WO2020008626A1

WO2020008626A1 - Check valve, oil control valve, and valve timing adjustment device

Info

Publication number: WO2020008626A1
Application number: PCT/JP2018/025713
Authority: WO
Inventors: 孝通小栗; 横山　雅之
Original assignee: 三菱電機株式会社
Priority date: 2018-07-06
Filing date: 2018-07-06
Publication date: 2020-01-09
Also published as: JP6918241B2; JPWO2020008626A1

Abstract

A valve seat (2) of this check valve (1) has an annular introduction port (2c) that is disposed on an end section on a cam shaft (20) side of a center bolt (30), and introduces working oil supplied from the cam shaft (20) into the center bolt (30). A valve body (3) has a circular oil hole (3b) on the inner circumference side from the annular introduction port (2c), and the valve body (3) is provided between the end section on the cam shaft (20) side of the center bolt (30) and the valve seat (2) and opens and closes the introduction port (2c). A spring (4) urges the valve body (3) in the direction toward the introduction port (2c).

Description

Check valve, oil control valve, and valve timing adjustment device

The present invention relates to a check valve, an oil control valve, and a valve timing adjusting device.

The oil control valve for driving the valve timing adjusting device of the engine is installed in the rotor of the valve timing adjusting device (for example, see Patent Document 1). The oil control valve is provided in a connection passage that connects an external oil pump and a working hydraulic chamber of the valve timing adjusting device, and is a check valve that prevents the flow of the working oil from the working hydraulic chamber toward the oil pump. Is provided. The check valve has a hemispherical bottom portion in which the connection passage abuts on a valve seat that is opened on the inner diameter side, and a cylindrical portion having a communication hole. The hydraulic oil that has flowed into the oil control valve via the connection passage opened to the valve seat hits the hemispherical bottom of the check valve, flows toward the outer peripheral side of the cylinder, and passes through the communication hole of the cylinder to form an inner portion of the cylinder. It enters the peripheral side and then flows out to the working hydraulic chamber.

JP 2014-156810 A

(4) The conventional check valve requires a communication hole for returning the hydraulic oil once directed to the outer peripheral side to the inner peripheral side, so that the flow path becomes complicated and the shaft length becomes longer. If an attempt is made to shorten the axial length of the check valve, the flow path of the hydraulic oil returning from the outer peripheral side to the inner peripheral side of the check valve will meander greatly, and the flow rate efficiency will decrease. As described above, the conventional check valve has a problem that the flow rate efficiency is reduced when the shaft length is reduced.

The present invention has been made to solve the above-described problems, and has as its object to shorten the shaft length without lowering the flow rate efficiency.

The check valve according to the present invention introduces hydraulic oil supplied from an oil pump by axially moving a spool installed inside a center bolt for fastening a rotor and a camshaft of a valve timing adjusting device. A check valve provided with an oil control valve that switches the tip to the advance hydraulic chamber or the retard hydraulic chamber of the valve timing adjusting device, which is installed at the end of the center bolt on the camshaft side and supplied from an oil pump. A valve seat having an annular introduction port for introducing hydraulic oil into the center bolt, and a circular oil hole on the inner peripheral side from the introduction port, between the cam shaft end of the center bolt and the valve seat. It is provided with a valve body provided to open and close the introduction port, and a check valve spring for urging the valve body toward the introduction port.

According to this invention, the hydraulic oil flows from the annular introduction port of the valve seat to the oil hole of the valve element located on the inner peripheral side of the annular introduction port, and flows into the spool coaxial with the oil hole. I do. Therefore, the flow path of the hydraulic oil becomes simple, and the shaft length can be shortened without reducing the flow rate efficiency.

FIG. 2 is a cross-sectional view illustrating a configuration example of a valve timing adjustment device according to the first embodiment. FIG. 2 is a plan view illustrating a configuration example of a valve timing adjustment device according to the first embodiment. It is sectional drawing to which the center bolt of FIG. 1 was expanded. It is sectional drawing to which the check valve of FIG. 1 was expanded. FIG. 5 is a plan view of the check valve of FIG. 4 as viewed from a valve seat side. FIG. 5 is a diagram showing a reference example for helping understanding of the check valve according to the first embodiment. FIG. 7 is a cross-sectional view illustrating a configuration example of a check valve according to a second embodiment.

