WO2018135584A1 - Valve timing adjustment device and check valve - Google Patents

Abstract

A supply check valve (61) that: permits the flow of hydraulic oil when the valve is opened, from a hydraulic oil supply source (8) side to a pressure accumulation space (500) side via a supply oil passage (54); and, when the valve is closed, restricts the flow of hydraulic oil from the pressure accumulation space (500) side to the hydraulic oil supply source (8) side via the supply oil passage (54). A recycle check valve (62) that: permits the flow of hydraulic oil, when the valve is opened, from a retard chamber- or advance chamber-side to the pressure accumulation space (500) side via a recycled oil passage (57); and, when the valve is closed, restricts the flow of hydraulic oil from the pressure accumulation space (500) side to the retard chamber- or advance chamber-side via the recycled oil passage (57). The characteristics pertaining to the opening of the supply check valve (61) differ from the characteristics pertaining to the opening of the recycle check valve (62).

Description

Valve timing adjusting device and check valve Cross-reference of related applications

This application is based on Patent Application No. 2017-7516 filed on January 19, 2017 and Patent Application No. 2017-2446489 filed on December 22, 2017. The description is incorporated.

This disclosure relates to a valve timing adjusting device and a check valve.

2. Description of the Related Art Conventionally, there is known a valve timing adjusting device that is provided in a power transmission path that transmits power from a driving shaft of an internal combustion engine to a driven shaft and adjusts valve timings of intake valves and exhaust valves that are driven to open and close by the driven shaft. In the case of a hydraulic type, the valve timing adjusting device includes a housing that rotates in conjunction with one of a drive shaft and a driven shaft, and a vane rotor that is fixed to the other end of the drive shaft and the driven shaft, and the vane rotor in the housing. The hydraulic oil is supplied to one of the first hydraulic chamber and the second hydraulic chamber that form a compartment, thereby rotating the vane rotor relative to the housing in the advance direction or the retard direction. The hydraulic oil is supplied by an oil passage switching valve.

US Patent Application Publication No. 2016/0024978 US Patent No. 7600531

For example, in the valve timing adjusting device of Patent Document 1, a supply oil passage for supplying hydraulic oil to a pressure accumulation space in the spool, a first hydraulic chamber or a second hydraulic chamber, and a pressure accumulation in a spool constituting the oil path switching valve. A recycle oil passage formed so as to be connectable to the space is formed. The recycle oil path enables reuse of hydraulic oil from the first hydraulic chamber and the second hydraulic chamber. On the radially inner side of the spool with respect to the supply oil passage, the hydraulic oil flow from the hydraulic oil supply source side to the pressure accumulation space side via the supply oil passage is permitted, and the hydraulic oil from the pressure accumulation space side via the supply oil passage is allowed. A supply check valve for restricting the flow of hydraulic oil to the supply source side is provided. Therefore, the backflow of the hydraulic oil from the pressure accumulation space side to the hydraulic oil supply source side can be suppressed. Also, on the inner side in the radial direction of the spool with respect to the recycle oil passage, the flow of hydraulic oil from the first hydraulic chamber or the second hydraulic chamber side to the pressure accumulation space side via the recycle oil passage is allowed and recycled from the pressure accumulation space side. A recycle check valve is provided for restricting the flow of hydraulic oil to the first hydraulic chamber or the second hydraulic chamber via the oil passage. Therefore, it is possible to suppress the backflow of hydraulic oil from the pressure accumulation space side to the first hydraulic chamber or the second hydraulic chamber side via the recycle oil passage.

By the way, the supply check valve and the recycle check valve have different characteristics regarding valve opening that should be given priority in consideration of pressure loss, response time, and the like. However, in the valve timing adjusting device of Patent Document 1, no consideration is given to the characteristics related to the opening of each of the supply check valve and the recycle check valve. For this reason, the valve opening pressures of the supply check valve and the recycle check valve may be set to be the same. Therefore, when the valve opening pressure of the supply check valve is set higher than an appropriate value and is difficult to open, the pressure loss when the hydraulic oil passes through the supply check valve increases and is supplied to each hydraulic chamber. There is a risk of increased hydraulic oil pressure loss. In addition, when the valve opening pressure of the recycle check valve is set lower than an appropriate value and the valve is easy to open, the recycle check valve cannot follow high-frequency positive and negative cam torque fluctuations at high rotation, and valve timing There is a possibility that the responsiveness of the adjusting device is lowered.
A first object of the present disclosure is to provide a valve timing adjusting device with low pressure loss of hydraulic oil supplied to a hydraulic chamber and high response.

Further, for example, in Patent Document 2, the flow of fluid that is provided inside a cylindrical tubular member having an inflow hole that communicates the outer peripheral wall and the inner peripheral wall and that flows toward the inner side of the cylindrical member via the inflow hole. A check valve that allows and restricts the flow of fluid from the inside of the cylindrical member toward the inflow hole is disclosed. Here, the check valve includes a valve body formed into a cylindrical shape by winding a single plate material. The valve body has a full range of curvature from the inner end to the outer end of the portion between the inner end that is one end in the circumferential direction and the outer end that is the other end in the circumferential direction. Is constant. For this reason, when the check valve is deformed and opened to shrink radially inward due to the flow of fluid from the inflow hole on the inner side of the cylindrical member, the inner end serves as a support point, and the load is applied to a position about 90 ° from the position. There is a risk of generating a large stress due to the bias. This may cause deformation or breakage of the check valve.
The second object of the present disclosure is to provide a check valve capable of suppressing stress generated during deformation.

A first aspect of the present disclosure is a valve timing adjustment device that is provided in a power transmission path that transmits power from a drive shaft to a driven shaft of an internal combustion engine and adjusts a valve timing of a valve that is driven to open and close by the driven shaft. , A housing, a vane rotor, a sleeve, a spool, a supply check valve, and a recycle check valve.

When one of the drive shaft and the driven shaft is a first shaft and the other of the drive shaft and the driven shaft is a second shaft, the housing rotates in conjunction with the first shaft and is fitted to the end of the second shaft. The second shaft is rotatably supported.

The vane rotor is fixed to the end of the second shaft and has a vane that divides the internal space of the housing into a first hydraulic chamber on one side in the circumferential direction and a second hydraulic chamber on the other side in the circumferential direction. It rotates relative to the housing according to the pressure of the hydraulic oil supplied from the source to the first hydraulic chamber and the second hydraulic chamber.

The sleeve is formed in a cylindrical shape, and has a supply port communicating with the hydraulic oil supply source, a first control port communicating with the first hydraulic chamber, and a second control port communicating with the second hydraulic chamber. is doing.

The spool is formed in a cylindrical shape so as to be capable of reciprocating in the axial direction inside the sleeve, and a pressure accumulation space formed inside, a supply oil passage formed to connect the pressure accumulation space and the supply port, and a pressure accumulation space And a control oil passage formed so as to be connectable to the first control port or the second control port, and a recycle oil passage formed so as to be connectable between the pressure accumulation space and the first control port or the second control port. ing. The recycle oil path enables reuse of hydraulic oil from the first hydraulic chamber and the second hydraulic chamber.

When the supply check valve is opened, it allows the flow of hydraulic oil from the hydraulic oil supply source side through the supply oil passage to the pressure accumulation space side.When the valve is closed, the supply check valve passes through the supply oil passage from the pressure accumulation space side. Thus, the flow of hydraulic oil toward the hydraulic oil supply source side is regulated. Therefore, the backflow of the hydraulic oil from the pressure accumulation space side to the hydraulic oil supply source side can be suppressed. Thereby, when the supply pressure of the hydraulic oil supply source is low, it is possible to suppress the hydraulic oil from flowing from the oil passage switching valve side to the hydraulic oil supply source side.

The recycle check valve allows the flow of hydraulic oil from the first hydraulic chamber or the second hydraulic chamber side to the pressure accumulation space side through the recycle oil passage when the valve is opened, and from the pressure accumulation space side when the valve is closed. The flow of hydraulic oil toward the first hydraulic chamber or the second hydraulic chamber via the recycle oil passage is regulated. Therefore, it is possible to suppress the backflow of the hydraulic oil from the pressure accumulation space side to the first hydraulic chamber or the second hydraulic chamber side. Thereby, the responsiveness of the valve timing adjusting device can be enhanced in a configuration in which the hydraulic oil can be reused.

In this disclosure, the characteristics related to the opening of the supply check valve are different from the characteristics related to the opening of the recycle check valve. Here, considering the degree of pressure loss, for example, if the valve opening pressure of the supply check valve is relatively low and set to a characteristic that is easy to open, the pressure loss when the hydraulic oil passes through the supply check valve decreases, The pressure loss of the hydraulic oil supplied to each hydraulic chamber can be reduced. Also, for example, considering the followability, if the valve opening pressure of the recycle check valve is relatively high and set to a characteristic that makes it difficult to open, the recycle check valve will follow high-frequency positive and negative cam torque fluctuations at high revolutions. And the responsiveness of the valve timing adjusting device can be improved.

The second aspect of the present disclosure is provided inside a cylindrical tubular member having an inflow hole that communicates the outer peripheral wall and the inner peripheral wall, and allows the flow of fluid toward the inner side of the cylindrical member via the inflow hole. And it is a check valve which can regulate the flow of the fluid which goes to the inflow hole from the inside of a cylinder member, Comprising: The valve main body is provided. The valve body is formed in a cylindrical shape by winding a single plate material.

When the check valve is in a free state, the valve body has a constant curvature at a specific portion between an inner end that is one end in the circumferential direction and an outer end that is the other end in the circumferential direction. It has a small curvature part with a curvature smaller than the curvature of a constant curvature part in parts other than a curvature part and the said constant curvature part of the circumferential direction. Therefore, when the check valve is deformed so as to shrink radially inward due to the fluid flow from the inflow hole inside the cylindrical member, the timing at which the deformation of the portion on the inner end side of the valve body starts is set on the outer end side. Can be delayed with respect to the site. As a result, the inner end serves as a support point, and it is possible to suppress the occurrence of stress due to the bias of the load at a position of about 90 ° from the position. Therefore, deformation or breakage of the check valve can be suppressed.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings. The drawing
FIG. 1 is a cross-sectional view showing a valve timing adjusting device according to a first embodiment. FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1, showing only the housing and the vane rotor; FIG. 3A is a view showing a check valve of the valve timing adjusting device according to the first embodiment; FIG. 3B is a view of FIG. 3A as viewed from the direction of arrow IIIB. FIG. 3C is an expanded view of the check valve. FIG. 4 is a cross-sectional view showing the valve timing adjusting device according to the second embodiment, FIG. 5A is a view showing a check valve of the valve timing adjusting device according to the second embodiment; 5B is a cross-sectional view taken along line VB-VB of FIG. 5A. FIG. 5C is a diagram showing a supply check valve; 6A is a cross-sectional view taken along line VIA-VIA of FIG. 4 and shows only a spool and a check valve; 6B is a cross-sectional view taken along the line VIB-VIB of FIG. 4 and shows only the spool and the check valve. FIG. 7 is a cross-sectional view showing a part of the valve timing adjusting device according to the third embodiment. FIG. 8 is a cross-sectional view showing a part of the valve timing adjusting device according to the fourth embodiment. FIG. 9 is a cross-sectional perspective view showing a spool and a check valve of the valve timing adjusting device according to the fourth embodiment. FIG. 10 is a cross-sectional view showing a part of the valve timing adjusting apparatus according to the fifth embodiment. FIG. 11 is a cross-sectional view showing an oil passage switching valve of a valve timing adjusting device according to a sixth embodiment. 12 is a cross-sectional view taken along line XII-XII of FIG. FIG. 13 is a view showing a check valve of the valve timing adjusting device according to the sixth embodiment, FIG. 14 is a view of FIG. 13 viewed from the direction of arrow XIV. FIG. 15 is a diagram illustrating a state at the time of maximum deformation of the check valve of the valve timing adjusting device according to the sixth embodiment, FIG. 16 is a view showing a check valve according to the first comparative embodiment, FIG. 17 is a diagram illustrating a state at the time of maximum deformation of the check valve according to the first comparative embodiment, FIG. 18 is a view showing a check valve according to the second comparative embodiment, FIG. 19 is a diagram showing a state at the time of maximum deformation of the check valve according to the second comparative embodiment, FIG. 20 is a diagram showing the relationship between the angle from the inner end of the valve body and the magnitude of the generated stress at the maximum deformation of the valve body, FIG. 21 is a view showing a check valve according to the seventh embodiment. FIG. 22 is a view showing a check valve according to the eighth embodiment. FIG. 23 is a view showing a check valve according to the ninth embodiment. FIG. 24 is a perspective view showing a check valve according to the tenth embodiment, FIG. 25 is a diagram when FIG. 24 is viewed from the direction of the arrow XXV. FIG. 26 is a view showing a check valve according to the third comparative embodiment.

Hereinafter, valve timing adjustment devices according to a plurality of embodiments of the present disclosure will be described with reference to the drawings. Note that, in a plurality of embodiments, substantially the same components are denoted by the same reference numerals, and description thereof is omitted.
(First embodiment)

A valve timing adjusting device according to a first embodiment of the present disclosure is shown in FIG. The valve timing adjusting device 10 changes the rotational phase of the camshaft 3 with respect to the crankshaft 2 of the engine 1 as an internal combustion engine to thereby change the intake valve 4 of the intake valve 4 or the exhaust valve 5 that the camshaft 3 is driven to open and close. The valve timing is adjusted. The valve timing adjusting device 10 is provided in a power transmission path from the crankshaft 2 to the camshaft 3. The crankshaft 2 corresponds to a “drive shaft”. The cam shaft 3 corresponds to a “driven shaft”.
The configuration of the valve timing adjusting device 10 will be described with reference to FIGS. 1 and 2.
The valve timing adjusting device 10 includes a housing 20, a vane rotor 30, and an oil passage switching valve 11.

The housing 20 includes a sprocket 21 and a case 22. The sprocket 21 is fitted to the end of the cam shaft 3. The camshaft 3 supports the sprocket 21 in a rotatable manner. The chain 6 is wound around the sprocket 21 and the crankshaft 2. The sprocket 21 rotates in conjunction with the crankshaft 2. The case 22 has a bottomed cylindrical shape, and an open end is fixed to the sprocket 21 by a bolt 12 while being combined with the sprocket 21. The case 22 has a plurality of partition walls 23 protruding radially inward. An opening 24 that opens to a space outside the case 22 is formed at the center of the bottom of the case 22. The opening 24 is located on the side opposite to the camshaft 3 with respect to the vane rotor 30.

The vane rotor 30 includes a boss 31 and a plurality of vanes 32. The boss 31 has a cylindrical shape and is fixed to the end of the cam shaft 3. The vane 32 protrudes between the partition walls 23 toward the radially outer side from the boss 31. The internal space 200 of the housing 20 is partitioned into a retard chamber 201 and an advance chamber 202 by a vane 32. The retard chamber 201 corresponds to the “first hydraulic chamber” and is located on one side in the circumferential direction with respect to the vane 32. The advance chamber 202 corresponds to the “second hydraulic chamber” and is located on the other side in the circumferential direction with respect to the vane 32. The vane rotor 30 rotates relative to the housing 20 in the retard direction or the advance direction according to the hydraulic pressure in the retard chamber 201 and the advance chamber 202.
The oil passage switching valve 11 has a sleeve 40, a spool 50, and a check valve 60.
The sleeve 40 includes an inner sleeve 41, an outer sleeve 42, a supply port 43, a first control port 44, a second control port 45, and a locking portion 47.

The inner sleeve 41 is formed of a metal having a relatively low hardness, such as aluminum. The inner sleeve 41 has a sleeve tube portion 411 and a sleeve bottom portion 412. The sleeve tube portion 411 is formed in a substantially cylindrical shape. The sleeve bottom 412 is formed integrally with the sleeve cylinder 411 so as to close one end of the sleeve cylinder 411.

The outer sleeve 42 is made of a metal such as iron. The outer sleeve 42 has a sleeve cylinder portion 421 and a screw portion 422. The sleeve cylinder portion 421 is formed in a substantially cylindrical shape. The screw part 422 is formed on the outer wall of one end of the sleeve cylinder part 421.

The inner sleeve 41 is provided inside the outer sleeve 42 so that the sleeve bottom portion 412 side faces the screw portion 422 side. Here, the outer wall of the inner sleeve 41 and the inner wall of the outer sleeve 42 are fitted. A substantially cylindrical inner space 400 is formed inside the sleeve cylinder portion 411 of the inner sleeve 41 inside the sleeve cylinder portion 421 of the outer sleeve 42.

The supply port 43 is formed so as to connect the outer wall and the inner wall of the sleeve tube portion 411 of the inner sleeve 41. The outer wall of the end portion on the sleeve bottom portion 412 side of the sleeve tube portion 411 of the inner sleeve 41 is partially cut away in the circumferential direction. Thereby, a notch oil passage 431 is formed between the sleeve tube portion 411 and the sleeve tube portion 421. The inner space 400 communicates with the space outside the sleeve 40 via the supply port 43 and the notch oil passage 431.

