hole portion 32b and the fourth hole portion 33b) or more. In this case, since the occupied area of the second hole portion 32b and the fourth hole portion 33b with respect to the first bottom portion 32A and the second bottom portion 33A can be effectively secured, the flow control valve V can be miniaturized. The shape and quantity of the holes 32a, 32b, 33a, 33b are not particularly limited, and may be appropriately designed according to the required flood pressure. For example, if the second hole portion 32b and the fourth hole portion 33b are set to fan-shaped holes instead of triangular holes, the occupied area of the second hole portion 32b and the fourth hole portion 33b with respect to the first bottom portion 32A and the second bottom portion 33A. Can be secured more effectively.

(2) In the arrangement of the linear motion member 31, the guide member 32, and the rotary member 33 in the above-described embodiment, the rotary member 33 is configured to be rotatable relative to the guide member 32 by the movement of the linear motion member 31. As long as it is, there is no particular limitation. For example, as shown in FIG. 13, the guide member 32, the linear motion member 31, and the rotating member 33 may be arranged in this order from the outer side in the radial direction to the inner side in the radial direction.
In this case, the pressure receiving surface 31a of the linear motion member 31 is composed of an annular end surface formed at the open end of the tubular portion 31B. With such an arrangement, the outer peripheral surface of the guide member 32 can be brought into close contact with the inner peripheral surface of the recess 21 of the engine block Eb, so that the sealing property can be improved. Since other actions and effects are the same as those in the above-described embodiment, detailed description thereof will be omitted.

(3) The number and arrangement of the through hole portion 31b, the first elongated hole 32d, and the second elongated hole 33d into which the guide pin 34 is inserted are not particularly limited. Further, the first elongated hole 32d may be inclined in a direction opposite to the inclined direction of the second elongated hole 33d with respect to the axis X direction. In this case, the hole lengths of the first elongated hole 32d and the second elongated hole 33d can be shortened.

(4) At least one of the linear motion member 31, the guide member 32, and the rotating member 33 may be displaced and arranged.

(5) In the above-described embodiment, the first hole portion 32a and the third hole portion 33a are arranged in the center of the first bottom portion 32A and the second bottom portion 33A, but on the outer peripheral side of the first bottom portion 32A and the second bottom portion 33A. It may be formed in a ring shape.

(6) In the above-described embodiment, the hole diameter and relative phase may be set so that the second hole portion 32b and the fourth hole portion 33b communicate with each other slightly in the small flow rate mode, or the large flow rate mode. The hole diameter and relative phase may be set so that a part of the second hole portion 32b and the fourth hole portion 33b communicate with each other.

(7) In the above-described embodiment, the flow rate control valve V is incorporated in the hydraulic oil supply device 10, but the flow rate control valve V may be installed in the path for circulating the cooling water.

The present invention can be used for a flow rate control valve that controls the flow rate by changing the opening degree according to the fluid pressure.

1 Valve opening / closing timing control device 2 Main gallery 3 Turbocharger 4 Piston jet 11 Oil pump 14 Common oil passage 15 First oil passage 16 Second oil passage 18 Continuous passage 20 Joint surface 21 Recession 31 Linear member 31A Collar 31B cylinder Shaped part (extended part)
31a Pressure receiving surface 31b Through hole 32 Guide member 32A First bottom 32B First cylindrical part (first side wall part)
32a First hole portion 32b Second hole portion 32d First elongated hole 33 Rotating member 33A Second bottom portion 33B Second cylindrical portion (second side wall portion)
33a Third hole 33b Fourth hole 33d Second elongated hole 34 Guide pin (pin-shaped member)
E Engine Ea Timing Chain Cover (Cover)
Eb engine block (housing)
S compression coil spring (biasing member)
V Flow control valve V1 First flow control valve V2 Second flow control valve X Shaft core

Claims (9)