Hereinafter, in order to explain this invention in greater detail, the preferred embodiments of the present invention will be described with reference to the accompanying drawings.
Embodiment 1 FIG.
FIG. 1 is a cross-sectional view illustrating a configuration example of a valve timing adjustment device 10 according to the first embodiment. FIG. 2 is a plan view showing a configuration example of the valve timing adjustment device 10 according to the first embodiment. In FIG. 2, the plate 13 is not shown. The valve timing adjusting device 10 adjusts the opening / closing timing of an intake valve or an exhaust valve (not shown) driven by the camshaft 20 by changing a rotation phase between a crankshaft (not shown) of the engine and the camshaft 20. Advancement of the rotation of the camshaft 20 with respect to the crankshaft is referred to as “advancing”, and delaying the rotation of the camshaft 20 with respect to the crankshaft is referred to as “retarding”. The valve timing adjusting device 10 shown in FIG. 2 is in a state where the camshaft 20 is advanced.

The case 11 has a plurality of shoes 11a protruding from the inner periphery to form a plurality of operating hydraulic chambers. The rotor 12 has a plurality of vanes 12a that partition the working hydraulic chamber of the case 11 into an advanced hydraulic chamber 11b and a retard hydraulic chamber 11c. With the rotor 12 housed inside the case 11, the plate 13, the case 11, and the cover 14 are fastened by a plurality of bolts 15 to be integrated. By the integration, both surfaces of the case 11 are closed by the plate 13 and the cover 14, and the working hydraulic chamber is sealed. The case 11, the plate 13, and the cover 14 constitute a first rotating body. The second rotating body is constituted by the rotor 12. The second rotating body is rotatable relative to the first rotating body.

スプ A sprocket 11d is formed on the outer peripheral surface of the case 11. The rotating force of the crankshaft of the engine is transmitted to the case 11 by a chain (not shown) mounted on the sprocket 11d, and the first rotating body constituted by the case 11, the plate 13, and the cover 14 rotates synchronously with the crankshaft. On the other hand, the rotor 12 is fastened to the camshaft 20 by the center bolt 30, and rotates synchronously with the camshaft.

A plurality of advance oil passages 12b and a plurality of retard oil passages 12c are formed inside the rotor 12. Each advance oil passage 12b communicates with each advance hydraulic chamber 11b, and each retard oil passage 12c communicates with each retard hydraulic chamber 11c. A lock pin 12d is provided on at least one of the vanes 12a of the rotor 12 so as to be movable in the axial direction. When the lock pin 12d receives the urging force of the spring 12e and engages with the engagement hole of the plate 13, the relative rotation between the first rotating body and the second rotating body is locked. Hydraulic oil is supplied to the lock pin release oil passage 12f communicating with the retard hydraulic chamber 11c, and when the oil pressure in the lock pin release oil passage 12f increases, the lock pin 12d comes out of the engagement hole of the plate 13, and The first rotator and the second rotator can be relatively rotated.

The center bolt 30 fastens the rotor 12 and the camshaft 20 together. Here, FIG. 3 is an enlarged sectional view of the center bolt 30 of FIG. The center bolt 30 functions as an oil control valve that switches the introduction destination of the hydraulic oil supplied from the oil pump 40 to the advance hydraulic chamber 11b or the retard hydraulic chamber 11c of the valve timing adjustment device 10.

An axially long spool accommodating portion 31 is formed inside the center bolt 30. The spool accommodating portion 31 accommodates a spool 32 and a spring 33 for urging the spool 32 toward the electromagnetic valve 50. . Further, inside the center bolt 30, an advance port 34 for communicating the spool housing portion 31 with the advance oil passage 12b of the rotor 12 and a retard oil passage 12c of the spool housing portion 31 and the rotor 12 are communicated. A retard port 35 is formed.

The spool 32 is disposed coaxially with the shaft 51 of the solenoid valve 50, and one end of the spool 32 is pressed by the shaft 51 and moves in the axial direction. The spool 32 has a hollow structure, and has a communication hole 32a that communicates the inside and the outside. As shown in FIG. 3, when the spool 32 is moved to the solenoid valve 50 side by the urging force of the spring 33, hydraulic oil is introduced into the advance port 34 from the open end of the spool 32 on the camshaft 20 side. You. On the other hand, when the spool 32 is moved toward the camshaft 20 by the pressing force of the shaft 51 of the solenoid valve 50, the communication hole 32a faces the retard port 35, and the hydraulic oil in the spool 32 is delayed from the communication hole 32a. It is introduced into the corner port 35.