The first control port 44 is formed so as to connect the outer wall of the sleeve tube portion 421 of the outer sleeve 42 and the inner wall of the sleeve tube portion 411 of the inner sleeve 41. A plurality of first control ports 44 are formed in the circumferential direction of the sleeve 40.

The second control port 45 is formed to connect the outer wall of the sleeve tube portion 421 of the outer sleeve 42 and the inner wall of the sleeve tube portion 411 of the inner sleeve 41. A plurality of second control ports 45 are formed in the circumferential direction of the sleeve 40.
The supply port 43, the first control port 44, and the second control port 45 are formed in this order so as to be arranged at a predetermined interval from one end side of the sleeve 40 toward the other end side. .
The locking portion 47 is formed in an annular shape so as to protrude radially outward from the outer wall on the other end side of the sleeve cylindrical portion 421.

A shaft hole 100 and a supply hole 101 are formed at the end of the cam shaft 3 on the valve timing adjusting device 10 side. The shaft hole portion 100 is formed so as to extend in the axial direction of the cam shaft 3 from the center of the end surface of the cam shaft 3 on the valve timing adjusting device 10 side. The supply hole 101 is formed to extend radially inward from the outer wall of the cam shaft 3 and communicate with the shaft hole 100.
On the inner wall of the shaft hole portion 100 of the cam shaft 3, a shaft side screw portion 110 that can be screwed to the screw portion 422 of the sleeve 40 is formed.

The sleeve 40 passes through the inside of the boss 31 of the vane rotor 30 and is fixed to the camshaft 3 so that the screw portion 422 is coupled to the shaft-side screw portion 110 of the camshaft 3. At this time, the locking portion 47 of the sleeve 40 locks the end surface of the boss 31 of the vane rotor 30 opposite to the camshaft 3. Accordingly, the vane rotor 30 is fixed to the cam shaft 3 so as to be sandwiched between the cam shaft 3 and the locking portion 47. Thus, the sleeve 40 is provided in the central part of the vane rotor 30.

An oil pump 8 is connected to the supply hole 101. The oil pump 8 pumps up the hydraulic oil stored in the oil pan 7 and supplies it to the supply hole 101. As a result, the hydraulic oil flows into the shaft hole 100. Here, the oil pump 8 corresponds to a “operating oil supply source”.
The hydraulic fluid that has flowed into the shaft hole portion 100 flows into the inner space 400 via the notch oil passage 431 and the supply port 43.

Further, in a state where the sleeve 40 is provided in the central portion of the vane rotor 30, the first control port 44 communicates with the retard chamber 201 via the retard oil passage 301 formed in the boss 31. The second control port 45 communicates with the advance chamber 202 via an advance oil passage 302 formed in the boss 31.
The spool 50 includes a spool cylinder portion 51, a spool lid portion 52, a spool bottom portion 53, a supply oil passage 54, a first control oil passage 55 and a second control oil passage 56 as a control oil passage, and a recycle oil passage 57. Yes.

The spool cylinder portion 51 is formed in a substantially cylindrical shape. The spool lid portion 52 is provided so as to close one end portion of the spool cylinder portion 51. In the present embodiment, the spool lid portion 52 is formed separately from the spool cylinder portion 51. The spool bottom 53 is formed integrally with the spool cylinder 51 so as to close the other end of the spool cylinder 51. A substantially cylindrical pressure accumulation space 500 is formed between the inner wall of the spool cylinder portion 51, the spool lid portion 52, and the spool bottom portion 53.

The supply oil passage 54 is formed so as to connect an annular recess formed in the outer wall of the spool cylinder 51 and the inner wall of the spool cylinder 51. In the present embodiment, four supply oil passages 54 are formed at equal intervals in the circumferential direction of the spool 50. The inner diameter of one supply oil passage 54 is set to be the same as the inner diameter of the other supply oil passage 54.

The first control oil passage 55 is formed so as to connect an annular recess formed in the outer wall of the spool cylinder 51 and the inner wall of the spool cylinder 51. In the present embodiment, four first control oil passages 55 are formed at equal intervals in the circumferential direction of the spool 50.

The second control oil passage 56 is formed so as to connect an annular recess formed in the outer wall of the spool cylinder 51 and the inner wall of the spool cylinder 51. In the present embodiment, four second control oil passages 56 are formed at equal intervals in the circumferential direction of the spool 50.

The recycle oil passage 57 is formed so as to connect an annular recess formed in the outer wall of the spool cylinder 51 and the inner wall of the spool cylinder 51. In the present embodiment, four recycling oil passages 57 are formed at equal intervals in the circumferential direction of the spool 50. The inner diameter of one recycled oil passage 57 is set to be the same as the inner diameter of the other recycled oil passage 57. Further, the inner diameter of one recycle oil passage 57 is set to be the same as the inner diameter of the supply oil passage 54. Therefore, the total flow area of the recycle oil passage 57 is the same as the total flow area of the supply oil passage 54.
The supply oil passage 54, the first control oil passage 55, the recycle oil passage 57, and the second control oil passage 56 are spaced in this order from one end side of the spool 50 toward the other end side. It is formed so as to be lined up.
The spool 50 is provided inside the sleeve 40, that is, in the inner space 400 such that the spool lid portion 52 faces the sleeve bottom portion 412. The spool 50 can reciprocate in the axial direction in the inner space 400.

A locking portion 71 is provided on the opposite side to the sleeve bottom portion 412 of the spool tube portion 51. The locking portion 71 is formed in an annular shape, and is provided so that the outer edge portion is fitted to the inner wall of the outer sleeve 42. The locking portion 71 can lock the end portion of the spool cylinder portion 51 opposite to the spool bottom portion 53. As a result, the spool 50 is prevented from coming off on the side opposite to the sleeve bottom 412.

The spool 50 forms a variable volume space 401 between the spool lid portion 52 and the sleeve bottom portion 412 in the inner space 400 of the sleeve 40. The volume of the variable volume space 401 changes when the spool 50 reciprocates in the axial direction.

A spring 72 is provided between the spool lid 52 and the sleeve bottom 412. The spring 72 urges the spool 50 toward the locking portion 71. As a result, the spool 50 is pressed against the locking portion 71.

A linear solenoid 9 is provided on the opposite side of the spool 50 from the cam shaft 3. The linear solenoid 9 presses the spool 50 against the urging force of the spring 72 toward the camshaft 3 when energized. As a result, the spool 50 changes its axial position with respect to the sleeve 40. The movable range of the spool 50 is from a position where the spool 50 abuts on the locking portion 71 to a position where the spool 50 abuts on the sleeve bottom 412.
The supply oil passage 54 communicates with the supply port 43 regardless of the position of the spool 50 in the axial direction with respect to the sleeve 40.

When the spool 50 is in a position where it abuts against the locking portion 71 (see FIG. 1), the first control oil passage 55 and the first control port 44 communicate with each other, and the second control port 45 and the recycle oil passage 57 communicate with each other. To do. As a result, the oil pump 8 and the retard chamber 201 are connected, and the advance chamber 202 and the recycled oil passage 57 are connected.

When the spool 50 is in a position where it abuts against the sleeve bottom 412, the second control oil passage 56 and the second control port 45 communicate with each other, and the first control port 44 and the recycle oil passage 57 communicate with each other. Thereby, the oil pump 8 and the advance chamber 202 are connected, and the retard chamber 201 and the recycled oil passage 57 are connected.

When the spool 50 is at an intermediate position between the locking portion 71 and the sleeve bottom portion 412, the first control oil passage 55, the recycle oil passage 57, the second control oil passage 56, the first control port 44, and the second control port 45 Communication is blocked. As a result, both the retard chamber 201 and the advance chamber 202 are closed.
As shown in FIG. 3, the check valve 60 includes a supply check valve 61, a recycle check valve 62, and a shaft portion 63.

The check valve 60 is formed by winding a thin metal plate 600 as shown in FIG. 3C, for example. The thin plate 600 is set to have a substantially uniform thickness, and includes a supply check valve corresponding portion 601, a recycle check valve corresponding portion 602, and a shaft portion corresponding portion 603. The supply check valve corresponding part 601, the recycle check valve corresponding part 602, and the shaft part corresponding part 603 are formed in a rectangular plate shape. The supply check valve corresponding portion 601 and the recycle check valve corresponding portion 602 are each formed integrally with the shaft portion corresponding portion 603 so as to extend from the longitudinal side of the shaft portion corresponding portion 603 in the short direction. Here, when the width of the supply check valve corresponding unit 601 is w1 and the width of the recycle check valve corresponding unit 602 is w2, the supply check valve corresponding unit 601 and the recycle check valve corresponding unit 602 satisfy the relationship of w1 <w2. It is formed (see FIG. 3C). The check valve 60 is formed by winding a shaft portion corresponding portion 603, a supply check valve corresponding portion 601, and a recycle check valve corresponding portion 602 in the short direction of the shaft portion corresponding portion 603.
The shaft portion 63 is formed in a substantially cylindrical shape (see FIGS. 3A and 3B). The shaft portion 63 does not overlap the plate material, that is, the shaft portion corresponding portion 603 in the circumferential direction.

The supply check valve 61 is formed in a substantially cylindrical shape so as to extend radially outward from the vicinity of one end of the shaft portion 63 and make one round around the shaft portion 63 (see FIGS. 3A and 3B). Thereby, the supply check valve 61 is formed to be elastically deformable in the radial direction. When the supply check valve 61 is deformed radially inward, the outer diameter is reduced. More specifically, the supply check valve 61 has a portion in which plate members, that is, supply check valve corresponding portions 601 overlap each other in the circumferential direction. When this overlap becomes large, it deforms radially inward and contracts in the radial direction, and when the overlap becomes small, it deforms radially outward and expands in the radial direction. A space inside the supply check valve 61 formed in a substantially cylindrical shape is opened in the axial direction of the check valve 60.

The recycle check valve 62 is formed in a substantially cylindrical shape so as to extend radially outward from the shaft portion 63 and make one round around the shaft portion 63 (see FIGS. 3A and 3B). Thereby, the recycle check valve 62 is formed to be elastically deformable in the radial direction. When the recycle check valve 62 is deformed radially inward, the outer diameter is reduced. More specifically, the recycle check valve 62 has a portion in which plate members, that is, the recycle check valve corresponding portions 602 overlap each other in the circumferential direction (see FIG. 3B). When this overlap becomes large, it deforms radially inward and contracts in the radial direction, and when the overlap becomes small, it deforms radially outward and expands in the radial direction. A space inside the recycle check valve 62 formed in a substantially cylindrical shape is opened in the axial direction of the check valve 60.

Here, the width of the supply check valve 61, that is, the length in the axial direction is w1. The width of the recycle check valve 62, that is, the length in the axial direction is w2 (see FIGS. 3A and 3C). Therefore, the supply check valve 61 and the recycle check valve 62 are formed so as to satisfy the relationship of w1 <w2. Therefore, the supply check valve 61 is easily deformed in the radial direction as compared with the recycle check valve 62. That is, when the same radial force is applied to the supply check valve 61 and the recycle check valve 62, the supply check valve 61 has a larger deformation than the recycle check valve 62.

The check valve 60 is provided in the pressure accumulation space 500 so that the supply check valve 61 corresponds to the supply oil passage 54 and the recycle check valve 62 corresponds to the recycle oil passage 57 (see FIG. 1). The shaft portion 63 is located between the spool lid portion 52 and the spool bottom portion 53 and supports the supply check valve 61 and the recycle check valve 62.

When the hydraulic oil travels from the oil pump 8 side via the supply oil passage 54 to the pressure accumulating space 500 side, the supply check valve 61 is deformed and opened radially inward by the outer peripheral surface being pushed by the hydraulic oil, A gap is formed between the inner wall of the spool 50 and the supply check valve 61. As a result, the hydraulic oil can flow into the pressure accumulation space 500 via the supply oil passage 54. On the other hand, when the hydraulic oil moves from the pressure accumulating space 500 side to the oil pump 8 side via the supply oil passage 54, the supply check valve 61 is deformed radially outward by the inner peripheral surface being pushed by the hydraulic oil and closed. Then, it sticks to the inner wall of the spool 50 so as to close the supply oil passage 54. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulation space 500 via the supply oil passage 54. In this manner, the supply check valve 61 allows the flow of hydraulic oil from the oil pump 8 side via the supply oil passage 54 to the pressure accumulation space 500 side, and from the pressure accumulation space 500 side via the supply oil passage 54. The flow of hydraulic oil toward the oil pump 8 is restricted.

When the hydraulic oil travels from the retarded angle chamber 201 or the advanced angle chamber 202 side to the pressure accumulating space 500 side via the recycle oil passage 57, the recycle check valve 62 is radially inward by pushing the outer peripheral surface by the hydraulic oil. The valve is deformed and opened, and a gap is formed between the inner wall of the spool 50 and the recycle check valve 62. As a result, the hydraulic oil can flow into the pressure accumulating space 500 via the recycle oil passage 57. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side via the recycle oil passage 57 to the retarded angle chamber 201 or the advanced angle chamber 202 side, the recycle check valve 62 has a diameter by pushing the inner peripheral surface by the hydraulic oil. It deforms outward in the direction and closes, and sticks to the inner wall of the spool 50 so as to close the recycled oil passage 57. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulation space 500 via the recycle oil passage 57. As described above, the recycle check valve 62 allows the flow of hydraulic oil from the retard chamber 201 or the advance chamber 202 side through the recycle oil passage 57 to the accumulator space 500 side, and recycle oil from the accumulator space 500 side. The flow of hydraulic oil toward the retard chamber 201 or the advance chamber 202 via the path 57 is restricted.

As described above, the supply check valve 61 is easily deformed in the radial direction as compared with the recycle check valve 62. In addition, the total flow area of the recycle oil passage 57 is the same as the total flow area of the supply oil passage 54. Therefore, the valve opening pressure of the supply check valve 61 is set lower than the valve opening pressure of the recycle check valve 62. That is, it can be said that the characteristics related to the opening of the supply check valve 61 are set to be easier to open than the recycle check valve 62.

In the present embodiment, the supply check valve 61 has a relatively low valve opening pressure and is set to a characteristic that is easy to open, so that the backflow of hydraulic oil from the pressure accumulation space 500 side to the oil pump 8 side is suppressed. The pressure loss of the hydraulic oil from the oil pump 8 side to the pressure accumulation space 500 side can be reduced.

When the valve timing adjusting device 10 rotates at a high speed, high-frequency positive and negative cam torque fluctuations act on the recycle check valve 62. Therefore, there is a concern that the recycle check valve 62 cannot follow the cam torque fluctuation. However, in the present embodiment, the recycle check valve 62 has a characteristic that the valve opening pressure is relatively high and is difficult to open, so that the pressure accumulation space 500 side to the retarding chamber 201 or the advance chamber 202 side. The recycle check valve 62 can follow the cam torque fluctuation while suppressing the backflow of the hydraulic oil.
In the present embodiment, the sleeve 40 further has a breathing hole 402.

The breathing hole 402 is formed so as to be recessed radially inward from the outer wall of the inner sleeve 41 and extend in the axial direction of the inner sleeve 41 (see FIG. 1). That is, the breathing hole 402 is formed between the inner sleeve 41 and the outer sleeve 42 outside the inner space 400. The breathing hole 402 is formed so as to communicate with the variable volume space 401 and the outside of the valve timing adjusting device 10, that is, the space opposite to the variable volume space 401 of the sleeve 40, that is, the atmosphere. Thereby, the pressure of the volume variable space 401 can be made equivalent to atmospheric pressure.

The oil passage switching valve 11 presses the spool 50 by driving the linear solenoid 9 and connects the advance chamber 202 and the recycled oil passage 57 while connecting the oil pump 8 and the retard chamber 201. A second operating state in which the retard chamber 201 and the recycled oil passage 57 are connected while the oil pump 8 and the advance chamber 202 are connected, and a holding state in which both the retard chamber 201 and the advance chamber 202 are closed. And operate. In the first operation state, the hydraulic oil is returned from the advance chamber 202 to the pressure accumulation space 500 while the hydraulic oil is supplied to the retard chamber 201. In the second operation state, the hydraulic oil is returned from the retard chamber 201 to the pressure accumulating space 500 while the hydraulic oil is supplied to the advance chamber 202. In the hold state, the hydraulic oil in the retard chamber 201 and the advance chamber 202 is held.

This embodiment further includes a lock pin 73 (see FIGS. 1 and 2). The lock pin 73 is formed in a bottomed cylindrical shape, and is accommodated in an accommodation hole 321 formed in the vane 32 so as to be reciprocally movable in the axial direction. A spring 74 is provided inside the lock pin 73. The spring 74 biases the lock pin 73 toward the sprocket 21 side. A fitting recess 25 is formed on the vane 32 side of the sprocket 21.

The lock pin 73 can be inserted into the insertion recess 25 when the vane rotor 30 is at the most retarded position with respect to the housing 20. When the lock pin 73 is fitted in the fitting recess 25, the relative rotation of the vane rotor 30 with respect to the housing 20 is restricted. On the other hand, when the lock pin 73 is not inserted into the insertion recess 25, relative rotation of the vane rotor 30 with respect to the housing 20 is allowed.

