阅读说明：本技术 工作油控制阀和阀正时调整装置 (Working oil control valve and valve timing adjusting device ) 是由 川村太 于 2020-03-24 设计创作，主要内容包括：被配置于阀正时调整装置(100)的旋转轴(AX)的工作油控制阀(10、10a～10e)具备套筒(20)、在套筒的径向的内侧沿轴向(AD)滑动的阀芯(50)以及捕捉包含在工作油中的异物的过滤器构件(200、200d、200e),套筒具有内套筒(40)以及形成有沿着轴向的轴孔(34、34b)的外套筒(30、30a～30c),轴孔与内套筒之间的径向的空间作为工作油供给油路(25)发挥功能,过滤器构件在空间中被配置于从径向观察时与被配置于内套筒的内部的内部构件(50、60、91)中的至少一个重叠的位置。(The hydraulic oil control valve (10, 10 a-10 e) disposed on a rotating shaft (AX) of a valve timing adjusting device (100) is provided with a sleeve (20), a valve body (50) sliding in an Axial Direction (AD) on the inner side in the radial direction of the sleeve, and filter members (200, 200d, 200e) for capturing foreign matter contained in hydraulic oil, wherein the sleeve comprises an inner sleeve (40) and outer sleeves (30, 30 a-30 c) formed with axial holes (34, 34b) along the axial direction, the radial space between the axial hole and the inner sleeve functions as a hydraulic oil supply oil passage (25), and the filter members are disposed in the space at positions overlapping at least one of the inner members (50, 60, 91) disposed inside the inner sleeve when viewed in the radial direction.)

1. In a valve timing adjustment device (100) that is fixed to one shaft end (321) of a drive shaft (310) and a driven shaft (320) that is driven by power transmitted from the drive shaft to open and close a valve (330) and that adjusts the valve timing of the valve, a hydraulic oil control valve (10, 10 a-10 e) that is disposed on a rotation shaft (AX) of the valve timing adjustment device and controls the flow of hydraulic oil supplied from a hydraulic oil supply source (350), the hydraulic oil control valve comprising:

a cylindrical sleeve (20);

a valve body (50) that is driven by an actuator (160) disposed in contact with one end of the valve body, and that slides in an Axial Direction (AD) inside the sleeve in the radial direction;

a filter member (200, 200d, 200e) that traps foreign matter contained in the working oil,

the sleeve has:

an inner sleeve (40) disposed outside the valve element in the radial direction; and

outer sleeves (30, 30 a-30 c) having axial holes (34, 34b) formed along the axial direction, the inner sleeves being inserted into the axial holes and capable of being fixed to the end of the one shaft by applying an axial force in the axial direction,

the radial space between the shaft hole and the inner sleeve functions as a hydraulic oil supply passage (25) that communicates with the hydraulic oil supply source in a state where the outer sleeve is fixed to the end of the one shaft,

the filter member is disposed in the space at a position overlapping at least one of inner members (50, 60, 91) disposed inside the inner sleeve as viewed from the radial direction.

2. The working oil control valve according to claim 1,

the inner member includes the spool and a spring (60) that urges the spool toward the actuator side in the axial direction.

3. The working oil control valve according to claim 1 or 2,

the space is formed over the entire circumference in at least a part of the axial direction.

4. The working oil control valve according to any one of claims 1 to 3,

the filter member is formed in a ring shape,

an inner sleeve end (248) on the opposite side of the actuator side as the axial end of the inner sleeve has an outer diameter smaller than an inner diameter of the filter member.

5. The working oil control valve according to any one of claims 1 to 4,

the filter member is fixed to a first sleeve (40) of one of the outer sleeve and the inner sleeve.

6. The working oil control valve according to claim 5,

a support portion (244, 244e) for supporting the filter member is formed in the first sleeve,

the filter member is formed in a ring shape, and has:

a fixing portion (210) formed along the axial direction and fixed to the first sleeve;

a catching part (230, 230d, 230e) connected to the fixing part, formed in a direction crossing the axial direction, and catching the foreign matter;

a filter end (222, 222d) that faces the other second sleeve (30, 30 a-30 c) of the outer sleeve and the inner sleeve and is located on the side opposite to the actuator side in the axial direction; and

a supported portion (232, 232e) supported by the supporting portion,

a linear dimension (L1) in a cross section along the axial direction from the filter end portion to the supported portion is larger than the dimension (L2) in the radial direction between the second sleeve and the supported portion.

7. A valve timing adjusting apparatus provided with the hydraulic oil control valve according to any one of claims 1 to 6.