供給 A supply port 31a communicating with the supply oil passage 21 of the camshaft 20 is formed on the camshaft 20 side of the spool housing portion 31. A hook portion 30a is formed on the outer peripheral surface of the spool housing portion 31 on the camshaft 20 side.

逆 A check valve 1 is provided at an end of the center bolt 30 on the camshaft 20 side. Here, FIG. 4 shows an enlarged sectional view of the check valve 1 of FIG. FIG. 5 is a plan view of the check valve 1 of FIG. 4 as viewed from the valve seat 2 side. The check valve 1 includes a valve seat 2, a valve body 3, and a spring 4.

The valve seat 2 has a cylindrical portion 2a attached to the end of the center bolt 30 on the camshaft 20 side, and an end surface portion 2b for closing an opening of the cylindrical portion 2a. In the example of FIG. 4, a concave portion 2e is formed on the outer peripheral surface of the cylindrical portion 2a, and the hook portion 30a of the center bolt 30 is engaged with the concave portion 2e, so that the valve seat 2 is attached to the center bolt 30. In addition, an annular introduction port 2c for introducing the hydraulic oil supplied from the oil pump 40 into the spool accommodating portion 31 of the center bolt 30 is opened on the outer peripheral side of the end face portion 2b. In the example of FIG. 5, portions connecting the inner peripheral side and the outer peripheral side of the end face portion 2 b are formed at four positions in the annular introduction port 2 c, but the number of the connection portions is arbitrary.

部位 A portion of the end face portion 2b that is in contact with the valve body 3 on the inner peripheral surface of the introduction port 2c is a tapered portion 2d. The tapered portion 2d has a tapered shape whose diameter increases from the center bolt 30 side to the camshaft 20 side. Further, a valve seat filter 5 is provided at the introduction port 2c. The valve seat 2 is a resin molded product. Note that the valve seat 2 may be an integrally molded product that is integrated with the valve seat filter 5 with a resin.

The valve element 3 is installed inside the valve seat 2 and is movable in the axial direction. The valve body 3 has a cylindrical portion 3a which is slightly smaller than the cylindrical portion 2a of the valve seat 2, and an oil hole 3b which is an opening of the cylindrical portion 3a. The oil hole 3b is a circular hole located on the inner peripheral side of the annular introduction port 2c, and serves as a flow path for supplying the hydraulic oil introduced into the introduction port 2c to the supply port 31a of the center bolt 30. The portion of the inner peripheral surface of the oil hole 3b of the valve body 3 that contacts the valve seat 2 is a tapered portion 3c. The tapered portion 3c has a tapered shape whose diameter increases from the center bolt 30 side toward the camshaft 20 side. The valve body 3 is a resin molded product. A spring 4 for urging the valve 3 toward the introduction port 2c is provided inside the valve 3.

The hydraulic pressure on the upstream side of the valve body 3, that is, the hydraulic pressure of the hydraulic oil in the supply oil passage 21 of the camshaft 20 is higher than the hydraulic pressure on the downstream side of the valve body 3, that is, the hydraulic pressure of the hydraulic oil in the supply port 31a of the spool housing 31. When the pressure is high, the upstream hydraulic pressure acts on one end surface of the cylindrical portion 3a on the introduction port 2c side, and the spring 4 is compressed, so that the one end surface of the cylindrical portion 3a is separated from the introduction port 2c. When the valve element 3 opens the introduction port 2c, the flow of hydraulic oil (indicated by an arrow in FIG. 4) from the oil pump 40 toward the spool housing portion 31 is allowed. When the valve is opened, as shown by the arrow in FIG. 4, the hydraulic oil flows into the valve seat 2 from the introduction port 2 c on the outer peripheral side of the end face 2 b and passes through the oil hole 3 b on the inner peripheral side of the valve body 3. Then, the oil flows into the spool 32 from the supply port 31a coaxial with the oil hole 3b. Therefore, the flow path of the hydraulic oil becomes simple, and the shaft length can be shortened without reducing the flow rate efficiency. On the other hand, when the oil pressure on the downstream side of the valve element 3 is higher than the oil pressure on the upstream side, the valve element 3 is urged by the spring 4 and sits on the introduction port 2c. When the valve body 3 closes the introduction port 2c, the flow of hydraulic oil from the spool housing portion 31 toward the oil pump 40 is prevented.