Between the lock pin 73 of the vane 32 and the retard chamber 201, a pin control oil passage 303 communicating with the retard chamber 201 is formed. Further, a pin control oil passage 304 communicating with the advance chamber 202 is formed between the lock pin 73 of the vane 32 and the advance chamber 202 (see FIG. 2). The pressure of the hydraulic oil flowing into the pin control oil passages 303 and 304 from the retard chamber 201 or the advance chamber 202 acts in a direction in which the lock pin 73 comes out of the fitting recess 25 against the urging force of the spring 74.
In the valve timing adjusting device 10 configured as described above, when hydraulic oil is supplied to the retard chamber 201 or the advance chamber 202, the hydraulic oil flows into the pin control oil paths 303 and 304, and the lock pin 73 is The vane rotor 30 comes out of the fitting recess 25 and is allowed to rotate relative to the housing 20.

When the rotational phase of the camshaft 3 is on the more advanced side than the target value, the valve timing adjusting device 10 sets the oil passage switching valve 11 to the first operating state. As a result, the vane rotor 30 rotates relative to the housing 20 in the retarding direction, and the rotational phase of the camshaft 3 changes toward the retarding side.

Further, the valve timing adjusting device 10 places the oil passage switching valve 11 in the second operating state when the rotational phase of the camshaft 3 is retarded from the target value. As a result, the vane rotor 30 rotates relative to the housing 20 in the advance direction, and the rotational phase of the camshaft 3 changes toward the advance side.
Further, the valve timing adjusting device 10 brings the oil passage switching valve 11 into a holding state when the rotational phase of the camshaft 3 matches the target value. Thereby, the rotational phase of the cam shaft 3 is maintained.

In the present embodiment, since the pressure of the variable volume space 401 is equal to the atmospheric pressure by the breathing hole 402, when the linear solenoid 9 presses the spool 50, the spool 50 is axially inside the sleeve 40. Smooth reciprocation. When hydraulic oil accumulates in the variable volume space 401, the hydraulic oil passes through the breathing hole 402 and the valve timing adjusting device 10, which is the space opposite to the camshaft 3, with respect to the oil passage switching valve 11. It is discharged to the outside, that is, to the atmosphere and returned to the oil pan 7.

As described above, this embodiment adjusts the valve timing of the intake valve 4 that is provided in the power transmission path that transmits power from the crankshaft 2 to the camshaft 3 of the engine 1 and that is driven to open and close by the camshaft 3. The valve timing adjusting device 10 includes a housing 20, a vane rotor 30, a sleeve 40, a spool 50, a supply check valve 61, and a recycle check valve 62.
When one of the crankshaft 2 and the camshaft 3 is a first shaft and the other of the crankshaft 2 and the camshaft 3 is a second shaft, the housing 20 rotates in conjunction with the first shaft, and the end of the second shaft And is rotatably supported by the second shaft.

The vane rotor 30 is fixed to the end of the second shaft, and includes a vane 32 that partitions the internal space 200 of the housing 20 into a retard chamber 201 on one side in the circumferential direction and an advance chamber 202 on the other side in the circumferential direction. The oil pump 8 rotates relative to the housing 20 according to the pressure of the hydraulic oil supplied to the retard chamber 201 and the advance chamber 202.

The sleeve 40 is formed in a cylindrical shape, and includes a supply port 43 communicating with the oil pump 8, a first control port 44 communicating with the retard chamber 201, and a second control port communicating with the advance chamber 202. 45.

The spool 50 is formed in a cylindrical shape so as to be reciprocally movable in the axial direction on the inner side of the sleeve 40, and the pressure accumulation space 500 formed on the inner side, the pressure accumulation space 500 and the supply port 43 are connected to each other. The first control oil passage 55 formed so that the oil passage 54, the pressure accumulation space 500 and the first control port 44 can be connected, and the second control oil passage formed so that the pressure accumulation space 500 and the second control port 45 can be connected. 56, and a recycle oil passage 57 formed so that the pressure accumulation space 500 and the first control port 44 or the second control port 45 can be connected. The recycle oil passage 57 allows the hydraulic oil from the retard chamber 201 and the advance chamber 202 to be reused.

When the supply check valve 61 is opened, the flow of hydraulic oil from the oil pump 8 side to the pressure accumulation space 500 side via the supply oil passage 54 is allowed, and when the valve is closed, the supply oil is supplied from the pressure accumulation space 500 side. The flow of hydraulic oil toward the oil pump 8 via the path 54 is restricted. Therefore, the backflow of the hydraulic oil from the pressure accumulation space 500 side to the oil pump 8 side can be suppressed. Thereby, when the supply pressure of the oil pump 8 is low, it is possible to suppress the hydraulic oil from flowing from the oil passage switching valve 11 side to the oil pump 8 side.

When the recycle check valve 62 is opened, the recycle check valve 62 allows the flow of hydraulic oil from the retard chamber 201 or the advance chamber 202 side through the recycle oil passage 57 to the accumulator space 500 side. The flow of hydraulic oil from the space 500 side to the retard chamber 201 or the advance chamber 202 side via the recycle oil passage 57 is regulated. Therefore, it is possible to suppress the backflow of hydraulic oil from the pressure accumulation space 500 side to the retard chamber 201 or the advance chamber 202 side. Thereby, the responsiveness of the valve timing adjustment apparatus 10 can be improved in the structure which can recycle hydraulic fluid.

In this embodiment, the characteristics related to the opening of the supply check valve 61 are different from the characteristics related to the opening of the recycle check valve 62. Here, considering the degree of pressure loss, for example, if the valve opening pressure of the supply check valve 61 is set to be relatively low and the valve opening characteristic is set to be easy to open, the pressure loss when the hydraulic oil passes through the supply check valve 61 is reduced. In addition, the pressure loss of the hydraulic oil supplied to each hydraulic chamber can be reduced. Further, for example, considering the followability, if the valve opening pressure of the recycle check valve 62 is relatively high and set to a characteristic that is difficult to open, the recycle check valve 62 can be changed to high-frequency positive and negative cam torque fluctuations at high revolutions. Accordingly, the responsiveness of the valve timing adjusting device 10 can be improved.

Further, in the present embodiment, the characteristics related to the opening of the supply check valve 61 are set to characteristics that are easier to open than the recycle check valve 62. Therefore, as described above, the pressure loss of the hydraulic oil supplied to each hydraulic chamber can be reduced and the responsiveness of the valve timing adjusting device 10 can be improved.

In this embodiment, the valve opening pressure of the supply check valve 61 is set lower than the valve opening pressure of the recycle check valve 62. That is, the characteristics related to the opening of the supply check valve 61 are set to characteristics that are easier to open than the recycle check valve 62.

In the present embodiment, the supply check valve 61 is provided inside the spool 50 and closes the supply oil passage 54 when the valve is closed. The recycle check valve 62 is provided inside the spool 50 and closes the recycle oil passage 57 when the valve is closed. In the present embodiment, since the supply check valve 61 and the recycle check valve 62 are both provided inside the spool 50, manufacturing is easy.

In the present embodiment, the supply check valve 61 and the recycle check valve 62 are formed of elastically deformable plates, and have different widths. In the present embodiment, the characteristics regarding the valve opening are made different by making the widths of the supply check valve 61 and the recycle check valve 62 different.
In the present embodiment, the sleeve 40 is disposed at the center of the vane rotor 30. That is, in the present embodiment, the sleeve 40 and the spool 50 that constitute the oil passage switching valve 11 are provided in the central portion of the vane rotor 30. As a result, the oil passage between the oil passage switching valve 11 and the retard chamber 201 and the advance chamber 202 can be shortened, and the responsiveness of the valve timing adjusting device 10 can be improved.

(Second Embodiment)
A valve timing adjusting device according to a second embodiment of the present disclosure is shown in FIG. The second embodiment differs from the first embodiment in the configuration of the spool 50 and the check valve 60.

In the present embodiment, five supply oil passages 54 are formed at equal intervals in the circumferential direction of the spool 50 (see FIG. 6A). The inner diameter of one supply oil passage 54 is set to be the same as the inner diameter of the other supply oil passage 54. As in the first embodiment, four recycle oil passages 57 are formed at equal intervals in the circumferential direction of the spool 50 (see FIG. 6B). The inner diameter of one recycled oil passage 57 is set to be the same as the inner diameter of the other recycled oil passage 57. Further, the inner diameter of one recycle oil passage 57 is set to be the same as the inner diameter of the supply oil passage 54. Therefore, the total flow area of the supply oil path 54 is larger than the total flow area of the recycle oil path 57.
The check valve 60 includes a supply check valve 61, a recycle check valve 62, and a support member 64.

The supply check valve 61, the recycle check valve 62, and the support member 64 are formed separately from each other. As in the first embodiment, the supply check valve 61 and the recycle check valve 62 are formed in a substantially cylindrical shape by, for example, winding a thin metal plate into a cylindrical shape (see FIG. 5). The supply check valve 61 is formed to be elastically deformable in the radial direction. When the supply check valve 61 is deformed radially inward, the outer diameter is reduced. More specifically, the supply check valve 61 has a portion in which the plate materials overlap each other in the circumferential direction (see FIG. 5C). When this overlap becomes large, it deforms radially inward and contracts in the radial direction, and when the overlap becomes small, it deforms radially outward and expands in the radial direction. A space inside the supply check valve 61 formed in a substantially cylindrical shape is opened in the axial direction of the check valve 60. The recycle check valve 62 is formed to be elastically deformable in the radial direction. When the recycle check valve 62 is deformed radially inward, the outer diameter is reduced. More specifically, the recycle check valve 62 has a portion in which the plate materials overlap each other in the circumferential direction. When this overlap becomes large, it deforms radially inward and contracts in the radial direction, and when the overlap becomes small, it deforms radially outward and expands in the radial direction. A space inside the recycle check valve 62 formed in a substantially cylindrical shape is opened in the axial direction of the check valve 60.

Here, when the width of the supply check valve 61, that is, the length in the axial direction is w3, and the width of the recycle check valve 62, that is, the length in the axial direction is w4, the supply check valve 61 and the recycle check valve 62 are , W3 = w4 (see FIG. 5A). Therefore, the ease of deformation of the supply check valve 61 in the radial direction is equivalent to that of the recycle check valve 62. In other words, when the same radial force is applied to the supply check valve 61 and the recycle check valve 62, the deformation amount of the supply check valve 61 and the deformation amount of the recycle check valve 62 are the same.

As shown in FIGS. 5A and 5B, the support member 64 is formed in a shape such that, for example, two rectangular plates are orthogonal to each other. Therefore, the support member 64 is formed so that the cross-sectional shape by a plane orthogonal to the longitudinal direction is substantially a cross (see FIGS. 5B and 6).

The support member 64 has notches 641 and 642. The cutout portion 641 is formed so as to be cut out inward from the outer edge portion of one end portion in the longitudinal direction of the support member 64. Four notches 641 are formed at equal intervals in the circumferential direction of the support member 64. The cutout 642 is formed so as to be cut out inward from the outer edge portion on the other end side in the longitudinal direction of the support member 64. Four notches 642 are formed at equal intervals in the circumferential direction of the support member 64.

The supply check valve 61 is provided in the notch 641 of the support member 64. The supply check valve 61 can be deformed radially inward at the notch 641. The length of the support member 64 in the longitudinal direction of the notch 641 is set to be slightly larger than the length w3 of the supply check valve 61 in the axial direction. The notch 641 can regulate the relative movement of the supply check valve 61 in the axial direction with respect to the support member 64.

The recycle check valve 62 is provided in the notch 642 of the support member 64. The recycle check valve 62 can be deformed radially inward at the notch 642. The length in the longitudinal direction of the support member 64 of the notch 642 is set slightly larger than the axial length w4 of the recycle check valve 62. The notch 642 can restrict the relative movement of the recycle check valve 62 in the axial direction with respect to the support member 64.

The check valve 60 is provided in the pressure accumulation space 500 so that the supply check valve 61 corresponds to the supply oil passage 54 and the recycle check valve 62 corresponds to the recycle oil passage 57 (see FIG. 4). The support member 64 is positioned between the spool lid portion 52 and the spool bottom portion 53 and supports the supply check valve 61 and the recycle check valve 62.

When the hydraulic oil travels from the oil pump 8 side via the supply oil passage 54 to the pressure accumulating space 500 side, the supply check valve 61 is deformed and opened radially inward by the outer peripheral surface being pushed by the hydraulic oil, A gap is formed between the inner wall of the spool 50 and the supply check valve 61. As a result, the hydraulic oil can flow into the pressure accumulation space 500 via the supply oil passage 54. On the other hand, when the hydraulic oil moves from the pressure accumulating space 500 side to the oil pump 8 side via the supply oil passage 54, the supply check valve 61 is deformed radially outward by the inner peripheral surface being pushed by the hydraulic oil and closed. Then, it sticks to the inner wall of the spool 50 so as to close the supply oil passage 54. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulation space 500 via the supply oil passage 54.

When the hydraulic oil travels from the retarded angle chamber 201 or the advanced angle chamber 202 side to the pressure accumulating space 500 side via the recycle oil passage 57, the recycle check valve 62 is radially inward by pushing the outer peripheral surface by the hydraulic oil. The valve is deformed and opened, and a gap is formed between the inner wall of the spool 50 and the recycle check valve 62. As a result, the hydraulic oil can flow into the pressure accumulating space 500 via the recycle oil passage 57. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side via the recycle oil passage 57 to the retarded angle chamber 201 or the advanced angle chamber 202 side, the recycle check valve 62 has a diameter by pushing the inner peripheral surface by the hydraulic oil. It deforms outward in the direction and closes, and sticks to the inner wall of the spool 50 so as to close the recycled oil passage 57. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulation space 500 via the recycle oil passage 57.

As described above, the ease of deformation of the supply check valve 61 in the radial direction is equivalent to that of the recycle check valve 62. Further, the total flow area of the supply oil passage 54 is larger than the total flow area of the recycle oil passage 57. Therefore, the valve opening pressure of the supply check valve 61 is set lower than the valve opening pressure of the recycle check valve 62. That is, it can be said that the characteristics related to the opening of the supply check valve 61 are set to be easier to open than the recycle check valve 62.
The second embodiment is the same as the first embodiment except for the points described above. Therefore, about the structure similar to 1st Embodiment, there can exist an effect similar to 1st Embodiment.

As described above, in this embodiment, the supply check valve 61 and the recycle check valve 62 are formed of elastically deformable plate materials having the same width and thickness. The total flow area of the supply oil passage 54 is different from the total flow area of the recycle oil passage 57. As a result, the characteristics relating to the opening of the supply check valve 61 and the characteristics relating to the opening of the recycle check valve 62 are differentiated. In the present embodiment, the supply check valve 61 and the recycle check valve 62 are formed with the same specifications (width, plate thickness). Thereby, the supply check valve 61 and the recycle check valve 62 can be arranged at predetermined positions without being distinguished. Therefore, it is easy to manufacture without worrying about misassembly.

Further, in the present embodiment, the supply oil passage 54 has the same inner diameter as the inner diameter of the recycle oil passage 57, and the number formed in the spool 50 is different from that of the recycle oil passage 57. As a result, the characteristics relating to the opening of the supply check valve 61 and the characteristics relating to the opening of the recycle check valve 62 are differentiated. Further, since the inner diameter of the supply oil passage 54 and the inner diameter of the recycle oil passage 57 are the same, the supply oil passage 54 and the recycle oil passage 57 can be formed by one cutting tool such as a drill. Therefore, manufacture is easy.

(Third embodiment)
A part of the valve timing adjusting device according to the third embodiment of the present disclosure is shown in FIG. The third embodiment is different from the first embodiment in the configuration of the sleeve 40, the spool 50, the check valve 60, and the like.
The sleeve 40 is made of a metal such as iron. The sleeve 40 includes a sleeve tube portion 451, a sleeve bottom portion 452, and a screw portion 453.

The sleeve cylinder portion 451 is formed in a substantially cylindrical shape. The sleeve bottom 452 is formed integrally with the sleeve cylinder 451 so as to close one end of the sleeve cylinder 451. The screw portion 453 is formed on the outer wall of the end portion of the sleeve tube portion 451 on the sleeve bottom portion 452 side.
The sleeve 40 passes through the inside of the boss 31 of the vane rotor 30 and is fixed to the cam shaft 3 so that the screw portion 453 is coupled to the shaft-side screw portion 110 of the cam shaft 3.

A breathing hole 402 is formed in the sleeve bottom 452. The breathing hole 402 is formed so as to penetrate the center of the sleeve bottom 452 in the thickness direction. That is, the breathing hole 402 is connected to the volume variable space 401.

The breathing hole 402 is formed to communicate with the outside of the cam shaft 3. Therefore, the variable volume space 401 communicates with the outside of the camshaft 3, that is, the atmosphere via the breathing hole 402. Thereby, the pressure of the volume variable space 401 can be made equivalent to atmospheric pressure. In the present embodiment, since the pressure of the variable volume space 401 is equal to the atmospheric pressure by the breathing hole 402, when the linear solenoid 9 presses the spool 50, the spool 50 is axially inside the sleeve 40. Smooth reciprocation.
In the present embodiment, the supply port 43 is formed between the first control port 44 and the second control port 45. A plurality of supply ports 43 are formed in the circumferential direction of the sleeve 40.