Technical Field

The present disclosure relates to a working oil control valve for a valve timing adjusting apparatus.

Background

Conventionally, a hydraulic valve timing adjusting device capable of adjusting the valve timing of an intake valve and an exhaust valve of an internal combustion engine is known. In a hydraulic valve timing adjusting device, a working oil control valve provided at a central portion of a vane rotor (vane rotor) may supply and discharge working oil to and from respective hydraulic chambers defined in a housing by the vane rotor. Patent document 1 discloses the following hydraulic oil control valve: the camshaft includes a cylindrical sleeve (sleeve) having a double structure including an outer sleeve and an inner sleeve, the outer sleeve being fastened to an end portion of the camshaft, and the oil passage being switched by sliding a valve body (spool) inside the inner sleeve. In the hydraulic oil control valve, a radial space between the outer sleeve and the inner sleeve functions as a hydraulic oil supply passage.

Documents of the prior art

Patent document

Patent document 1: international publication No. 2018/135586

Disclosure of Invention

In the hydraulic oil control valve described in patent document 1, a filter member for trapping foreign matter contained in the hydraulic oil is disposed at an end portion of the inner sleeve on the camshaft side. Therefore, the dimension of the inner sleeve in the axial direction may be increased in size for disposing the filter member. Due to the increase in size, the degree of freedom in designing the hydraulic oil control valve may be reduced, such as an increase in size of the outer sleeve in the axial direction. Therefore, a technique capable of suppressing an increase in the size of the inner sleeve in the axial direction is desired.

The present disclosure can be implemented as follows.

According to one aspect of the present disclosure, a working oil control valve is provided. In a valve timing adjusting device that is fixed to an end portion of one of a drive shaft and a driven shaft that is driven by power transmitted from the drive shaft to open and close a valve and that adjusts a valve timing of the valve, the hydraulic control valve is used by being disposed on a rotary shaft of the valve timing adjusting device and controls a flow of hydraulic oil supplied from a hydraulic oil supply source, and the hydraulic control valve includes: a cylindrical sleeve; a valve body that is driven by an actuator disposed in contact with one end of the valve body, and that slides in an axial direction inside the sleeve in a radial direction; a filter member that traps foreign matter contained in the working oil, the sleeve having: an inner sleeve disposed outside the valve element in the radial direction; and an outer sleeve having an axial hole along the axial direction, the inner sleeve being inserted into the axial hole and being capable of being fixed to an end portion of the one shaft by applying an axial force in the axial direction, wherein the radial space between the axial hole and the inner sleeve functions as a hydraulic oil supply passage communicating with the hydraulic oil supply source in a state where the outer sleeve is fixed to the end portion of the one shaft, and the filter member is disposed in the space at a position overlapping at least one of internal members disposed inside the inner sleeve when viewed in the radial direction.

According to the hydraulic oil control valve of this aspect, the filter member is disposed in the radial space between the shaft hole that functions as the hydraulic oil supply passage and the inner sleeve at a position that overlaps with at least one of the inner members disposed inside the inner sleeve when viewed in the radial direction. Therefore, the size of the inner sleeve in the axial direction can be prevented from being increased by the arrangement of the filter member.

The present disclosure can also be implemented in various ways. For example, the present invention can be realized by a method for manufacturing a hydraulic oil control valve, a valve timing adjusting apparatus including a hydraulic oil control valve, a method for manufacturing the valve timing adjusting apparatus, and the like.

Drawings

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. In the context of this figure, it is shown,

FIG. 1 is a sectional view showing a schematic configuration of a valve timing adjusting apparatus including a hydraulic oil control valve,

figure 2 is a sectional view showing a section along line II-II of figure 1,

fig 3 is a sectional view showing a detailed structure of the operating oil control valve,

fig. 4 is an exploded perspective view showing the detailed structure of the hydraulic oil control valve in an exploded manner,

figure 5 is a perspective view showing the detailed structure of the filter member,

figure 6 is a sectional perspective view showing a detailed structure of the filter member,

figure 7 is an enlarged cross-sectional view showing an enlarged area VII of figure 3,

FIG. 8 is a sectional view showing a state where the valve body abuts on the stopper,

FIG. 9 is a sectional view showing a state where the spool is located at substantially the center of the sliding range,

fig. 10 is a sectional view showing the detailed structure of the working oil control valve of the second embodiment,

fig. 11 is a sectional view showing the detailed structure of the working oil control valve of the third embodiment,

fig. 12 is a sectional view showing a detailed structure of a working oil control valve of the fourth embodiment,

figure 13 is a sectional view illustrating a filter member in the fifth embodiment,

fig. 14 is a sectional view illustrating a filter member in the sixth embodiment.