Here, the flow of hydraulic oil from the oil pump 40 to the valve timing adjustment device 10 will be described.
When the camshaft 20 is advanced, an ECU (Electronic Control Unit) 60 stops supplying power to the connector 52 of the solenoid valve 50. As a result, the spool 32 is urged by the spring 33 and moves toward the solenoid valve 50, and the supply port 31a and the advance port 34 communicate. The hydraulic oil supplied by the oil pump 40 passes through the supply oil passage 21 of the camshaft 20 and the introduction port 2c of the check valve 1, flows into the supply port 31a, and is advanced from the supply port 31a to the advance port 34 and the advance oil. It is introduced into the advanced hydraulic chamber 11b through the path 12b. The hydraulic oil in the retard hydraulic chamber 11c is discharged from the retard oil passage 12c through a drain oil passage (not shown). When the hydraulic oil is supplied to the advance hydraulic chamber 11b, the second rotating body rotates clockwise with respect to the first rotating body, and the relative phase of the camshaft 20 with respect to the crankshaft advances.

When the camshaft 20 is retarded, the ECU 60 causes the shaft 51 to protrude from the solenoid valve 50 by supplying power to the connector 52 of the solenoid valve 50. As a result, the spool 32 moves toward the camshaft 20, the communication hole 32a of the spool 32 partially faces the retard port 35, and the supply port 31a communicates with the retard port 35. The hydraulic oil supplied by the oil pump 40 passes through the supply oil passage 21 of the camshaft 20 and the introduction port 2c of the check valve 1, flows into the supply port 31a, and flows from the supply port 31a to the retard port 35 and the retard oil. It passes through the path 12c and is introduced into the retard hydraulic chamber 11c. The hydraulic oil in the advance hydraulic chamber 11b is discharged from the advance oil passage 12b through a drain oil passage (not shown). When the hydraulic oil is supplied to the retard hydraulic chamber 11c, the second rotating body rotates counterclockwise with respect to the first rotating body, and the relative phase of the camshaft 20 with respect to the crankshaft is retarded.

When hydraulic oil is supplied from the oil pump 40 to the advance hydraulic chamber 11b and the retard hydraulic chamber 11c as described above, the advance hydraulic chamber 11b and the retard hydraulic chamber are caused by the alternating torque acting on the rotor 12. There is a case where the hydraulic oil flows backward from 11c to the oil pump 40 side. The check valve 1 prevents this backflow.

FIG. 6 is a diagram showing a reference example for helping the understanding of the check valve 1 according to the first embodiment. The check valve 100 of the reference example shown in the cross-sectional view of FIG. 6 is provided at the end of the center bolt 30 shown in FIG. The check valve 100 of the reference example includes a valve seat 102, a valve body 103, a spring 104, and a valve seat filter 105. The valve seat 102 is installed at an end of the center bolt 30 on the camshaft 20 side. The valve seat 102 has a circular introduction port 102c that opens on the inner peripheral side. The inlet port 102c is provided with a valve seat filter 105. The valve body 103 has a cylindrical portion 103a and a disk portion 103b. The disk portion 103b has a shape that closes the circular introduction port 102c. The spring 104 urges the valve body 103 in the direction of the introduction port 102c. In the check valve 100 of this reference example, the hydraulic oil flows from the introduction port 102c of the valve seat 102 to the gap between the valve body 103 and the valve seat 102 on the outer peripheral side from the introduction port 102c and is coaxial with the gap. It flows into the upper supply port 31b.

In the configuration of the check valve 100 of this reference example, the hydraulic oil that has flowed into the introduction port 102c hits the disk portion 103b of the valve body 103, flows to the outer peripheral side of the cylindrical portion 103a, and flows into the outer peripheral supply port 31b. Therefore, a communication hole (not shown) for communicating the supply port 31b with the spool 32 is required to return the hydraulic oil once directed to the outer circumference to the inner circumference, that is, inside the spool 32, and the flow path is complicated. become. In addition, the meandering flow path lowers the flow rate efficiency.