The spool 50 includes a seal member 58 instead of the spool lid portion 52. The seal member 58 is formed in a substantially cylindrical shape, and is provided inside the spool cylinder portion 51. A substantially cylindrical pressure accumulation space 500 is formed between the outer wall of the seal member 58 and the inner wall of the spool cylinder portion 51.
In the present embodiment, the spool 50 has recycling oil paths 571 and 572 instead of the recycling oil path 57.

The recycle oil passage 571 is formed on the side opposite to the sleeve bottom portion 452 with respect to the supply oil passage 54 so as to connect an annular recess formed in the outer wall of the spool tube portion 51 and the inner wall of the spool tube portion 51. . A plurality of the recycle oil passages 571 are formed in the circumferential direction of the spool 50 and the same number as the supply ports 43. The inner diameter of one recycled oil passage 571 is set to be the same as the inner diameter of the other recycled oil passage 571. Further, the inner diameter of one recycle oil passage 571 is set smaller than the inner diameter of the supply port 43.

The recycle oil passage 572 is formed on the opposite side of the recycle oil passage 571 from the sleeve bottom portion 452 so as to connect the annular recess formed in the outer wall of the spool tube portion 51 and the inner wall of the spool tube portion 51. . A plurality of the recycle oil passages 572 are formed in the circumferential direction of the spool 50, and the same number as the recycle oil passages 571 is formed. The inner diameter of one recycled oil passage 572 is set to be the same as the inner diameter of the other recycled oil passage 572. Further, the inner diameter of one recycle oil passage 572 is set to be the same as the inner diameter of the recycle oil passage 571.
The total flow area of the supply port 43 is set larger than the total flow area of the recycle oil path 571 or the recycle oil path 572.
In the present embodiment, the first control oil passage 55, the second control oil passage 56, and the supply oil passage 54 are integrally formed between the recycle oil passage 571 and the recycle oil passage 572.
The check valve 60 includes a supply check valve 61 and recycle check valves 621 and 622.

The supply check valve 61 and the recycle check valves 621 and 622 are formed separately. As in the first embodiment, the supply check valve 61 and the recycle check valves 621 and 622 are formed by, for example, winding a thin metal plate into a cylindrical shape. Here, the plate thickness of the thin plate forming the supply check valve 61 is set smaller than the plate thickness of the thin plate forming the recycle check valves 621 and 622.

The supply check valve 61 is formed to be elastically deformable in the radial direction. When the supply check valve 61 is deformed radially inward, the outer diameter is reduced. The recycle check valves 621 and 622 are formed to be elastically deformable in the radial direction. When the recycle check valves 621 and 622 are deformed radially inward, the outer diameter is reduced.

Here, the inner diameter and outer diameter of the supply check valve 61 are set larger than the outer diameters of the recycle check valves 621 and 622. Further, the width of the supply check valve 61, that is, the length in the axial direction is the same as the length in the axial direction of the recycle check valves 621 and 622.

The supply check valve 61 has a plate thickness smaller than that of the recycle check valves 621 and 622 and an outer diameter larger than that of the recycle check valves 621 and 622. Compared to 622, it is easily deformed in the radial direction. That is, when the same radial force is applied to the supply check valve 61 and the recycle check valves 621 and 622, the supply check valve 61 has a larger deformation amount than the recycle check valves 621 and 622.

The supply check valve 61 is provided at a position corresponding to the supply port 43 between the sleeve 40 and the spool 50. The recycle check valve 621 is provided at a position corresponding to the recycle oil passage 571 between the spool cylinder 51 and the seal member 58. The recycle check valve 622 is provided at a position corresponding to the recycle oil passage 572 between the spool cylinder 51 and the seal member 58.

When the hydraulic oil travels from the oil pump 8 side to the pressure accumulating space 500 side via the supply oil passage 54, the supply check valve 61 is deformed radially inward and opened, and the inner wall of the sleeve 40, the supply check valve 61, A gap is formed between the two. As a result, the hydraulic oil can flow into the pressure accumulation space 500 via the supply port 43 and the supply oil passage 54. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side to the oil pump 8 side via the supply port 43, the supply check valve 61 is deformed radially outward and closed to close the supply port 43. Stick to 40 inner walls. As a result, the hydraulic oil is restricted from flowing out of the sleeve 40 from the pressure accumulation space 500 via the supply oil passage 54 and the supply port 43. In this way, the supply check valve 61 allows the flow of hydraulic oil from the oil pump 8 side via the supply oil passage 54 toward the pressure accumulation space 500 side, and allows oil to flow from the pressure accumulation space 500 side via the supply port 43. The flow of hydraulic oil toward the pump 8 side is restricted.

When the hydraulic oil travels from the retard chamber 201 or the advance chamber 202 side to the pressure accumulation space 500 side via the recycle oil passages 571 and 572, the recycle check valves 621 and 622 are respectively deformed radially inward to open the valve. In addition, a gap is formed between the inner wall of the spool 50 and the recycle check valves 621 and 622. As a result, the hydraulic oil can flow into the pressure accumulation space 500 via the recycle oil passages 571 and 572. On the other hand, when the hydraulic oil goes from the pressure accumulating space 500 side to the retard chamber 201 or the advance chamber 202 side via the recycle oil passages 571 and 572, the recycle check valves 621 and 622 are deformed radially outward and closed. Then, it sticks to the inner wall of the spool 50 so as to close the recycled oil passages 571 and 572. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulating space 500 via the recycle oil passages 571 and 572. In this way, the recycle check valves 621 and 622 allow the flow of hydraulic oil from the retard chamber 201 or the advance chamber 202 side to the accumulator space 500 via the recycle oil passages 571 and 572, and the accumulator space 500. The flow of hydraulic oil from the side toward the retard chamber 201 or the advance chamber 202 via the recycle oil passages 571 and 572 is restricted.

In this embodiment, when the spool 50 is in a position where it abuts against the locking portion 71 (see FIG. 7), the hydraulic oil is supplied to the advance chamber 202 via the second control port 45, and the retard chamber 201 The hydraulic oil flows through the first control port 44 into the concave portion on the radially outer side of the recycle oil passage 571. The hydraulic oil that has flowed into the recess is returned to the pressure accumulating space 500 via the recycle oil passage 571 and the recycle check valve 621.

When the spool 50 is in a position where it abuts against the sleeve bottom 452, the hydraulic oil is supplied to the retard chamber 201 via the first control port 44, and the hydraulic oil in the advance chamber 202 passes through the second control port 45. Via, it flows into the concave portion on the radially outer side of the recycle oil passage 572. The hydraulic oil that has flowed into the recess is returned to the pressure accumulating space 500 via the recycle oil passage 572 and the recycle check valve 622.

As described above, the supply check valve 61 is more easily deformed in the radial direction than the recycle check valves 621 and 622. Further, the total flow area of the supply port 43 is set to be larger than the total flow area of the recycle oil passage 571 or the recycle oil passage 572. Therefore, the valve opening pressure of the supply check valve 61 is set lower than the valve opening pressures of the recycle check valves 621 and 622. That is, it can be said that the characteristics related to the opening of the supply check valve 61 are set to characteristics that are easier to open than the recycle check valves 621 and 622.
The third embodiment is the same as the first embodiment except for the points described above. Therefore, about the structure similar to 1st Embodiment, there can exist an effect similar to 1st Embodiment.

As described above, in this embodiment, the supply check valve 61 is provided outside the spool 50 and closes the supply port 43 when the valve is closed. The recycle check valves 621 and 622 are provided inside the spool 50 and close the recycle oil passages 571 and 572 when the valves are closed. In the present embodiment, the supply check valve 61 and the recycle check valves 621 and 622 are different in the arrangement location in the oil passage switching valve 11. Therefore, erroneous assembly can be suppressed.

(Fourth embodiment)
A valve timing adjusting device according to a fourth embodiment of the present disclosure is shown in FIG. The fourth embodiment differs from the first embodiment in the configuration of the sleeve 40, the spool 50, the check valve 60, and the like.
Similar to the third embodiment, the sleeve 40 includes a sleeve tube portion 451, a sleeve bottom portion 452, and a screw portion 453.
The supply port 43 is formed so as to connect the outer wall and the inner wall of the sleeve tube portion 451. The supply port 43 communicates with the supply hole portion 101 via a cylindrical gap between the outer wall of the spool 50 and the inner wall of the shaft hole portion 100.
The first control port 44 is formed so as to connect the outer wall and the inner wall of the sleeve tube portion 451 on the locking portion 47 side with respect to the supply port 43.
The second control port 45 is formed to connect the outer wall and the inner wall of the sleeve tube portion 451 on the locking portion 47 side with respect to the first control port 44.

In the present embodiment, the pin control port 410 is formed between the supply port 43 and the first control port 44 so as to connect the outer wall and the inner wall of the sleeve cylindrical portion 451. The vane rotor 30 is also formed with a pin control oil passage 305 that connects the pin control port 410 and the accommodation hole 321. An insertion recess 26 into which the lock pin 73 can be inserted is formed on the vane 32 side of the case 22. The spring 74 biases the lock pin 73 toward the case 22 side. The pressure of the hydraulic oil flowing into the pin control port 410 and the pin control oil passage 305 acts in a direction in which the lock pin 73 comes out of the fitting recess 26 against the urging force of the spring 74. When the lock pin 73 is inserted into the insertion recess 26, the relative rotation of the vane rotor 30 with respect to the housing 20 is restricted, and when the lock pin 73 is not inserted into the insertion recess 26, relative rotation of the vane rotor 30 with respect to the housing 20 is allowed. Is done.

The spool 50 has a seal member 59 instead of the spool lid portion 52. The seal member 59 is provided inside the spool cylinder portion 51. A pressure accumulation space 500 extending in the axial direction of the spool 50 is formed between the inner wall of the seal member 59 and the inner wall of the spool cylinder portion 51.

The supply oil passage 54, the first control oil passage 55, the recycle oil passage 57, and the second control oil passage 56 are spaced in this order from one end side of the spool 50 toward the other end side. It is formed so as to be lined up. The supply oil passage 54, the first control oil passage 55, the recycle oil passage 57, and the second control oil passage 56 communicate the pressure accumulation space 500 and the outside of the spool 50. Here, the flow passage area of the supply oil passage 54 is set to be the same as the flow passage area of the recycle oil passage 57.

In this embodiment, when the spool 50 is in a position where it abuts against the locking portion 71 (see FIG. 8), the supply port 43 and the supply oil passage 54 are not connected. When the spool 50 moves to the camshaft 3 side by a predetermined amount, the supply port 43 and the supply oil passage 54 are connected, the first control oil passage 55 and the first control port 44 are connected, and the second control port 45 is recycled. The oil passage 57 is connected. At this time, the first control oil passage 55 and the pin control port 410 are connected.

When the spool 50 is in a position where it abuts against the sleeve bottom 412, the supply port 43 and the supply oil passage 54 are connected, the second control oil passage 56 and the second control port 45 are connected, and the first control port 44 Recycle oil passage 57 is connected. At this time, the first control oil passage 55 and the pin control port 410 are connected.
The check valve 60 includes a supply check valve 68 and a recycle check valve 69.

The supply check valve 68 and the recycle check valve 69 are formed separately. The supply check valve 68 and the recycle check valve 69 are formed, for example, by bending a thin metal plate. Here, the plate thickness of the thin plate forming the supply check valve 68 is set smaller than the plate thickness of the thin plate forming the recycle check valve 69.

The supply check valve 68 and the recycle check valve 69 are formed to be elastically deformable. Since the thickness of the supply check valve 68 is smaller than that of the recycle check valve 69, the supply check valve 68 is more easily deformed than the recycle check valve 69. That is, when the same force is applied to the supply check valve 68 and the recycle check valve 69, the supply check valve 68 has a larger deformation amount than the recycle check valve 69.

The supply check valve 68 is provided at a position corresponding to the supply oil passage 54 of the pressure accumulating space 500. The supply check valve 68 is supported by a supply side support portion 591 formed on the inner wall of the seal member 59. Here, the supply side support portion 591 is formed in a shape corresponding to the shape of the supply check valve 68 (see FIGS. 8 and 9). The supply check valve 68 can be elastically deformed in the radial direction of the spool 50.

The recycle check valve 69 is provided at a position corresponding to the recycle oil passage 57 of the pressure accumulating space 500. The recycle check valve 69 is supported by a recycle side support portion 592 formed on the inner wall of the seal member 59. Here, the recycle side support portion 592 is formed in a shape corresponding to the shape of the recycle check valve 69 (see FIGS. 8 and 9). The recycle check valve 69 can be elastically deformed in the radial direction of the spool 50.

When the hydraulic oil travels from the oil pump 8 side to the pressure accumulating space 500 side via the supply oil passage 54, the supply check valve 68 is deformed and opened inward in the radial direction of the spool 50 to check the supply of the inner wall of the spool 50 and the supply check valve. A gap is formed between the valve 68. As a result, the hydraulic oil can flow into the pressure accumulation space 500 via the supply oil passage 54. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side to the oil pump 8 side via the supply oil passage 54, the supply check valve 68 is deformed outwardly in the radial direction of the spool 50 and is closed. It sticks to the inner wall of the spool 50 so as to close it. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulation space 500 via the supply oil passage 54. In this way, the supply check valve 68 allows the flow of hydraulic oil from the oil pump 8 side via the supply oil passage 54 to the pressure accumulation space 500 side, and from the pressure accumulation space 500 side via the supply oil passage 54. The flow of hydraulic oil toward the oil pump 8 is restricted.

When the hydraulic oil travels from the retarded angle chamber 201 or the advanced angle chamber 202 toward the pressure accumulating space 500 via the recycle oil passage 57, the recycle check valve 69 is deformed inward in the radial direction of the spool 50 and opened. A gap is formed between the 50 inner walls and the recycle check valve 69. As a result, the hydraulic oil can flow into the pressure accumulating space 500 via the recycle oil passage 57. On the other hand, when the hydraulic oil travels from the pressure accumulation space 500 side to the retard chamber 201 or the advance chamber 202 side via the recycle oil passage 57, the recycle check valve 69 is deformed outward in the radial direction of the spool 50 and closed. Then, the recycle oil passage 57 is stuck to the inner wall of the spool 50. As a result, the hydraulic oil is restricted from flowing out of the spool 50 from the pressure accumulation space 500 via the recycle oil passage 57. In this way, the recycle check valve 69 allows the flow of hydraulic oil from the retard chamber 201 or the advance chamber 202 to the accumulator space 500 via the recycle oil passage 57, and the recycle oil from the accumulator space 500 side. The flow of hydraulic oil toward the retard chamber 201 or the advance chamber 202 via the path 57 is restricted.

In the present embodiment, when the spool 50 moves to the camshaft 3 side by a predetermined amount from the position where the spool 50 abuts on the locking portion 71 (see FIG. 8), the hydraulic oil passes through the supply port 43, the supply oil passage 54, and the supply check valve 68. Via the first control oil passage 55, hydraulic oil flows into the pin control port 410 and the pin control oil passage 305, and relative rotation of the vane rotor 30 with respect to the housing 20 is allowed. . At this time, the hydraulic oil in the pressure accumulating space 500 is supplied to the retard chamber 201 via the first control oil passage 55 and the first control port 44, and the hydraulic oil in the advance chamber 202 passes through the second control port 45. Via, it flows into the concave portion on the radially outer side of the recycled oil passage 57. The hydraulic fluid that has flowed into the recess is returned to the pressure accumulating space 500 via the recycle oil passage 57 and the recycle check valve 69.

Further, when the spool 50 is in a position where it abuts against the sleeve bottom 452, the hydraulic oil flows into the pin control port 410 and the pin control oil passage 305 via the first control oil passage 55, and the vane rotor 30 with respect to the housing 20 flows. Relative rotation is allowed. At this time, the hydraulic oil is supplied to the advance chamber 202 via the second control oil passage 56 and the second control port 45, and the hydraulic oil in the retard chamber 201 passes through the first control port 44. The recycle oil passage 57 flows into the concave portion on the radially outer side. The hydraulic fluid that has flowed into the recess is returned to the pressure accumulating space 500 via the recycle oil passage 57 and the recycle check valve 69.

As described above, the supply check valve 68 is more easily deformed than the recycle check valve 69. The flow passage area of the supply oil passage 54 is set to be the same as the flow passage area of the recycle oil passage 57. Therefore, the valve opening pressure of the supply check valve 68 is set lower than the valve opening pressure of the recycle check valve 69. That is, it can be said that the characteristics related to the opening of the supply check valve 68 are set to characteristics that make it easier to open than the recycle check valve 69.
The configuration of the fourth embodiment is the same as that of the first embodiment except for the points described above. Therefore, about the structure similar to 1st Embodiment, there can exist an effect similar to 1st Embodiment.

As described above, in this embodiment, the spool 50 includes the supply side support portion 591 that supports the supply check valve 68 and the recycle side support portion 592 that supports the recycle check valve 69. Therefore, for example, by forming the supply side support portion 591 corresponding to the shape of the supply check valve 68 and forming the recycle side support portion 592 corresponding to the shape of the recycle check valve 69, By making the shape different from the recycle side support portion 592, it is possible to suppress erroneous assembly of the supply check valve 68 and the recycle check valve 69.