Detailed Description

A. The first embodiment:

a-1. device structure:

the valve timing adjusting apparatus 100 shown in fig. 1 adjusts the valve timing of a valve that is driven to open and close by a camshaft 320 to which power is transmitted from a crankshaft 310 in an internal combustion engine 300 provided in a vehicle, not shown. The valve timing adjusting apparatus 100 is provided in a power transmission path from the crankshaft 310 to the camshaft 320. More specifically, the valve timing adjusting apparatus 100 is fixedly disposed at the end 321 of the camshaft 320 in a direction along the rotation axis AX of the camshaft 320 (hereinafter also referred to as "axial direction AD"). The rotation axis AX of the valve timing adjusting device 100 coincides with the rotation axis AX of the camshaft 320. The valve timing adjusting apparatus 100 of the present embodiment adjusts the valve timing of the intake valve 330 and the exhaust valve 340.

A shaft hole 322 and a supply hole 326 are formed in an end 321 of the camshaft 320. The shaft hole portion 322 is formed in the axial direction AD. A shaft fixing portion 323 for fixing the hydraulic oil control valve 10 described later is formed on the inner circumferential surface of the shaft hole portion 322. The shaft fixing portion 323 has a female screw portion 324 formed therein. The female screw portion 324 is screwed to a male screw portion 33 formed in the valve fixing portion 32 of the hydraulic oil control valve 10. The supply hole portion 326 is formed in a radial direction so that the outer circumferential surface of the camshaft 320 communicates with the supply hole 328. The supply hole 326 is supplied with hydraulic oil from a hydraulic oil supply source 350. The working oil supply source 350 has an oil pump 351 and an oil pan (oil pan) 352. The oil pump 351 draws the working oil stored in the oil pan 352.

As shown in fig. 1 and 2, the valve timing adjusting apparatus 100 includes a housing 120, a vane rotor 130, and a hydraulic oil control valve 10. In fig. 2, the working oil control valve 10 is not shown.

As shown in fig. 1, the housing 120 has a sprocket (sprocket)121 and a case 122. The sprocket 121 is fitted to the end 321 of the camshaft 320 and is rotatably supported. The sprocket 121 has an engagement recess 128 formed at a position corresponding to a lock pin 150 described later. An endless timing chain 360 is hung on the sprocket 121 together with the sprocket 311 of the crankshaft 310. The sprocket 121 is fixed to the housing 122 by a plurality of bolts 129. Therefore, the housing 120 rotates in conjunction with the crankshaft 310. The case 122 has a bottomed cylindrical external shape, and the open end is closed by the sprocket 121. As shown in fig. 2, the housing 122 has a plurality of partition walls 123 formed to be circumferentially aligned with each other toward the radially inner side. Between the partition walls 123 adjacent to each other in the circumferential direction, the partition walls function as hydraulic chambers 140. As shown in fig. 1, an opening 124 is formed in the center of the bottom of the case 122.

The vane rotor 130 is housed in the casing 120, and rotates relative to the casing 120 in the retarded angle direction or the advanced angle direction according to the hydraulic pressure of the hydraulic oil supplied from the hydraulic oil control valve 10 described later. Therefore, the vane rotor 130 functions as a phase changing portion that changes the phase of the driven shaft with respect to the drive shaft. The blade rotor 130 has a plurality of blades 131 and a hub 135.

As shown in fig. 2, each of the plurality of blades 131 protrudes radially outward from the hub 135 located at the center of the blade rotor 130, and is formed to be aligned with each other in the circumferential direction. Each vane 131 is accommodated in each hydraulic chamber 140, and divides each hydraulic chamber 140 into a retarded angle chamber 141 and an advanced angle chamber 142 in the circumferential direction. The retard angle chamber 141 is located at one circumferential side with respect to the vane 131. The advance chamber 142 is located on the other side in the circumferential direction with respect to the vane 131. A receiving hole portion 132 is formed in one blade 131 of the plurality of blades 131 in the axial direction. The housing hole 132 communicates with the retarded angle chamber 141 through a retarded angle chamber side pin control oil passage 133 formed in the vane 131, and communicates with the advanced angle chamber 142 through an advanced angle chamber side pin control oil passage 134. A lock pin 150 that is capable of reciprocating in the axial direction AD is disposed in the housing hole 132. The lock pin 150 restricts relative rotation of the vane rotor 130 with respect to the housing 120, and suppresses collision between the housing 120 and the vane rotor 130 in the circumferential direction in a state where the oil pressure is insufficient. The lock pin 150 is biased in the axial direction AD toward the fitting recess 128 formed in the sprocket 121 by a spring 151.