As described above, the check valve 1 according to the first embodiment includes the valve seat 2, the valve body 3, and the spring 4. The valve seat 2 is provided at an end of the center bolt 30 on the camshaft 20 side, and has an annular introduction port 2 c for introducing hydraulic oil supplied from the camshaft 20 into the center bolt 30. The valve element 3 has a circular oil hole 3b on the inner peripheral side of the annular introduction port 2c, and is provided between the end of the center bolt 30 on the camshaft 20 side and the valve seat 2 to close the introduction port 2c. Open and close. The spring 4 urges the valve element 3 toward the introduction port 2c. With this configuration, the hydraulic oil flows from the annular introduction port 2c of the valve seat 2 to the oil hole 3b of the valve body 3 located on the inner peripheral side of the annular introduction port 2c, and is coaxial with the oil hole 3b. It flows into a certain spool 32. Therefore, the check valve 1 has a simpler flow path of hydraulic oil than the reference example of FIG. 6, and can shorten the axial length of the check valve 1 without lowering the flow rate efficiency. Since the axial length of the check valve 1 can be shortened, the check valve 1 can be downsized.

The valve seat 2 of the first embodiment has a cylindrical portion 2a attached to an end of the center bolt 30 on the camshaft 20 side. Thereby, the cylindrical portion 2a serves as a guide when the valve 3 is closed. Therefore, the displacement of the valve body 3 with respect to the valve seat 2 is reduced, and the sealing performance is improved.

The valve body 3 of the first embodiment has a cylindrical portion 3a guided on the inner peripheral surface of the cylindrical portion 2a of the valve seat 2. Thereby, the cylindrical portion 3a serves as a guide when the valve body 3 moves in the axial direction and a guide for the spring 4. Therefore, the movement of the valve element 3 becomes smooth, and the flow rate efficiency is further improved.

Further, in the first embodiment, the valve seat 2 includes an inner peripheral surface of the introduction port 2c and the tapered portion 2d that contacts the valve body 3, and an inner peripheral surface of the oil hole 3b of the valve body 3 and includes the valve seat. Each of the tapered portions 3c abutting on 2 has a tapered shape whose diameter increases from the center bolt 30 side toward the camshaft 20 side. Thereby, the flow of the hydraulic oil becomes smooth, and the flow rate efficiency is further improved.

Further, in the first embodiment, a hook portion 30a is provided at an end of the center bolt 30 on the camshaft 20 side, and a concave portion 2e which engages with the hook portion 30a is provided in the valve seat 2 of the check valve 1. ing. The mounting structure of the check valve 1 to the center bolt 30 is a snap-fit structure including the hook portion 30a and the concave portion 2e, so that assemblability is improved.

The valve seat 2 and the valve body 3 of the first embodiment are resin molded products. This eliminates the need for processing the inlet port 2c and the like of the valve seat 2 and processing of the oil hole 3b and the like of the valve body 3, thereby improving mass productivity and reducing costs.

In addition, the valve seat 2 of the first embodiment is provided with the valve seat filter 5 at the introduction port 2c. The valve seat filter 5 prevents foreign matter from entering downstream of the check valve 1, thereby improving the reliability of the oil control valve and the valve timing adjusting device 10. In this case, by integrally molding the valve seat 2 and the valve seat filter 5 with resin, the step of assembling the valve seat filter 5 to the valve seat 2 can be eliminated, thereby improving mass productivity and reducing costs. be able to.

Embodiment 2 FIG.
FIG. 7 is a cross-sectional view illustrating a configuration example of the check valve 1 according to the second embodiment. In FIG. 7, the same or corresponding portions as those in FIGS. 1 to 5 are denoted by the same reference numerals, and description thereof will be omitted.

The check valve 1 according to the first embodiment has a configuration in which the valve seat filter 5 is provided at the introduction port 2c of the valve seat 2. On the other hand, the check valve 1 according to the second embodiment has a configuration in which the valve element filter 6 is provided in the oil hole 3 b of the valve element 3. The valve body filter 6 prevents foreign matter from entering downstream of the check valve 1, thereby improving the reliability of the oil control valve and the valve timing adjusting device 10. In this case, since the valve body 3 and the valve body filter 6 are integrally formed of resin, the step of assembling the valve body filter 6 to the valve body 3 can be eliminated, thereby improving mass productivity and reducing costs. be able to.