In the present embodiment, the supply check valve 68 and the recycle check valve 69 are formed of elastically deformable plate materials, each having a different plate thickness. As a result, the characteristics relating to the opening of the supply check valve 68 and the characteristics relating to the opening of the recycle check valve 69 are made different.

(Fifth embodiment)
FIG. 10 shows a part of the valve timing adjusting device according to the fifth embodiment of the present disclosure. The fifth embodiment differs from the third embodiment in the configuration of the sleeve 40, the spool 50, the check valve 60, and the like.
The supply port 43 is formed so as to connect the outer wall and the inner wall of the sleeve tube portion 451. The supply port 43 is connected to the oil pump 8.
The first control port 44 is formed so as to connect the outer wall and the inner wall of the sleeve tube portion 451 on the locking portion 47 side with respect to the supply port 43.
The second control port 45 is formed to connect the outer wall and the inner wall of the sleeve tube portion 451 on the locking portion 47 side with respect to the first control port 44.
In the present embodiment, the sleeve 40 further includes recycle ports 481 and 482 and drain ports 46 and 49.

The recycle port 481 is formed between the first control port 44 and the second control port 45 so as to connect the outer wall and the inner wall of the sleeve cylindrical portion 451. The recycle port 481 communicates with the retardation chamber 201. The inner diameter of the recycle port 481 is set smaller than the inner diameter of the supply port 43. The total flow area of the recycle port 481 is set smaller than the total flow area of the supply port 43.

The recycle port 482 is formed between the recycle port 481 and the second control port 45 so as to connect the outer wall and the inner wall of the sleeve cylindrical portion 451. The recycle port 481 communicates with the advance chamber 202. The inner diameter of the recycle port 482 is set smaller than the inner diameter of the supply port 43. The total flow area of the recycle port 482 is set smaller than the total flow area of the supply port 43. The inner diameter of the recycle port 482 is set to be the same as the inner diameter of the recycle port 481. Further, the total flow area of the recycle port 482 is set to be the same as the total flow area of the recycle port 481.

The drain port 46 is formed between the supply port 43 and the first control port 44 so as to connect the outer wall and the inner wall of the sleeve cylindrical portion 451. The drain port 46 communicates with the outside of the valve timing adjusting device 10.

The drain port 49 is formed in a substantially cylindrical shape between the drain cylinder 49 and the spool 50 on the inner side of the end of the sleeve cylinder part 451 on the locking part 47 side. The drain port 49 communicates with the oil path switching valve 11 on the side opposite to the camshaft 3, that is, on the outside of the valve timing adjusting device 10.
In the present embodiment, the first control oil passage 55 and the recycle oil passage 571 are formed integrally with the supply oil passage 54 on the spool bottom 53 side.
The second control oil passage 56 and the recycle oil passage 572 are integrally formed on the spool bottom 53 side with respect to the first control oil passage 55 and the recycle oil passage 571.
The check valve 60 includes a supply check valve 61 and recycle check valves 621 and 622.

The supply check valve 61 and the recycle check valves 621 and 622 are formed separately. As in the third embodiment, the supply check valve 61 and the recycle check valves 621 and 622 are formed by, for example, winding a thin metal plate into a cylindrical shape. Here, the width and thickness of the thin plate forming the supply check valve 61 are set to be the same as the width and thickness of the thin plate forming the recycle check valves 621 and 622. Therefore, the ease of deformation of the supply check valve 61 is about the same as that of the recycle check valves 621 and 622. In other words, when the same radial force is applied to the supply check valve 61 and the recycle check valves 621 and 622, the deformation amount of the supply check valve 61 is approximately the same as the deformation amount of the recycle check valves 621 and 622. .

The supply check valve 61 is provided at a position corresponding to the supply port 43 between the sleeve 40 and the spool 50. The recycle check valve 621 is provided at a position corresponding to the recycle port 481 between the sleeve 40 and the spool 50. The recycle check valve 622 is provided at a position corresponding to the recycle port 482 between the sleeve 40 and the spool 50.

When the hydraulic oil travels from the oil pump 8 side to the pressure accumulating space 500 side via the supply oil passage 54, the supply check valve 61 is deformed radially inward and opened, and the inner wall of the sleeve 40, the supply check valve 61, A gap is formed between the two. As a result, the hydraulic oil can flow into the pressure accumulation space 500 via the supply port 43 and the supply oil passage 54. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side to the oil pump 8 side via the supply port 43, the supply check valve 61 is deformed radially outward and closed to close the supply port 43. Stick to 40 inner walls. As a result, the hydraulic oil is restricted from flowing out of the sleeve 40 from the pressure accumulation space 500 via the supply oil passage 54 and the supply port 43. In this way, the supply check valve 61 allows the flow of hydraulic oil from the oil pump 8 side via the supply oil passage 54 toward the pressure accumulation space 500 side, and allows oil to flow from the pressure accumulation space 500 side via the supply port 43. The flow of hydraulic oil toward the pump 8 side is restricted.

When the hydraulic oil travels from the retarding chamber 201 side to the pressure accumulating space 500 side via the recycle port 481 and the recycle oil passage 571, the recycle check valve 621 is deformed radially inward and opened, and the inner wall of the sleeve 40 A gap is formed with the recycle check valve 621. As a result, the hydraulic oil can flow into the pressure accumulating space 500 via the recycle oil passage 571. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side to the retarded chamber 201 side via the recycle oil passage 571 and the recycle port 481, the recycle check valve 621 is deformed radially outward and closed, and the recycle port 481 is closed. Is attached to the inner wall of the sleeve 40. Thus, the hydraulic oil is restricted from flowing out of the sleeve 40 from the pressure accumulation space 500 via the recycle oil passage 571. Thus, the recycle check valve 621 allows the flow of hydraulic oil from the retarding chamber 201 side to the accumulator space 500 side via the recycle port 481 and the recycle oil passage 571, and the recycle oil passage from the accumulator space 500 side. 571, restricts the flow of hydraulic oil toward the retarded angle chamber 201 via the recycle port 481.

When the hydraulic oil travels from the advance chamber 202 side to the pressure accumulation space 500 side via the recycle port 482 and the recycle oil passage 572, the recycle check valve 622 is deformed radially inward and opened, A gap is formed with the recycle check valve 622. As a result, the hydraulic oil can flow into the pressure accumulating space 500 via the recycle oil passage 572. On the other hand, when the hydraulic oil travels from the pressure accumulating space 500 side to the advance chamber 202 side via the recycle oil passage 572 and the recycle port 482, the recycle check valve 622 is deformed radially outward and closed, and the recycle port 482 is closed. Is attached to the inner wall of the sleeve 40. Accordingly, the hydraulic oil is restricted from flowing out of the sleeve 40 from the pressure accumulation space 500 via the recycle oil passage 572. As described above, the recycle check valve 622 allows the flow of hydraulic oil from the advance chamber 202 side to the pressure accumulation space 500 side via the recycle port 482 and the recycle oil path 572, and the recycle oil path from the pressure accumulation space 500 side. 572, restricts the flow of hydraulic oil toward the advance chamber 202 via the recycle port 482.

In the present embodiment, when the spool 50 is in a position where it abuts against the locking portion 71 (see FIG. 10), hydraulic oil is supplied to the advance chamber 202 via the second control port 45, and The hydraulic oil is returned to the pressure accumulating space 500 via the recycle port 481 and the recycle check valve 621, and is discharged to the outside of the valve timing adjusting device 10 via the first control port 44 and the drain port 46.

When the spool 50 is in a position where it abuts against the sleeve bottom 452, the hydraulic oil is supplied to the retard chamber 201 via the first control port 44, and the hydraulic oil in the advance chamber 202 is recycled to the recycle port 482. The pressure is returned to the pressure accumulating space 500 via the check valve 622 and discharged to the outside of the valve timing adjusting device 10 via the second control port 45 and the drain port 49.

As described above, the ease of deformation of the supply check valve 61 is comparable to that of the recycle check valves 621 and 622. Further, the total flow area of the supply port 43 is set larger than the total flow area of the recycle ports 481 and 482. Therefore, the valve opening pressure of the supply check valve 61 is set lower than the valve opening pressures of the recycle check valves 621 and 622. That is, it can be said that the characteristics related to the opening of the supply check valve 61 are set to characteristics that are easier to open than the recycle check valves 621 and 622.
The configuration of the fifth embodiment is the same as that of the third embodiment except for the points described above. Therefore, about the structure similar to 3rd Embodiment, there can exist an effect similar to 3rd Embodiment.

In the present embodiment, the supply check valve 61 and the recycle check valves 621 and 622 are formed with the same specifications (width and plate thickness). Accordingly, the supply check valve 61, the recycle check valve 621, and the recycle check valve 622 can be arranged at predetermined positions without being distinguished from each other. Therefore, it is easy to manufacture without worrying about misassembly.
As described above, in the present embodiment, the sleeve 40 further includes the recycle ports 481 and 482 formed so that the pressure accumulating space 500 and the retard chamber 201 or the advance chamber 202 can be connected.
The supply check valve 61 is provided outside the spool 50 and closes the supply port 43 when the valve is closed.
The recycle check valves 621 and 622 are provided outside the spool 50 and close the recycle ports 481 and 482 when the valves are closed.
In the present embodiment, the supply check valve 61 and the recycle check valves 621 and 622 are both provided between the spool 50 and the sleeve 40. Therefore, the physique in the radial direction of the oil passage switching valve 11 can be reduced.

(Sixth embodiment)
An oil passage switching valve of a valve timing adjusting device according to a sixth embodiment of the present disclosure is shown in FIG. The sixth embodiment is different from the first embodiment in the configuration of the sleeve 40, the spool 50, the check valve, and the like.

In the present embodiment, the valve timing adjusting device 10 includes a retard supply oil path RRs, an advance supply oil path RAs, a retard drain oil path RRd, an advance drain oil path RAd, and a retard supply check valve 81 as a check valve. And an advance supply check valve 82 and the like.

In the present embodiment, the locking portion 71 is formed in a bottomed cylindrical shape, and the outer peripheral wall is provided so as to be fitted to the inner peripheral wall of the sleeve cylindrical portion 421 of the outer sleeve 42. A hole is formed in the center of the bottom of the locking part 71, and the spool bottom 53 is located inside the hole.

The locking part 71 can lock one end of the spool 50 by the bottom part. The locking portion 71 can restrict the movement of the spool 50 to the side opposite to the sleeve bottom portion 412 of the spool 50. As a result, the spool 50 is prevented from falling off from the inner side of the inner sleeve 41.

The spool 50 is movable in the axial direction from a position where it comes into contact with the locking portion 71 to a position where it comes into contact with the sleeve bottom 412. That is, the movable range relative to the sleeve 40 is from the position (see FIG. 11) that contacts the locking portion 71 to the position that contacts the sleeve bottom 412. Hereinafter, the movable range of the spool 50 is referred to as a “stroke section”.

As shown in FIG. 11, the end of the inner sleeve 41 on the sleeve bottom 412 side has an outer diameter smaller than the inner diameter of the outer sleeve 42. Thereby, a cylindrical space St <b> 1 that is a substantially cylindrical space is formed between the outer peripheral wall of the end portion of the inner sleeve 41 on the sleeve bottom 412 side and the inner peripheral wall of the outer sleeve 42.

Further, the inner sleeve 41 is formed with an annular recess Ht. The annular recess Ht is formed so as to be recessed annularly radially inward from a position corresponding to the engaging portion 47 of the outer peripheral wall of the inner sleeve 41. Thus, an annular space St2 that is an annular space is formed between the annular recess Ht and the inner peripheral wall of the outer sleeve 42.

Further, the inner sleeve 41 is formed with a flow channel groove 510. The channel groove 510 is formed so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 41 and to extend in the axial direction of the inner sleeve 41. The channel groove 510 forms an axial supply oil path RsA. That is, the axial supply oil passage RsA is formed so as to extend in the axial direction of the sleeve 40 at the interface T1 between the outer sleeve 42 and the inner sleeve 41. One end of the axial supply oil passage RsA is connected to the cylindrical space St1, and the other end is connected to the annular space St2.

Further, the inner sleeve 41 is formed with restriction groove portions 511 and 512. The restriction groove portion 511 is formed so as to be annularly recessed radially outward from a position corresponding to the end portion of the cylindrical space St1 of the inner peripheral wall of the inner sleeve 41. The restriction groove portion 512 is formed so as to be annularly recessed outward in the radial direction from a position corresponding to the annular recessed portion Ht of the inner peripheral wall of the inner sleeve 41.

The sleeve 40 has a retard supply opening ORs, an advance supply opening OAs, a retard opening OR, and an advance opening OA. The retard supply opening ORs as the “inflow hole” extends in the radial direction of the sleeve 40 and connects the regulation groove 511 of the inner sleeve 41 as the “tubular member” with the cylindrical space St1 and the axial supply oil passage RsA. It is formed to do. A plurality of retard angle supply openings ORs are formed in the circumferential direction of the inner sleeve 41.

The advance angle supply opening OAs as the “inflow hole” extends in the radial direction of the sleeve 40 and is formed so as to connect the restriction groove portion 512 of the inner sleeve 41 with the annular space St2 and the axial supply oil passage RsA. A plurality of advance angle supply openings OAs are formed in the circumferential direction of the inner sleeve 41.

The retarded angle opening OR extends in the radial direction of the sleeve 40 and is formed to connect the space inside the inner sleeve 41 and the space outside the outer sleeve 42. A plurality of the retarded angle openings OR are formed in the circumferential direction of the sleeve 40. The retarded angle opening OR communicates with the retarded angle chamber 201 via the retarded oil passage 301.

The advance opening OA extends in the radial direction of the sleeve 40 and is formed so as to connect the space inside the inner sleeve 41 and the space outside the outer sleeve 42. The advance opening OA is formed on the locking portion 47 side with respect to the retard opening OR. A plurality of advance opening portions OA are formed in the circumferential direction of the sleeve 40. The advance opening OA communicates with the advance chamber 202 via the advance oil passage 302.

The spool 50 has a retard supply recess HRs, a retard drain recess HRd, an advance drain recess HAd, an advance supply recess HAs, and drain openings Od1, Od2. The retard supply recess HRs, the retard drain recess HRd, the advance drain recess HAd, and the advance supply recess HAs are each formed in an annular shape so as to be recessed radially inward from the outer peripheral wall of the spool 50. The retard supply recess HRs, the retard drain recess HRd, the advance drain recess HAd, and the advance supply recess HAs are formed to be aligned in the axial direction of the spool 50 in this order. The retard drain concavity HRd and the advance drain concavity HAd are integrally formed. The retard drain concavity HRd and the advance drain concavity HAd form a specific space Ss between the inner peripheral wall of the inner sleeve 41. That is, the spool 50 forms a specific space Ss between the sleeve 50 and the spool 50.

The drain opening Od1 is formed so as to communicate the space inside the spool 50 with the retard drain concavity HRd and the advance drain concavity HAd, that is, the specific space Ss. The drain opening Od2 is formed to communicate the inner space and the outer space at the end of the spool 50 on the spool bottom 53 side. A plurality of drain openings Od1 and Od2 are formed in the circumferential direction of the spool 50, respectively.

The retard supply oil path RRs connects the oil pump 8 and the retard chamber 201 via the oil path switching valve 11. The advance angle supply oil path RAs connects the oil pump 8 and the advance angle chamber 202 via the oil path switching valve 11. A retarded drain oil path RRd as a drain oil path connects the retarded chamber 201 and the oil pan 7. An advance drain oil passage RAd as a drain oil passage connects the advance chamber 202 and the oil pan 7.

The retard supply oil path RRs includes a supply hole 101, a shaft hole 100, a cylindrical space St1, an axial supply oil path RsA, a retard supply opening ORs, a regulation groove 511, a retard supply recess HRs, and a retard opening. The oil pump 8 and the retard chamber 201 are connected via the part OR and the retard oil passage 301. The advance angle supply oil path RAs includes a supply hole 101, a shaft hole 100, a cylindrical space St1, an axial supply oil path RsA, an advance angle supply opening OAs, a restriction groove 512, an advance angle supply recess HAs, and an advance angle opening. The oil pump 8 and the advance chamber 202 are connected via the part OA and the advance oil passage 302.

The retarded drain oil passage RRd connects the retarded chamber 201 and the oil pan 7 via the retarded oil passage 301, the retarded opening OR, the retarded drain recess HRd, and the drain openings Od1 and Od2. Yes. The advance drain oil passage RAd connects the advance chamber 202 and the oil pan 7 via the advance oil passage 302, the advance opening OA, the advance drain recess HAd, and the drain openings Od1, Od2. Yes. In this way, the retard angle supply oil path RRs, the advance angle supply oil path RAs, the retard angle drain oil path RRd, and the advance angle drain oil path RAd are partially formed inside the oil path switching valve 11.