The boss 135 has a cylindrical external shape and is fixed to an end 321 of the camshaft 320. Therefore, the vane rotor 130 formed with the hub 135 is fixed to the end 321 of the camshaft 320 and rotates integrally with the camshaft 320. A through hole 136 penetrating in the axial direction AD is formed in the center of the hub 135. The hydraulic oil control valve 10 is disposed in the through hole 136. In the hub 135, a plurality of retarded angle oil passages 137 and a plurality of advanced angle oil passages 138 are formed to penetrate in the radial direction. The retarded angle oil passages 137 and the advanced angle oil passages 138 are formed in an axial direction AD in an aligned manner. Each of the retarded angle oil passages 137 communicates a retarded angle port 27 of the hydraulic oil control valve 10 described later with a retarded angle chamber 141. Each advance oil passage 138 communicates an advance chamber 142 with an advance port 28 of the hydraulic oil control valve 10, which will be described later. In the through hole 136, a space between each retarded angle oil passage 137 and each advanced angle oil passage 138 is sealed by an outer sleeve 30 of the hydraulic oil control valve 10 described later.

In the present embodiment, the casing 120 and the vane rotor 130 are formed of an aluminum alloy, but the present invention is not limited to the aluminum alloy, and may be formed of any metal material such as iron and stainless steel, a resin material, or the like.

As shown in fig. 1, the hydraulic oil control valve 10 is disposed at the rotation axis AX of the valve timing adjusting device 100, and controls the flow of hydraulic oil supplied from a hydraulic oil supply source 350. The operation of the hydraulic control valve 10 is controlled in accordance with an instruction from an ECU (not shown) that controls the overall operation of the internal combustion engine 300. The hydraulic oil control valve 10 is driven by a solenoid 160 disposed on the opposite side of the camshaft 320 in the axial direction AD. The solenoid 160 has an electromagnetic portion 162 and a shaft 164. The solenoid 160 displaces the shaft 164 in the axial direction AD by energization of the solenoid portion 162 based on the instruction of the ECU, thereby pressing the valve body 50 of the hydraulic control valve 10 described later toward the camshaft 320 against the biasing force of the spring 60. In the following description, for convenience, the side opposite to the solenoid 160 side in the axial direction AD is referred to as "the camshaft 320 side". As will be described later, the valve body 50 slides in the axial direction AD by pressing, and thereby the oil passage communicating with the retarded angle chamber 141 and the oil passage communicating with the advanced angle chamber 142 can be switched.

As shown in fig. 3 and 4, the hydraulic oil control valve 10 includes a sleeve 20, a valve body 50, a spring 60, a fixing member 70, a check valve 90, and a filter member 200. Further, in fig. 3, a cross section along the rotation axis AX is shown.

The sleeve 20 has an outer sleeve 30 and an inner sleeve 40. The outer sleeve 30 and the inner sleeve 40 each have a substantially cylindrical external shape. The sleeve 20 has a schematic structure in which the inner sleeve 40 is inserted into the shaft hole 34 formed in the outer sleeve 30.

The outer sleeve 30 constitutes an outer contour of the hydraulic oil control valve 10 and is disposed radially outward of the inner sleeve 40. The outer sleeve 30 includes a body portion 31, a valve fixing portion 32, a projecting portion 35, an enlarged diameter portion 36, a movement restricting portion 80, and a tool engaging portion 38. A shaft hole 34 is formed along the axial direction AD in the body portion 31 and the valve fixing portion 32. The shaft hole 34 is formed to penetrate the outer sleeve 30 in the axial direction AD.

The main body 31 has a cylindrical external shape, and is disposed in the through hole 136 of the blade 131 as shown in fig. 1. As shown in fig. 4, the main body portion 31 is formed with a plurality of outer retard angle ports 21 and a plurality of outer advance angle ports 22. The plurality of outer retard angle ports 21 are formed in a circumferential direction in a mutually aligned manner, and each communicate the outer peripheral surface of the body portion 31 with the shaft hole 34. The plurality of outer advance angle ports 22 are formed on the solenoid 160 side of the outer retard angle ports 21 in the axial direction AD. The plurality of outer advance ports 22 are formed in a circumferential direction in a mutually aligned manner, and communicate the outer circumferential surface of the main body portion 31 with the shaft hole 34.