By using the check valve 1 according to the first and second embodiments for an oil control valve, it is possible to improve the flow rate efficiency and reduce the size of the oil control valve. Further, by using the oil control valve provided with the check valve 1 according to the first and second embodiments for the valve timing adjusting device 10, the flow rate efficiency of the valve timing adjusting device 10 can be improved and the size can be reduced. it can.

In the first and second embodiments, the center bolt 30 is provided with the hook 30a and the valve seat 2 is provided with the recess 2e. On the contrary, the center bolt 30 is provided with the recess and the hook is provided in the valve seat 2. It may be provided.

Within the scope of the present invention, any combination of each embodiment, modification of any component of each embodiment, or omission of any component of each embodiment is possible within the scope of the present invention.

Since the check valve according to the present invention has a reduced shaft length without reducing the flow rate efficiency, it is suitable for use as a check valve incorporated in an oil control valve that drives a valve timing adjusting device. .

1,100 check valve, 2,102 valve seat, 2a cylinder (valve seat cylinder), 2b end face, 2c, 102c introduction port, 2d taper, 2e recess, 3,103 valve body, 3a, 103a cylinder Part (valve body cylindrical part), 3b oil hole, 3c taper part, 4,104 spring (check valve spring), 5,105 valve seat filter, 6 valve valve filter, 10 valve timing adjustment device, 11 case, 11a shoe , 11b advance hydraulic chamber, 11c retard hydraulic chamber, 11d sprocket, 12 rotor, 12a vane, 12b advance oil path, 12c retard oil path, 12d lock pin, 12e spring, 12f lock pin release oil path, 13 plate , 14 cover, 15 bolt, 20 camshaft, 21 supply Road, 30 center bolt (oil control valve), 30a hook, 31 spool housing, 31a, 31b supply port, 32 spool, 32a communication hole, 33 spring, 34 advance port, 35 retard port, 40 oil pump, 50 solenoid valve, 51 shaft, 52 connector, 60 ECU, 103b disc.

Claims

The spool installed inside the center bolt for fastening the rotor and the camshaft of the valve timing adjusting device moves in the axial direction, so that the introduction destination of the hydraulic oil supplied from the oil pump advances to the valve timing adjusting device. A check valve provided with an oil control valve that switches to an angular hydraulic chamber or a retard hydraulic chamber,
A valve seat provided at an end of the center bolt on the camshaft side and having an annular introduction port for introducing the hydraulic oil supplied from the oil pump into the center bolt;
A valve body that has a circular oil hole on the inner peripheral side from the introduction port, and is provided between the end portion of the center bolt on the camshaft side and the valve seat to open and close the introduction port;
A check valve spring for urging the valve body toward the introduction port.
The check valve according to claim 1, wherein the valve seat has a valve seat cylindrical portion attached to an end of the center bolt on the camshaft side.
The check valve according to claim 2, wherein the valve body has a valve body cylindrical portion guided on an inner peripheral surface of the valve seat cylindrical portion.
The part of the valve seat that is the inner peripheral surface of the introduction port and abuts on the valve body, and the part of the valve body that is the inner peripheral surface of the oil hole and abuts on the valve seat, The check valve according to claim 1, wherein the check valve has a tapered shape whose diameter increases from the center bolt side toward the camshaft side.
When one of a hook portion and a concave portion is provided at an end of the center bolt on the camshaft side,
The valve seat has one of a concave portion and a hook portion that is engaged with one of the hook portion and the concave portion provided at an end of the center bolt on the oil pump side. Item 1. The check valve according to Item 1.
The check valve according to claim 1, wherein a valve seat filter is provided at the introduction port of the valve seat.
逆 The check valve according to claim 1, wherein the valve seat is a resin molded product.
7. The check valve according to claim 6, wherein the valve seat is an integrally molded product integrated with the valve seat filter by a resin.
2. The check valve according to claim 1, wherein a valve filter is provided in the oil hole of the valve.
逆 The check valve according to claim 1, wherein the valve body is a resin molded product.
The check valve according to claim 9, wherein the valve element is an integrally molded product integrated with the valve element filter by a resin.
An oil control valve comprising the check valve according to claim 1.
A valve timing adjusting device having an oil control provided with the check valve according to claim 1.