When the spool 50 is in contact with the locking portion 71 (see FIG. 11), that is, when the spool 50 is positioned at one end of the stroke section, the spool 50 opens the retard opening OR, The oil pump 8 includes a supply hole portion 101, a shaft hole portion 100, a cylindrical space St1, an axial supply oil passage RsA, a retardation supply opening portion ORs, a regulation groove portion 511, and a retardation supply recess portion HRs of the retardation supply oil passage RRs. The retard chamber 201 communicates with the retard chamber 201 via the retard opening OR and the retard oil passage 301. As a result, the hydraulic oil can be supplied from the oil pump 8 to the retard chamber 201 via the retard supply oil passage RRs. At this time, the advance chamber 202 enters the oil pan 7 via the advance oil passage 302 of the advance drain oil passage RAd, the advance opening OA, the advance drain recess HAd, and the drain openings Od1 and Od2. Communicate. As a result, the hydraulic oil can be discharged from the advance chamber 202 to the oil pan 7 via the advance drain oil path RAd.

When the spool 50 is positioned between the locking portion 71 and the sleeve bottom portion 412, that is, when the spool 50 is positioned in the middle of the stroke section, the oil pump 8 is supplied with the supply hole portion of the advance supply oil passage RAs. 101, the shaft hole 100, the cylindrical space St1, the axial supply oil passage RsA, the advance supply opening OAs, the regulation groove 512, the advance supply recess HAs, the advance opening OA, and the advance oil passage 302. To communicate with the advance chamber 202. At this time, the oil pump 8 and the retard chamber 201 are in communication with each other through the retard supply oil passage RRs. Accordingly, the hydraulic oil can be supplied from the oil pump 8 to the retard chamber 201 and the advance chamber 202 via the retard supply oil passage RRs and the advance supply oil passage RAs. However, since the retard drain oil passage RRd and the advance drain oil passage RAd are closed by the spool 50, that is, blocked, the hydraulic oil is discharged from the retard chamber 201 and the advance chamber 202 to the oil pan 7. Not.

When the spool 50 is in contact with the sleeve bottom 412, that is, when the spool 50 is located at the other end of the stroke section, the retard chamber 201 is connected to the retard oil passage 301 of the retard drain oil passage RRd. The oil pan 7 communicates with the corner opening OR, the retard drain concavity HRd, and the drain openings Od1 and Od2. At this time, the oil pump 8 and the advance chamber 202 are in communication with each other through the advance supply oil passage RAs. As a result, the hydraulic oil can be discharged from the retard chamber 201 to the oil pan 7 via the retard drain oil passage RRd, and the advance chamber 202 from the oil pump 8 via the advance feed oil passage RAs. Can be supplied with hydraulic oil.

A filter 75 is provided inside the end of the outer sleeve 42 on the sleeve bottom 412 side, that is, in the middle of the retard supply oil passage RRs and the advance supply oil passage RAs. The filter 75 is a disk-shaped mesh, for example. The filter 75 can collect foreign substances contained in the hydraulic oil. Therefore, it is possible to suppress the foreign matter from flowing to the downstream side of the filter 75, that is, the side opposite to the oil pump 8.

In this embodiment, a retard supply check valve 81 and an advance supply check valve 82 are provided as “check valves”. Each of the retard supply check valve 81 and the advance supply check valve 82 is formed in a cylindrical shape by winding a single rectangular plate made of, for example, metal so that the longitudinal direction thereof is along the circumferential direction. The retard supply check valve 81 and the advance supply check valve 82 as “check valves” are inner ends that are one end in the circumferential direction when provided inside the inner sleeve 41 as a “tubular member”. The end is located inside the outer end which is the other end in the circumferential direction. Here, at the outer end portions of the retard supply check valve 81 and the advance supply check valve 82, an overlapping portion 830 that is a portion overlapping the inner end portion in the circumferential direction is formed. The configuration related to the shapes and the like of the retard supply check valve 81 and the advance supply check valve 82 will be described in detail later.

The retard supply check valve 81 is provided in the regulation groove 511. The retard supply check valve 81 is provided in the regulating groove 511 so as to be elastically deformable in the radial direction. The retard supply check valve 81 is provided on the radially inner side of the inner sleeve 41 with respect to the retard supply opening ORs. The retard supply check valve 81 is provided in the restriction groove 511, and in a state where hydraulic fluid as “fluid” does not flow in the retard supply oil path RRs, that is, in a state where no external force is applied, the overlapping portion 830 is provided. It is the state which overlapped with the inner end part.

When the hydraulic oil flows from the retard supply opening ORs side to the retard supply recess HRs side in the retard supply oil path RRs, the retard supply check valve 81 is pushed by the hydraulic oil so that the outer peripheral wall is contracted radially inward. That is, the inner diameter is deformed to be reduced. Accordingly, the outer peripheral wall of the retard supply check valve 81 is separated from the retard supply opening ORs, and the hydraulic oil can flow to the retard supply recess HRs side via the retard supply check valve 81. At this time, the overlapping portion 830 is in a state in which a part of the overlapping portion 830 is maintained while the length of the overlapping range between the overlapping portion 830 and the inner end portion of the retard supply check valve 81 is enlarged.

When the flow rate of the hydraulic oil flowing through the retarded supply oil passage RRs becomes a predetermined value or less, the retarded supply check valve 81 is deformed so as to expand radially outward, that is, the inner diameter is expanded. Further, when the hydraulic oil flows from the retard supply recess HRs side to the retard supply opening ORs side, the inner peripheral wall of the retard supply check valve 81 is pushed radially outward by the hydraulic oil, and enters the retard supply opening ORs. Abut. Thereby, the flow of the hydraulic oil from the retard supply recess HRs side to the retard supply opening ORs side is restricted.

In this way, the retard supply check valve 81 functions as a check valve, allows the hydraulic oil to flow from the retard supply opening ORs side to the retard supply recess HRs side, and from the retard supply recess HRs side. The flow of hydraulic oil to the retard supply opening ORs side can be regulated. That is, the retard supply check valve 81 is provided inside the cylindrical inner sleeve 41 having the retard supply opening ORs that communicates the outer peripheral wall and the inner peripheral wall, and the inner via the retard supply opening ORs. The flow of hydraulic oil toward the inner side of the sleeve 41 is allowed, and the flow of hydraulic oil from the inner side of the inner sleeve 41 toward the retard supply opening ORs can be regulated. The retard supply check valve 81 is provided on the oil pump 8 side with respect to the spool 50 of the oil path switching valve 11 in the retard supply oil path RRs, and only the flow of hydraulic oil from the oil pump 8 side to the retard chamber 201 side is provided. Allow.

The advance angle supply check valve 82 is provided in the restriction groove portion 512. The advance angle supply check valve 82 is provided in the regulating groove portion 512 so as to be elastically deformable in the radial direction. The advance angle supply check valve 82 is provided on the radially inner side of the inner sleeve 41 with respect to the advance angle supply opening OAs. The advance angle supply check valve 82 is provided in the restriction groove portion 512, and the overlapping portion 830 overlaps the inner end portion in a state where hydraulic oil does not flow in the advance angle supply oil passage RAs, that is, in a state where no external force is acting. (See FIG. 12).

When hydraulic fluid flows from the advanced angle supply opening OAs side to the advanced angle supply recess HAs side in the advanced angle supply oil path RAs, the advanced angle supply check valve 82 is pushed by the hydraulic oil so that the outer peripheral wall is contracted radially inward. That is, the inner diameter is deformed to be reduced. Thereby, the outer peripheral wall of the advance angle supply check valve 82 is separated from the advance angle supply opening OAs, and the hydraulic fluid can flow to the advance angle supply recess HAs side via the advance angle supply check valve 82. At this time, the overlapping portion 830 is in a state where a part of the overlapping portion 830 is maintained while the overlapping range between the overlapping portion 830 and the inner end portion of the advance angle supply check valve 82 is enlarged.

When the flow rate of the hydraulic oil flowing through the advance angle supply oil passage RAs becomes a predetermined value or less, the advance angle supply check valve 82 is deformed so as to expand radially outward, that is, the inner diameter increases. Further, when the hydraulic oil flows from the advance angle supply recess HAs side to the advance angle supply opening OAs side, the inner peripheral wall of the advance angle supply check valve 82 is pushed radially outward by the hydraulic oil, and enters the advance angle supply opening OAs. Abut. As a result, the flow of hydraulic oil from the advance angle supply recess HAs side to the advance angle supply opening OAs side is restricted.

In this way, the advance angle supply check valve 82 functions as a check valve, allows the hydraulic oil to flow from the advance angle supply opening OAs side to the advance angle supply recess HAs side, and from the advance angle supply recess HAs side. The flow of hydraulic oil to the advance angle supply opening OAs side can be regulated. That is, the advance angle supply check valve 82 is provided inside the cylindrical inner sleeve 41 having the advance angle supply opening OAs that communicates the outer peripheral wall and the inner peripheral wall, and the inner angle via the advance angle supply opening OAs. The flow of hydraulic oil toward the inside of the sleeve 41 is allowed, and the flow of hydraulic oil toward the advance angle supply opening OAs from the inner side of the inner sleeve 41 can be regulated. The advance angle supply check valve 82 is provided on the oil pump 8 side with respect to the spool 50 of the oil path switching valve 11 in the advance angle oil supply path RAs, and only the flow of hydraulic oil from the oil pump 8 side to the advance chamber 202 side is provided. Allow.

The restriction grooves 511 and 512 can restrict the movement of the retard supply check valve 81 and the advance supply check valve 82 in the axial direction, respectively. As shown in FIG. 12, five advance angle supply openings OAs are formed in the inner sleeve 41. The advance angle supply opening OAs is formed in approximately half of the entire circumferential range of the inner sleeve 41. That is, the advance angle supply opening OAs is formed so as to be biased to a specific portion in the circumferential direction of the inner sleeve 41. Therefore, when the hydraulic oil flows from the advance angle supply opening OAs side to the advance angle supply recess HAs side, the advance angle supply check valve 82 is moved to the opposite side of the advance groove supply opening OAs of the restriction groove 512 by the hydraulic oil. Pressed. Thereby, it is possible to suppress the advance angle supply check valve 82 from dropping from the restriction groove portion 512. Therefore, the restriction groove portion 512 can maintain the function of restricting the movement of the advance angle supply check valve 82 in the axial direction.

The retard angle supply openings ORs are also formed in the inner sleeve 41 in the same manner as the advance angle supply openings OAs. The retard supply opening ORs is formed in approximately half of the entire circumferential range of the inner sleeve 41. That is, the retard supply opening ORs is formed at a specific portion in the circumferential direction of the inner sleeve 41. Therefore, when the hydraulic oil flows from the retard supply opening ORs side to the retard supply recess HRs side, the retard supply check valve 81 is moved to the opposite side of the regulation groove portion 511 from the retard supply opening ORs by the hydraulic oil. Pressed. Thereby, it is possible to suppress the retard supply check valve 81 from dropping from the restriction groove 511. Therefore, the regulation groove 511 can maintain the function of regulating the movement of the retard supply check valve 81 in the axial direction.

The linear solenoid 9 is provided so as to contact the spool bottom 53. The linear solenoid 9 is energized to press the spool 50 against the urging force of the spring 72 via the spool bottom 53 against the camshaft 3 side. As a result, the axial position of the spool 50 with respect to the sleeve 40 changes in the stroke section.

Next, the configuration related to the shape and the like of the retard supply check valve 81 and the advance supply check valve 82 will be described in detail. Since the configuration of the retard supply check valve 81 is the same as that of the advance supply check valve 82, only the configuration of the advance supply check valve 82 will be described, and the description of the configuration of the retard supply check valve 81 will be omitted. To do.

As shown in FIGS. 13 and 14, the advance angle supply check valve 82 includes a valve body 850. 13 and 14 show the advance angle supply check valve 82 in a state where it is not provided inside the inner sleeve 41, that is, in a free state where no external force is acting. The valve body 850 is formed in a cylindrical shape by winding a single rectangular plate made of, for example, metal so that the longitudinal direction is along the circumferential direction. When the advance angle supply check valve 82 is in a free state, the valve body 850 has a portion on the inner end 851 side which is one end portion in the circumferential direction on the outer end portion 852 side which is the other end portion in the circumferential direction. It forms so that it may be located inside a site | part (refer FIG. 14).

The valve body 850 has a constant curvature portion 861 and a small curvature portion 871. The constant curvature portion 861 is a specific portion of the valve body 850 in the circumferential direction, and one end thereof coincides with the outer end portion 852 and the other end is located between the outer end portion 852 and the inner end portion 851. . The small curvature portion 871 is a specific portion in the circumferential direction of the valve body 850, and one end thereof coincides with the other end of the constant curvature portion 861 and the other end coincides with the inner end portion 851.

The constant curvature portion 861 has a constant curvature over the entire range from one end to the other when the advance angle supply check valve 82 is in a free state. Further, the small curvature portion 871 has a constant curvature in the entire range from one end to the other end when the advance angle supply check valve 82 is in a free state. Here, the radius r1 of the small curvature portion 871 is smaller than the radius r2 of the constant curvature portion 861 (see FIG. 14). That is, the valve main body 850 has a curvature at a portion other than the constant curvature portion 861 having a constant curvature at a specific portion in the circumferential direction and a portion other than the constant curvature portion 861 at the circumferential direction when the advance supply check valve 82 is in a free state. A small curvature portion 871 smaller than the curvature of the constant curvature portion 861 is provided.

The angle θ1 from one end to the other end of the constant curvature portion 861 is, for example, about 330 °. Further, the angle θ2 from one end to the other end of the small curvature portion 871 is, for example, about 75 °. When the advance angle supply check valve 82 is in a free state, the outer end portion 852 of the valve main body 850 is located on the radially outer side of a substantially intermediate position between one end and the other end of the small curvature portion 871. At this time, a gap S1 is formed between the inner peripheral wall of the outer end 852 of the valve body 850 and the outer peripheral wall of the small curvature portion 871 (see FIG. 14). Thus, in this embodiment, when the advance angle supply check valve 82 is in the free state, the valve main body 850 is arranged such that the portion on the inner end portion 851 side is located inside the portion on the outer end portion 852 side, that is, Both ends are formed to overlap in the circumferential direction.

FIG. 15 shows the advance angle supply check valve 82 when it is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41. At this time, the constant curvature portion 861 is deformed so that the radius r3 is smaller than r1 and r2. In this embodiment, the radius of the small curvature portion 871 when the advance angle supply check valve 82 is in the free state is r1, the radius of the constant curvature portion 861 when the advance angle supply check valve 82 is in the free state is r2, and the advance angle supply. When the check valve 82 is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41, the radius of the constant curvature portion 861 is r3, and the curvature reduction coefficient R is (r2-r1) / (r2 -R3), the valve body 850 is formed to satisfy the relationship of R = 0.58.

As shown in FIG. 15, when the advance angle supply check valve 82 is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41, the maximum stress among the stresses generated in the valve body 850. The maximum stress generation point P1 that is the generation point of is the position of about 180 ° from the inner end portion 851.

Next, by comparing the advance angle supply check valve 82 according to the present embodiment with the first comparative embodiment and the second comparative embodiment, the advantages of the present embodiment over the first comparative embodiment and the second comparative embodiment are clarified. To do.

16 is different from the advance supply check valve 82 according to the present embodiment in that the valve main body 850 is formed so as to satisfy the relationship of R = 0.00. That is, the radius r1 of the small curvature portion 871 when the advance angle supply check valve 85 according to the first comparative embodiment is in the free state is the same as the radius r2 of the constant curvature portion 861. Therefore, in the advance angle supply check valve 85 according to the first comparative embodiment, the valve body 850 does not have the small curvature portion 871, and the constant curvature portion 861 having a constant curvature (r2) from the outer end portion 852 to the inner end portion 851. It can also be said that it has. Therefore, when the advance angle supply check valve 85 is in the free state, the inner peripheral wall of the outer end 852 of the valve body 850 is in contact with the outer peripheral wall of the portion on the inner end 851 side (see FIG. 16). The advance angle supply check valve 85 according to the first comparative embodiment has the same configuration as the check valve of Patent Document 2 (U.S. Pat. No. 7,600,561) described above.

As shown in FIG. 17, when the advance angle supply check valve 85 according to the first comparative embodiment is deformed most by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41, the inner end portion 851 is the support point. Thus, the maximum stress generation point P2, which is the generation point of the maximum stress among the stresses generated in the valve body 850, is a position of about 90 ° from the inner end portion 851.

18 is different from the advance supply check valve 82 according to the present embodiment in that the valve main body 850 is formed so as to satisfy the relationship of R = 1.00. That is, the radius r1 of the small curvature portion 871 when the advance angle supply check valve 86 according to the second comparative embodiment is in the free state is smaller than the radius r1 of the small curvature portion 871 of the advance angle supply check valve 82 according to the present embodiment. Therefore, the clearance S1 formed between the inner peripheral wall of the outer end 852 of the valve body 850 and the outer peripheral wall of the small curvature portion 871 when the advance supply check valve 86 according to the second comparative embodiment is in the free state is the present embodiment. It is larger than the clearance S1 in the advance angle supply check valve 82 according to the form.

As shown in FIG. 19, when the advance angle supply check valve 86 according to the second comparative embodiment is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41, the stress generated in the valve body 850 Among them, the maximum stress generation point P3, which is the generation point of the maximum stress, is at a position of about 180 ° from the inner end portion 851.