The valve fixing portion 32 has a cylindrical external shape and is formed to be continuous with the body portion 31 in the axial direction AD. The valve fixing portion 32 is formed to have substantially the same diameter as the body portion 31, and is inserted into the shaft fixing portion 323 of the camshaft 320 as shown in fig. 1. The valve fixing portion 32 is formed with a male screw portion 33. The male screw portion 33 is screwed to a female screw portion 324 formed in the shaft fixing portion 323. The outer sleeve 30 is fixed to the end 321 of the camshaft 320 by being applied with an axial force in the axial direction AD toward the camshaft 320 by fastening the male screw portion 33 and the female screw portion 324. By applying the axial force, the displacement of the hydraulic oil control valve 10 from the end 321 of the camshaft 320 due to the eccentric force of the camshaft 320 generated by pressing the intake valve 330 can be suppressed, and the leakage of the hydraulic oil can be suppressed.

The protruding portion 35 is formed to protrude radially outward from the main body portion 31. As shown in fig. 1, the protruding portion 35 sandwiches the vane rotor 130 in the axial direction AD between the protruding portion and the end 321 of the camshaft 320.

As shown in fig. 3, an enlarged diameter portion 36 is formed at the end of the body portion 31 on the solenoid 160 side. The enlarged diameter portion 36 is formed to have an inner diameter larger than the other portion of the body portion 31. A flange portion 46 of the inner sleeve 40 described later is disposed in the enlarged diameter portion 36.

The movement restricting portion 80 is formed as a radial step formed by the enlarged diameter portion 36 on the inner circumferential surface of the outer sleeve 30. The movement restricting portion 80 sandwiches a flange portion 46 of the inner socket 40, which will be described later, between the fixing member 70 and the movement restricting portion in the axial direction AD. Thereby, the movement restricting portion 80 restricts the movement of the inner sleeve 40 in the axial direction AD in the direction away from the electromagnetic portion 162 of the solenoid 160, that is, toward the camshaft 320 side.

The tool engagement portion 38 is formed on the solenoid 160 side of the protrusion 35 in the axial direction AD. The tool engagement portion 38 is configured to be engageable with a tool such as a socket head cap, not shown, and is used to fasten and fix the hydraulic oil control valve 10 including the outer sleeve 30 to the end portion 321 of the camshaft 320.

The inner sleeve 40 includes a cylindrical portion 41, a bottom portion 42, a plurality of retarded-angle-side projecting walls 43, a plurality of advanced-angle-side projecting walls 44, a closing wall 45, a flange portion 46, a stopper 49, and a filter fixing portion 242, a support portion 244, and a filter stopper 246, which will be described later.

The cylindrical portion 41 has a substantially cylindrical external shape, and is located radially inward of the outer sleeve 30 over the body portion 31 and the valve fixing portion 32 of the outer sleeve 30. As shown in fig. 3 and 4, the cylinder 41 is formed with a retard-angle-side supply port SP1, an advance-angle-side supply port SP2, and a recirculation port 47, respectively. The retard-side supply port SP1 is formed closer to the bottom portion 42 than the retard-side wall 43 in the axial direction AD, and communicates the outer peripheral surface and the inner peripheral surface of the tube portion 41. In the present embodiment, the plurality of retard-angle-side supply ports SP1 are formed in a row on a half circumference in the circumferential direction, but may be formed on the entire circumference or may be single. The advance side supply port SP2 is formed closer to the solenoid 160 than the advance side projecting wall 44 in the axial direction AD, and communicates the outer peripheral surface and the inner peripheral surface of the tube portion 41. In the present embodiment, the advance angle side supply port SP2 is formed in a plurality of rows in a half circumferential circumference, but may be formed in the entire circumferential circumference or may be formed in a single row. The retard-side supply port SP1 and the advance-side supply port SP2 communicate with the shaft hole portion 322 of the camshaft 320 shown in fig. 1, respectively. As shown in fig. 3 and 4, the recirculation port 47 is formed between the retarded side wall 43 and the advanced side wall 44 in the axial direction AD, and communicates the outer peripheral surface and the inner peripheral surface of the cylindrical portion 41. The recirculation port 47 communicates with the retard-angle-side supply port SP1 and the advance-angle-side supply port SP2, respectively. Specifically, the recirculation port 47 communicates with the supply ports SP1, SP2 through a space between the retarded side projecting walls 43 and a space between the advanced side projecting walls 44, which are adjacent to each other in the circumferential direction, as a space between the inner peripheral surface of the main body portion 31 of the outer sleeve 30 and the outer peripheral surface of the cylindrical portion 41 of the inner sleeve 40. Therefore, the recirculation port 47 functions as a recirculation mechanism for returning the hydraulic oil discharged from the retard chamber 141 and the advance chamber 142 to the supply side. In the present embodiment, the recirculation port 47 is formed in plural numbers in the circumferential direction, but may be formed in a single number. The operation of the valve timing adjusting apparatus 100 including the switching operation of the oil passage due to the sliding of the valve body 50 will be described later.