A linear motion member having a pressure receiving surface on which the pressure of the fluid acts and being movable along the flow direction of the fluid by the pressure acting on the pressure receiving surface.
An urging member that urges the linear motion member against the pressure, and
A bottomed tubular guide member having a first bottom portion including a first hole portion and a second hole portion and guiding the movement of the linear motion member,
It has a second bottom portion including a third hole portion and a fourth hole portion, and includes a bottomed tubular rotating member that rotates relative to the guide member in conjunction with the movement of the linear motion member. ,
The first bottom portion and the second bottom portion are in contact with each other in a state where the first hole portion and the third hole portion are always in communication with each other.
The second hole portion and the fourth hole portion are flow control valves configured such that the communication area can be changed by the relative rotation of the rotating member with respect to the guide member. The linear motion member has an annular flange-shaped portion including the pressure receiving surface and an extending portion extending from the flange-shaped portion, and a through hole portion is formed in the extending portion.
A first elongated hole along the flow direction is formed in the first side wall portion extending from the first bottom portion of the guide member.
A second elongated hole inclined with respect to the first elongated hole is formed in the second side wall portion extending from the second bottom portion of the rotating member.
A pin-shaped member arranged over the through hole portion, the first elongated hole, and the second elongated hole and supported by the through hole portion is provided.
The flow rate control according to claim 1, wherein the pin-shaped member moves while abutting on the edge of the second elongated hole due to the movement of the linear motion member, and the rotating member rotates relative to the guide member. valve. The linear motion member, the guide member, and the rotating member are all cylindrical and arranged on the same axis, and the pressure receiving surface is adjacent to the guide member and the end portion of the rotating member. In the state, it is arranged radially outside the guide member and the rotating member.
The flow rate control valve according to claim 1 or 2, wherein a communication passage that allows the flow of the fluid to the pressure receiving surface is formed at the end of the guide member. Any one of claims 1 to 3, wherein the linear motion member, the guide member, and the rotating member are housed in a recess formed in a mating surface between a housing to be mounted and a cover to be mounted on the housing. The flow control valve according to one item. The pressure receiving surface is arranged on the upstream side in the distribution direction, and the first bottom portion and the second bottom portion are arranged on the downstream side in the distribution direction.
In the initial state before the linear motion member moves, only the first hole portion and the third hole portion communicate with each other, and as the linear motion member moves, the second hole portion and the fourth hole portion are in communication with each other. 6. Flow control valve. The pressure receiving surface is arranged on the downstream side in the distribution direction, and the first bottom portion and the second bottom portion are arranged on the upstream side in the distribution direction.
In the initial state before the linear motion member moves, the second hole portion and the fourth hole portion are completely in communication with each other, and as the linear motion member moves, the second hole portion and the fourth hole portion are in perfect communication with each other. Any one of claims 1 to 4 in which the communication area of the four holes gradually decreases and only the first hole and the third hole communicate with each other in the movement completed state in which the linear motion member has been moved. The flow control valve described in. A hydraulic oil supply device including the flow control valve according to claim 5.
An oil pump that drives according to the engine speed,
A common oil passage to which hydraulic oil is supplied from the oil pump, and
A first oil passage that branches off from the common oil passage and communicates with at least one of a valve opening / closing timing controller, a turbocharger, and a piston jet.
A second oil channel that branches off from the common oil channel and communicates with the main gallery is provided.
The flow rate control valve is a hydraulic oil supply device provided in the second oil passage. A hydraulic oil supply device including the flow control valve according to claim 6.
An oil pump that drives according to the engine speed,
A common oil passage to which hydraulic oil is supplied from the oil pump, and
A first oil passage that branches off from the common oil passage and communicates with at least one of a valve opening / closing timing controller, a turbocharger, and a piston jet.
A second oil channel that branches off from the common oil channel and communicates with the main gallery is provided.
The flow rate control valve is a hydraulic oil supply device provided in the first oil passage. The flow rate control valve according to claim 5 is a first flow rate control valve, the flow rate control valve according to claim 6 is a second flow rate control valve, and the first flow rate control valve and the second flow rate control. A hydraulic oil supply device equipped with a valve
An oil pump that drives according to the engine speed,
A common oil passage to which hydraulic oil is supplied from the oil pump, and
A first oil passage that branches off from the common oil passage and communicates with at least one of a valve opening / closing timing controller, a turbocharger, and a piston jet.
A second oil channel that branches off from the common oil channel and communicates with the main gallery is provided.
The first flow control valve is provided in the second oil passage, and is provided.
The second flow rate control valve is a hydraulic oil supply device provided in the first oil passage.

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