FIG. 20 shows a valve for the case where the curvature reduction coefficient R is 0.00 (first comparative embodiment), 0.29, 0.58 (this embodiment), 0.77, 1.00 (second comparative embodiment). When the main body 850 is most deformed by the flow of hydraulic oil from the advance supply opening OAs inside the inner sleeve 41, the relationship between the angle (position) from the inner end 851 of the valve main body 850 and the magnitude of the generated stress. Indicates.

As shown in FIG. 20, when the curvature reduction coefficient R is 0.00 (first comparative example), the stress increases when the angle from the inner end 851 is from 0 ° to about 90 °, and from about 90 ° to 180 °. The stress decreases until °. That is, when the curvature reduction coefficient R is 0.00 (first comparative example), the location where the maximum stress is generated is at a position of about 90 ° from the inner end portion 851. The maximum stress is relatively large. Therefore, a large stress is generated at a position of about 90 ° from the inner end portion 851, that is, the stress is concentrated at a specific location, which may cause deformation or breakage of the valve body 850.

As shown in FIG. 20, when the curvature reduction coefficient R is 1.00 (second comparative example), the stress is substantially 0 when the angle from the inner end 851 is from 0 ° to about 45 °, and about 45 °. From 180 to 180 °. That is, when the curvature reduction coefficient R is 1.00 (second comparative example), the location where the maximum stress is generated is at a position of about 180 ° from the inner end portion 851. The maximum stress is smaller than that in the case where the curvature reduction coefficient R is 0.00 (first comparative example). Therefore, although stress concentration can be avoided while reducing the stress generated in the valve body 850, the bending deformation in the vicinity of the inner end portion 851 (from 0 ° to about 45 °) of the valve body 850 becomes excessively small, which is sufficient for the valve body 850. There is a possibility that the spring force cannot be exerted.

As shown in FIG. 20, when the curvature reduction coefficient R is 0.58 (this embodiment), the stress gradually increases from the angle from the inner end 851 to 0 ° to 180 °. That is, when the curvature reduction coefficient R is 0.58 (this embodiment), the location where the maximum stress is generated is at a position of about 180 ° from the inner end portion 851. The maximum stress is smaller than that in the case where the curvature reduction coefficient R is 1.00 (second comparative example). Therefore, the valve body 850 is smoothly bent from the inner end portion 851 to a position of about 180 °, and stress concentration is avoided while reducing the stress generated in the valve body 850, and sufficient spring force is exerted on the valve body 850. Can be made. As described above, the advance angle supply check valve 82 according to the present embodiment causes the valve body 850 to exert a sufficient spring force while avoiding stress concentration while reducing the stress generated in the valve body 850 at the maximum deformation. This is advantageous over the first and second comparative embodiments.

As shown in FIG. 20, even when the curvature reduction coefficient R is 0.29, the stress generated in the valve body 850 is reduced as compared with the case where the curvature reduction coefficient R is 0.00 (first comparative embodiment). However, stress concentration can be avoided. Further, even when the curvature reduction coefficient R is 0.77, the vicinity of the inner end portion 851 of the valve body 850 (from 0 ° to about 45 °) is compared with the case where the curvature reduction coefficient R is 1.00 (second comparative embodiment). Can be increased, and the valve body 850 can exhibit an appropriate spring force.

In the present embodiment, the small curvature portion 871 has the curvature (r1) when the advance angle supply check valve 82 is in a free state (see FIG. 14), and the advance angle supply check valve 82 supplies the advance angle inside the inner sleeve 41. It is set to be larger than the curvature (r3) of the constant curvature portion 861 when it is most deformed by the flow of hydraulic oil from the opening OAs (see FIG. 15).

Further, in the present embodiment, the small curvature portion 871 is formed so as to include the inner end portion 851 of the valve body 850, and when the advance angle supply check valve 82 is provided inside the inner sleeve 41, the small curvature portion 871 is fixed. The end opposite to the curvature portion 861, that is, the inner end portion 851 is separated from the inner peripheral wall of the constant curvature portion 861 (see FIG. 12), and the advance angle supply check valve 82 advances inside the inner sleeve 41. The end opposite to the constant curvature portion 861, that is, the inner end portion 851 of the constant curvature portion 861 until the time when it is most deformed by the flow of hydraulic oil from the corner supply opening OAs (see FIG. 15). Contact the inner wall.

That is, in the present embodiment, the valve main body 850 has the inner end portion 851 separated from the inner peripheral wall of the portion on the outer end portion 852 side when the advance angle supply check valve 82 is provided inside the inner sleeve 41. The inner end portion 851 is located on the outer end portion 852 side until the advance angle supply check valve 82 is most deformed by the flow of hydraulic oil from the advance angle supply opening portion OAs inside the inner sleeve 41. It touches the inner peripheral wall.

As described above, in the present embodiment, the inner sleeve 41 as a cylindrical tube member having the retard supply opening ORs and the advance supply opening OAs as the inflow holes communicating the outer peripheral wall and the inner peripheral wall. Provided inside, allowing the flow of hydraulic oil toward the inside of the inner sleeve 41 via the retard supply opening ORs and the advance supply opening OAs, the retard supply opening ORs from the inner sleeve 41, The retard supply check valve 81 and the advance supply check valve 82 are capable of regulating the flow of hydraulic oil toward the advance supply opening OAs, and include a valve body 850. The valve body 850 is formed in a cylindrical shape by winding a single plate material.

When the retard supply check valve 81 and the advance supply check valve 82 are in a free state, the valve body 850 includes an inner end 851 that is one end in the circumferential direction and an outer end that is the other end in the circumferential direction. A constant curvature portion 861 having a constant curvature at a specific portion between the 852 and a small curvature portion 871 having a curvature smaller than the curvature of the constant curvature portion 861 at a portion other than the constant curvature portion 861 in the circumferential direction. . Therefore, the retard supply check valve 81 and the advance supply check valve 82 are deformed so as to be contracted radially inward by the flow of hydraulic oil from the retard supply opening ORs and the advance supply opening OAs inside the inner sleeve 41. When the valve is opened, the timing at which the deformation of the portion on the inner end 851 side of the valve main body 850 starts can be delayed with respect to the portion on the outer end 852 side. As a result, the inner end portion 851 serves as a support point, and it is possible to suppress the occurrence of stress due to load bias at a position of about 90 ° from the position. Therefore, deformation or breakage of the retard supply check valve 81 and the advance supply check valve 82 can be suppressed. In the present embodiment, when the retard supply check valve 81 and the advance supply check valve 82 are in the free state, the valve body 850 is positioned such that the inner end 851 side portion is located inside the outer end 852 side portion. That is, both ends are formed to overlap in the circumferential direction.

In this embodiment, the small curvature portion 871 is formed at the inner end portion 851 of the valve body 850. By bringing the small curvature portion 871 toward the inner end portion 851 of the valve body 850, the contact point with the portion on the outer end portion 852 side is continuously moved with respect to the diameter reduction, so that the contact position is rapidly increased. It is possible to prevent an extreme inflection point from occurring in the spring load characteristics due to the change.

Further, in the present embodiment, the small curvature portion 871 has the curvature when the retard supply check valve 81 and the advance supply check valve 82 are in the free state, and the retard supply check valve 81 and the advance supply check valve 82 are inner. It is set to be larger than the curvature of the constant curvature portion 861 when it is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the sleeve 41. Thus, since the small curvature part 871 is set to be equal to or greater than the curvature at the time of the maximum deformation of the entire valve body 850, the entire small curvature part 871 is deformed and a larger spring force can be exerted.

In the present embodiment, the valve main body 850 has the inner end portion 851 on the outer end portion 852 side when the retard supply check valve 81 and the advance supply check valve 82 are provided inside the inner sleeve 41. Until the time when the retard supply check valve 81 and the advance supply check valve 82 are most deformed by the flow of hydraulic oil from the advance supply opening OAs inside the inner sleeve 41. Further, the inner end portion 851 contacts the inner peripheral wall of the portion on the outer end portion 852 side. Therefore, while avoiding stress concentration of the valve body 850, the valve body 850 can exert a spring force at any time from the state set inside the inner sleeve 41 to the maximum deformation.

In this embodiment, the radius of the small curvature portion 871 is r1 when the retard supply check valve 81 and the advance supply check valve 82 are in the free state, and the retard supply check valve 81 and the advance supply check valve 82 are free. When the radius of the constant curvature portion 861 in the state is r2, the retard supply check valve 81, and the advance supply check valve 82 are most deformed by the flow of hydraulic oil from the advance supply opening OAs inside the inner sleeve 41. When the radius of the constant curvature portion 861 is r3 and the curvature reduction coefficient R is (r2-r1) / (r2-r3), the valve body 850 is formed to satisfy the relationship of R> 0.29. Therefore, stress concentration can be avoided while reducing the stress generated in the valve body 850.

In this embodiment, the valve body 850 is formed so as to satisfy the relationship of R <0.77. Therefore, the bending deformation in the vicinity of the inner end portion 851 of the valve body 850 (from 0 ° to about 45 °) can be increased, and an appropriate spring force can be exerted on the valve body 850. In this embodiment, the valve body 850 is formed so as to satisfy the relationship of R = 0.58. Therefore, the valve body 850 is smoothly bent from the inner end portion 851 to a position of about 180 °, and the valve body A sufficient spring force can be exerted on the valve body 850 while avoiding stress concentration while reducing stress generated in the 850.

(Seventh embodiment)
FIG. 21 shows an advance angle supply check valve that is a part of the valve timing adjustment device according to the seventh embodiment of the present disclosure. The seventh embodiment differs from the sixth embodiment in the configuration of the retard supply check valve 81 and the advance supply check valve 82.

FIG. 21 shows the lead angle supply check valve 82 in a free state. As shown in FIG. 21, in the advance angle supply check valve 82 according to the present embodiment, the valve body 850 has a constant curvature portion 861, a small curvature portion 871, and a constant curvature portion 862. The constant curvature portion 861 is a specific portion of the valve body 850 in the circumferential direction, and one end thereof coincides with the outer end portion 852 and the other end is located between the outer end portion 852 and the inner end portion 851. . The small curvature portion 871 is a specific portion in the circumferential direction of the valve main body 850, one end coincides with the other end of the constant curvature portion 861, and the other end is positioned between the outer end portion 852 and the inner end portion 851. is doing. The constant curvature portion 862 is a specific portion of the valve body 850 in the circumferential direction, and one end thereof coincides with the other end of the small curvature portion 871 and the other end thereof coincides with the inner end portion 851.

The curvature of the constant curvature portion 861 and the constant curvature portion 862 are constant over the entire range from one end to the other when the advance angle supply check valve 82 is in a free state. Further, the small curvature portion 871 has a constant curvature in the entire range from one end to the other end when the advance angle supply check valve 82 is in a free state. Here, the radius r1 of the small curvature portion 871 is smaller than the radius r2 of the constant curvature portion 861 and the constant curvature portion 862 (see FIG. 21). That is, the valve body 850 includes a constant curvature portion 861, a constant curvature portion 862, and a circumferential constant curvature portion 861, each having a constant curvature at a specific portion in the circumferential direction, when the advance supply check valve 82 is in a free state. A portion other than the constant curvature portion 862 has a constant curvature portion 861 and a small curvature portion 871 smaller than the curvature of the constant curvature portion 862. In other words, the small curvature portion 871 is formed between the inner end portion 851 and the outer end portion 852 of the valve body 850 and at a position away from each of the inner end portion 851 and the outer end portion 852.

The angle θ1 from one end of the constant curvature portion 861 to the other end is, for example, about 270 °. Further, the angle θ2 from one end of the small curvature portion 871 to the other end is, for example, about 70 °. Further, the angle θ3 from one end of the constant curvature portion 862 to the other end is, for example, about 35 °. When the advance angle supply check valve 82 is in a free state, the outer end portion 852 of the valve body 850 is located on the radially outer side of the constant curvature portion 862. At this time, a gap S2 is formed between the inner peripheral wall of the outer end 852 of the valve body 850 and the outer peripheral wall of the constant curvature portion 862 (see FIG. 21). Thus, in this embodiment, when the advance angle supply check valve 82 is in the free state, the valve main body 850 is arranged such that the portion on the inner end portion 851 side is located inside the portion on the outer end portion 852 side, that is, Both ends are formed to overlap in the circumferential direction. The configuration of the retard supply check valve 81 is the same as the configuration of the advance supply check valve 82.

As described above, in the present embodiment, the valve main body 850 includes the inner peripheral portion 851 that is one end portion in the circumferential direction and the peripheral portion when the retard supply check valve 81 and the advance supply check valve 82 are in the free state. Other than the outer end 852 which is the other end in the direction, a constant curvature portion 861 having a constant curvature, a constant curvature portion 862, and a constant curvature portion 861 in the circumferential direction, and other than the constant curvature portion 862 The portion has a small curvature portion 871 whose curvature is smaller than the curvature of the constant curvature portion 861 and the constant curvature portion 862. Therefore, in the present embodiment, as in the sixth embodiment, deformation or breakage of the retard supply check valve 81 and the advance supply check valve 82 can be suppressed. In the present embodiment, when the retard supply check valve 81 and the advance supply check valve 82 are in the free state, the valve body 850 is positioned such that the inner end 851 side portion is located inside the outer end 852 side portion. That is, both ends are formed to overlap in the circumferential direction.

In the present embodiment, the small curvature portion 871 is formed between the inner end portion 851 and the outer end portion 852. Note that the small curvature portion 871 is formed at a predetermined distance from each of the inner end portion 851 and the outer end portion 852 and does not overlap the outer end portion 852 in the circumferential direction.

(Eighth embodiment)
FIG. 22 shows an advance angle supply check valve that is a part of the valve timing adjusting device according to the eighth embodiment of the present disclosure. The eighth embodiment differs from the sixth embodiment in the configuration of the retard supply check valve 81 and the advance supply check valve 82.

FIG. 22 shows the lead angle supply check valve 82 in a free state. In the present embodiment, the small curvature portion 871 is formed so that the radius gradually decreases from one end to the other end. The radius of one end of the small curvature portion 871, that is, the end portion on the constant curvature portion 861 side is r2, the radius of the other end of the small curvature portion 871, that is, the inner end portion 851, is r4, and the average of r2 and r4 is r1 It is. Here, when the advance angle supply check valve 82 is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41, the radius of the constant curvature portion 861 is r3, and the curvature reduction coefficient R is (r2). Assuming −r1) / (r2−r3), the valve body 850 is formed to satisfy the relationship of R = 0.58. The configuration of the retard supply check valve 81 is the same as the configuration of the advance supply check valve 82. In the present embodiment, as in the sixth embodiment, deformation or breakage of the retard supply check valve 81 and the advance supply check valve 82 can be suppressed.

(Ninth embodiment)
FIG. 23 shows an advance angle supply check valve that is a part of the valve timing adjustment device according to the ninth embodiment of the present disclosure. The ninth embodiment differs from the sixth embodiment in the configuration of the retard supply check valve 81 and the advance supply check valve 82.

FIG. 23 shows the lead angle supply check valve 82 in a free state. In the present embodiment, the valve main body 850 includes a constant curvature portion 861, a small curvature portion 871, and a small curvature portion 872. The constant curvature portion 861 is a specific portion of the valve body 850 in the circumferential direction, and one end thereof coincides with the outer end portion 852 and the other end is located between the outer end portion 852 and the inner end portion 851. . The small curvature portion 871 is a specific portion in the circumferential direction of the valve main body 850, one end coincides with the other end of the constant curvature portion 861, and the other end is positioned between the outer end portion 852 and the inner end portion 851. is doing. The small curvature portion 872 is a specific portion in the circumferential direction of the valve body 850, and one end coincides with the other end of the small curvature portion 871 and the other end coincides with the inner end portion 851.

The angle θ1 from one end to the other end of the constant curvature portion 861 is, for example, about 330 °. Further, the angle θ2 from one end to the other end of the small curvature portion 871 is, for example, about 45 °. The angle θ3 from one end to the other end of the small curvature portion 872 is, for example, about 45 °. When the advance angle supply check valve 82 is in a free state, the outer end portion 852 of the valve body 850 is located on the radially outer side near the other end of the small curvature portion 871 (see FIG. 23).

The constant curvature portion 861 has a constant curvature over the entire range from one end to the other when the advance angle supply check valve 82 is in a free state. Further, the small curvature portion 871 and the small curvature portion 872 each have a constant curvature over the entire range from one end to the other end when the advance angle supply check valve 82 is in a free state. Here, the radius r5 of the small curvature portion 871 is smaller than the radius r2 of the constant curvature portion 861. Further, the radius r6 of the small curvature portion 872 is smaller than the radius r5 of the small curvature portion 871 (see FIG. 23). The average of r5 and r6 is r1. Here, when the advance angle supply check valve 82 is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs inside the inner sleeve 41, the radius of the constant curvature portion 861 is r3, and the curvature reduction coefficient R is (r2). Assuming −r1) / (r2−r3), the valve body 850 is formed to satisfy the relationship of R = 0.58. The configuration of the retard supply check valve 81 is the same as the configuration of the advance supply check valve 82. In the present embodiment, as in the sixth embodiment, deformation or breakage of the retard supply check valve 81 and the advance supply check valve 82 can be suppressed.

(10th Embodiment)
A check valve that is a part of the valve timing adjusting device according to the tenth embodiment of the present disclosure is shown in FIGS. The tenth embodiment differs from the first embodiment in the configuration of the supply check valve 61 and the recycle check valve 62. Since the configuration of the recycle check valve 62 is the same as that of the supply check valve 61, only the configuration of the supply check valve 61 will be described, and the description of the configuration of the recycle check valve 62 will be omitted.

24 and 25 show the supply check valve 61 of the check valve 60 in a free state. In the present embodiment, the supply check valve 61 includes a valve main body 850, a small curvature portion 875, and a flat surface portion 881. The valve body 850 has a constant curvature portion 861 and a small curvature portion 871. The constant curvature portion 861 is a specific portion of the valve body 850 in the circumferential direction, and one end thereof coincides with the outer end portion 852 and the other end is located between the outer end portion 852 and the inner end portion 851. . The small curvature portion 871 is a specific portion in the circumferential direction of the valve body 850, and one end coincides with the other end of the constant curvature portion 861 and the other end coincides with the inner end portion 851.

The small curvature portion 875 has one end coinciding with the other end of the small curvature portion 871, that is, the inner end portion 851 of the valve main body 850. The flat portion 881 is formed in a flat shape. The flat portion 881 is formed integrally with the valve body 850, the small curvature portion 875, and the shaft portion 63 so that one end is connected to the other end of the small curvature portion 875 and the other end is connected to the shaft portion 63. The shaft portion 63, the flat surface portion 881, and the small curvature portion 875 support the valve body 850.

The angle θ1 from one end of the constant curvature portion 861 to the other end is, for example, about 270 °. Further, the angle θ2 from one end to the other end of the small curvature portion 871 is, for example, about 90 °. Further, the angle θ3 from one end to the other end of the small curvature portion 875 is, for example, about 90 °. When the supply check valve 61 is in a free state, the outer end 852 of the valve main body 850 is located on the radially outer side near one end of the small curvature portion 875. At this time, a gap S1 is formed between the inner peripheral wall of the outer end 852 of the valve body 850 and the outer peripheral wall of the small curvature portion 875 (see FIG. 25). Thus, in this embodiment, the valve main body 850 is formed so that the inner end portion 851 and the outer end portion 852 do not overlap in the circumferential direction when the supply check valve 61 is in a free state.

The constant curvature portion 861 has a constant curvature over the entire range from one end to the other when the supply check valve 61 is in a free state. Further, the small curvature portion 871 and the small curvature portion 875 each have a constant curvature in the entire range from one end to the other end when the supply check valve 61 is in a free state. Here, the radius r1 of the small curvature portion 871 is smaller than the radius r2 of the constant curvature portion 861. Further, the radius r7 of the small curvature portion 875 is smaller than the radius r1 of the small curvature portion 871 (see FIG. 25). Here, when the supply check valve 61 is most deformed by the flow of hydraulic oil from the supply oil passage 54 inside the spool 50, the radius of the constant curvature portion 861 is r3, and the curvature reduction coefficient R is (r2-r1) / ( Assuming that r2-r3), the valve body 850 is formed to satisfy the relationship of R = 0.58. Further, since the dimension of r3 is adjusted so that r3> r7, the small curvature portion 875 does not deform even when the supply check valve 61 is most deformed, and does not exert a spring force.

Next, by comparing the supply check valve 61 according to the present embodiment with the third comparative embodiment, the advantages of the present embodiment over the third comparative embodiment will be clarified.

26 is different from the supply check valve 61 according to the present embodiment in that the radius r1 of the small curvature portion 871 is the same as the radius r2 of the constant curvature portion 861. Therefore, in the supply check valve 65 according to the third comparative embodiment, the valve main body 850 does not have the small curvature portion 871, but has a constant curvature (from the outer end portion 852 to one end of the small curvature portion 875, that is, the inner end portion 851). It can also be said that it has the constant curvature portion 861 of r2). In the supply check valve 65 according to the third comparative embodiment, the angle θ1 from one end to the other end of the constant curvature portion 861 is, for example, about 270 °. Further, the angle θ2 from one end to the other end of the small curvature portion 871 is, for example, about 90 °. Therefore, when the supply check valve 65 is in a free state, the inner peripheral wall of the outer end 852 of the valve body 850 and the outer peripheral wall of the small curvature portion 871 are in contact (see FIG. 26). The supply check valve 65 according to the third comparative embodiment is formed so that the valve body 850 satisfies the relationship of R = 0.00. The supply check valve 65 of the third comparison form has the same configuration as the supply check valve 61 according to the first embodiment.

When the supply check valve 65 of the third comparative embodiment is most deformed by the flow of hydraulic oil from the supply oil passage 54 inside the spool 50, the inner end 851 serves as a support point, and the maximum stress generated in the valve body 850 The maximum stress generation location, which is the location where the stress is generated, is a position about 90 ° from the inner end portion 851.

On the other hand, when the supply check valve 61 according to the present embodiment is most deformed by the flow of hydraulic oil from the supply oil passage 54 inside the spool 50, the maximum of the stresses generated in the valve body 850 is the maximum stress generation location. The stress generation point is at a position of about 180 ° from the inner end 851. Further, the magnitude of the maximum stress is smaller than the maximum stress generated in the supply check valve 65 of the third comparison form. As described above, the supply check valve 61 according to the present embodiment is superior to the third comparative embodiment in that stress concentration can be avoided while reducing the stress generated in the valve body 850 at the maximum deformation.

As described above, the present embodiment is provided inside the spool 50 as a cylindrical tube member having the supply oil passage 54 and the recycle oil passage 57 as the inflow holes that communicate the outer peripheral wall and the inner peripheral wall. Allow the flow of hydraulic oil toward the inside of the spool 50 via the supply oil path 54 and the recycle oil path 57, and regulate the flow of hydraulic oil toward the supply oil path 54 and the recycle oil path 57 from the inside of the spool 50 The supply check valve 61 and the recycle check valve 62 are provided with a valve body 850. The valve body 850 is formed in a cylindrical shape by winding a single plate material.

When the supply check valve 61 and the recycle check valve 62 are in a free state, the valve main body 850 is between the inner end 851 that is one end in the circumferential direction and the outer end 852 that is the other end in the circumferential direction. The constant curvature portion 861 having a constant curvature at the specific portion and the small curvature portion 871 having a curvature smaller than the curvature of the constant curvature portion 861 at a portion other than the constant curvature portion 861 in the circumferential direction. Therefore, when the supply check valve 61 and the recycle check valve 62 are deformed so as to shrink radially inward due to the flow of hydraulic oil from the supply oil passage 54 and the recycle oil passage 57 inside the spool 50, The timing at which the deformation of the portion on the inner end 851 side can be delayed with respect to the portion on the outer end 852 side. As a result, the inner end portion 851 serves as a support point, and it is possible to suppress the occurrence of stress due to load bias at a position of about 90 ° from the position. Therefore, deformation or breakage of the supply check valve 61 and the recycle check valve 62 can be suppressed. In this embodiment, the valve main body 850 is formed so that the inner end portion 851 and the outer end portion 852 do not overlap in the circumferential direction when the supply check valve 61 and the recycle check valve 62 are in a free state.

(Other embodiments)
In the above-described embodiment, the example in which the sleeve 40 and the spool 50 constituting the oil passage switching valve 11 are arranged in the central portion of the vane rotor 30 has been shown. On the other hand, in another embodiment of the present disclosure, the oil passage switching valve 11 may be disposed at a location other than the central portion of the vane rotor 30, for example, outside the housing 20.

In the above-described embodiment, the first control oil passage 55 that can be connected to the first control port and the second control oil passage 56 that can be connected to the second control port are shown as control oil passages formed in the spool 50. It was. On the other hand, in another embodiment of the present disclosure, a common control oil path that can be connected to the first control port and the second control port may be formed in the spool 50. In this case, a drain oil passage connected to each control port may be formed in the spool.

Further, in the above-described sixth embodiment, the example in which the valve body 850 is formed to satisfy the relationship of R = 0.58 has been shown. On the other hand, in other embodiments of the present disclosure, the valve body 850 may not be formed to satisfy the relationship of R = 0.58. However, from the viewpoint of the effect that can be exhibited, the valve body 850 is preferably formed so as to satisfy the relationship of 0.29 <R <0.77.

Further, in the above-described sixth embodiment, the small curvature portion 871 is formed so as to include the inner end portion 851 of the valve body 850, and the advance angle supply check valve 82 is provided inside the inner sleeve 41. At this time, the end opposite to the constant curvature portion 861, that is, the inner end portion 851 is separated from the inner peripheral wall of the constant curvature portion 861 (see FIG. 12), and the advance angle supply check valve 82 is located on the inner sleeve 41. The end opposite to the constant curvature portion 861, that is, the inner end portion 851 has a constant curvature until it is most deformed by the flow of hydraulic oil from the advance angle supply opening OAs (see FIG. 15). The example which contacts the internal peripheral wall of the part 861 was shown. On the other hand, in another embodiment of the present disclosure, the small curvature portion 871 is an end portion on the opposite side to the constant curvature portion 861 when the advance angle supply check valve 82 is provided inside the inner sleeve 41. That is, the inner end portion 851 may be in contact with the inner peripheral wall of the constant curvature portion 861. That is, in the valve body 850, when the advance angle supply check valve 82 is provided inside the inner sleeve 41, the inner end portion 851 may be in contact with the inner peripheral wall of the portion on the outer end portion 852 side. In this embodiment, the valve body 850 can exert a spring force from the state set inside the inner sleeve 41 while avoiding stress concentration of the valve body 850.

Further, in another embodiment of the present disclosure, the housing 20 and the crankshaft 2 may be connected by a transmission member such as a belt instead of the chain 6.

Further, in the above-described embodiment, an example in which the crankshaft 2 is the “first axis” and the camshaft 3 is the “second axis” has been described. On the other hand, in another embodiment of the present disclosure, the crankshaft 2 may be a “second shaft” and the camshaft 3 may be a “first shaft”. That is, the vane rotor 30 may be fixed to the end of the crankshaft 2 and the housing 20 may rotate in conjunction with the camshaft 3.
The valve timing adjusting device 10 of the present disclosure may adjust the valve timing of the exhaust valve 5 of the engine 1.
Thus, the present disclosure is not limited to the above-described embodiment, and can be implemented in various forms without departing from the gist thereof.

This disclosure has been described based on embodiments. However, the present disclosure is not limited to the embodiments and structures. The present disclosure also includes various modifications and modifications within the equivalent scope. Also, various combinations and forms, as well as other combinations and forms including only one element, more or less, are within the scope and spirit of the present disclosure.

Claims (19)

1. A valve that is provided in a power transmission path for transmitting power from the drive shaft (2) to the driven shaft (3) of the internal combustion engine (1) and adjusts the valve timing of the valves (4, 5) that are driven to open and close by the driven shaft. A timing adjustment device (10) comprising:
   When one of the drive shaft and the driven shaft is a first axis and the other of the drive shaft and the driven shaft is a second axis,
   A housing (20) that rotates in conjunction with the first shaft, engages with an end of the second shaft, and is rotatably supported by the second shaft;
   Fixed to the end of the second shaft, the internal space (200) of the housing is partitioned into a first hydraulic chamber (201) on one circumferential side and a second hydraulic chamber (202) on the other circumferential side. A vane rotor (30) having a vane (32) and rotating relative to the housing according to the pressure of hydraulic oil supplied from the hydraulic oil supply source (8) to the first hydraulic chamber and the second hydraulic chamber. When,
   A supply port (43) communicating with the hydraulic oil supply source, a first control port (44) communicating with the first hydraulic chamber, and a second control port (45) communicating with the second hydraulic chamber A cylindrical sleeve (40) having
   A pressure accumulating space (500) provided inside the sleeve so as to be reciprocally movable in the axial direction, a supply oil passage (54) formed to connect the pressure accumulating space and the supply port, and the pressure accumulating A control oil passage (55, 56) formed so that the space and the first control port or the second control port can be connected, and the pressure accumulation space and the first control port or the second control port are connected A cylindrical spool (50) having a recycle oil passage (57, 571, 572) formed possible;
   When the valve is opened, the flow of hydraulic oil from the hydraulic oil supply source side to the pressure accumulation space side via the supply oil path is allowed, and when the valve is closed, the pressure accumulation space side is routed through the supply oil path. Supply check valves (61, 68) for regulating the flow of hydraulic oil toward the hydraulic oil supply source side,
   When the valve is opened, the flow of hydraulic oil from the first hydraulic chamber or the second hydraulic chamber side to the pressure accumulating space side via the recycle oil passage is allowed, and when the valve is closed, the pressure accumulating space side A recycle check valve (62, 621, 622, 69) that regulates the flow of hydraulic oil toward the first hydraulic chamber or the second hydraulic chamber via the recycle oil passage,
   The valve timing adjusting device is different in characteristics relating to opening of the supply check valve from those relating to opening of the recycle check valve.
2. 2. The valve timing adjusting device according to claim 1, wherein the characteristics relating to the opening of the supply check valve are set to characteristics that are easier to open than the recycle check valve.
3. The valve timing adjusting device according to claim 1 or 2, wherein a valve opening pressure of the supply check valve is set lower than a valve opening pressure of the recycle check valve.
4. The supply check valve is provided inside the spool, and closes the supply oil passage when the valve is closed,
   The valve timing adjusting device according to any one of claims 1 to 3, wherein the recycle check valve is provided inside the spool and closes the recycle oil passage when the valve is closed.
5. The valve timing adjusting device according to claim 4, wherein the spool has a supply side support portion (591) for supporting the supply check valve and a recycle side support portion (592) for supporting the recycle check valve. .
6. The valve timing adjusting device according to any one of claims 1 to 5, wherein the supply check valve and the recycle check valve are formed of elastically deformable plate materials, each having a different width or plate thickness.
7. The supply check valve and the recycle check valve are formed of elastically deformable plate materials having the same width and thickness,
   The valve timing adjusting device according to any one of claims 1 to 5, wherein a total flow area of the supply oil path is different from a total flow area of the recycle oil path.
8. The valve timing adjusting device according to claim 7, wherein the supply oil passage has an inner diameter that is the same as an inner diameter of the recycle oil passage, and the number of spools formed in the spool is different from that of the recycle oil passage.
9. The supply check valve is provided outside the spool, and closes the supply port when the valve is closed,
   The valve timing adjusting device according to any one of claims 1 to 3, wherein the recycle check valve is provided inside the spool and closes the recycle oil passage when the valve is closed.
10. The sleeve further includes a recycle port (481, 482) formed so as to be connectable to the pressure accumulation space and the first hydraulic chamber or the second hydraulic chamber.
    The supply check valve is provided outside the spool, and closes the supply port when the valve is closed,
    The valve timing adjusting device according to any one of claims 1 to 3, wherein the recycle check valve is provided outside the spool and closes the recycle port when the valve is closed.
11. The valve timing adjusting device according to any one of claims 1 to 10, wherein the sleeve is disposed at a central portion of the vane rotor.
12. Provided inside a cylindrical tube member (41, 50) having an inflow hole (ORs, OAs, 54, 57) communicating with the outer peripheral wall and the inner peripheral wall, and inside the cylindrical member via the inflow hole A check valve (61, 62, 81, 82) capable of regulating the flow of fluid toward the inflow hole from the inside of the cylindrical member,
    A valve body (850) formed into a cylindrical shape by winding a single plate material,
    When the check valve is in a free state, the valve body is specified between an inner end (851) that is one end in the circumferential direction and an outer end (852) that is the other end in the circumferential direction. And constant curvature portions (861, 862) having a constant curvature in the region, and small curvature portions (871, 872) having a curvature smaller than the curvature of the constant curvature portion in the region other than the constant curvature portion in the circumferential direction. Check valve.
13. The check valve according to claim 12, wherein the small curvature portion is formed at the inner end portion.
14. The check valve according to claim 12, wherein the small curvature portion is formed between the inner end portion and the outer end portion.
15. The small curvature portion is larger in curvature when the check valve is in a free state than the curvature of the constant curvature portion when the check valve is most deformed by the flow of fluid from the inflow hole inside the cylindrical member. The check valve according to any one of claims 12 to 14, which is set to be
16. In the valve body, when the check valve is provided inside the cylindrical member, the inner end portion is separated from an inner peripheral wall of a portion on the outer end portion side, and the check valve is connected to the cylindrical member. The inner end portion contacts the inner peripheral wall of the outer end portion side until the innermost wall is deformed most by the fluid flow from the inflow hole. Check valve described.
17. 16. The valve main body according to claim 12, wherein the inner end portion is in contact with an inner peripheral wall of a portion on the outer end portion side when the check valve is provided inside the cylindrical member. The check valve according to one item.
18. The radius of the small curvature portion when the check valve is in a free state is r1, the radius of the constant curvature portion when the check valve is in a free state is r2, and the check valve is inside the cylindrical member from the inflow hole. When the radius of the constant curvature portion when deformed most by the flow of the fluid is r3 and the curvature reduction coefficient R is (r2-r1) / (r2-r3),
    The check valve according to any one of claims 12 to 17, wherein the valve body is formed so as to satisfy a relationship of R> 0.29.
19. The check valve according to claim 18, wherein the valve body is formed so as to satisfy a relationship of R <0.77.

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