As shown in fig. 3, the bottom portion 42 is formed integrally with the cylindrical portion 41, and closes an inner sleeve end 248 on the opposite side of the solenoid 160 in the axial direction AD of the cylindrical portion 41. One end of the spring 60 abuts the bottom 42.

As shown in fig. 4, the plurality of retarded angle side walls 43 are formed in a circumferential direction so as to protrude radially outward from the cylindrical portion 41. The retarded angle side projecting walls 43 adjacent to each other in the circumferential direction communicate with the supply hole 328, and the working oil supplied from the working oil supply source 350 shown in fig. 1 flows therethrough. As shown in fig. 3 and 4, each of the retard angle side walls 43 has an inner retard angle port 23 formed therein. Each of the inner retard angle ports 23 communicates the outer peripheral surface and the inner peripheral surface of the retard angle side wall 43, respectively. As shown in fig. 3, each of the inner retard angle ports 23 communicates with each of the outer retard angle ports 21 formed in the outer sleeve 30, respectively. The axis of the inner retard angle port 23 is offset in the axial direction AD with respect to the axis of the outer retard angle port 21.

As shown in fig. 4, each of the advanced angle side protruding walls 44 is formed on the solenoid 160 side of the retarded angle side protruding wall 43 in the axial direction AD. The plurality of advanced angle side protruding walls 44 are formed in a circumferential direction so as to protrude radially outward from the cylindrical portion 41. The advanced side projecting walls 44 adjacent to each other in the circumferential direction communicate with the supply hole 328, and the working oil supplied from the working oil supply source 350 shown in fig. 1 flows therethrough. As shown in fig. 3 and 4, an inner advance angle port 24 is formed in each advance angle side projection wall 44. Each of the inner advance ports 24 communicates the outer peripheral surface and the inner peripheral surface of the advance side projecting wall 44. As shown in fig. 3, each of the inner advance angle ports 24 communicates with each of the outer advance angle ports 22 formed in the outer sleeve 30. The axis of the inner advance angle port 24 is offset in the axial direction AD with respect to the axis of the outer advance angle port 22.

The closing wall 45 is formed to protrude radially outward over the entire circumference of the cylindrical portion 41 on the solenoid 160 side of the advance angle side supply port SP2 in the axial direction AD. The closing wall 45 seals the inner peripheral surface of the body portion 31 of the outer sleeve 30 and the outer peripheral surface of the cylindrical portion 41 of the inner sleeve 40, thereby suppressing leakage of the working oil flowing through the working oil supply passage 25, which will be described later, to the solenoid 160 side. The outer diameter of the blocking wall 45 is formed substantially the same as the outer diameters of the retarded side wall 43 and the advanced side wall 44.

The flange portion 46 is formed at the end of the inner sleeve 40 on the solenoid 160 side so as to protrude radially outward over the entire circumference of the cylindrical portion 41. The flange portion 46 is disposed at the enlarged diameter portion 36 of the outer sleeve 30. As shown in fig. 4, a plurality of fitting portions 48 are formed in the flange portion 46. The plurality of fitting portions 48 are formed to be arranged in the circumferential direction on the outer edge portion of the flange portion 46. In the present embodiment, each fitting portion 48 is formed by cutting the outer edge portion of the flange portion 46 linearly, but is not limited to a linear shape, and may be formed in a curved shape. Each fitting portion 48 is fitted to each fitting protrusion 73 of the fixing member 70 described later.

The stopper 49 shown in fig. 3 is formed at an end portion on the camshaft 320 side as an end portion in the axial direction AD of the inner sleeve 40. The stopper 49 is formed so as to have a smaller inner diameter than the other portion of the cylinder portion 41, and thereby can be brought into contact with the end portion of the valve body 50 on the camshaft 320 side. The stopper 49 defines a sliding limit of the valve element 50 in a direction away from the solenoid portion 162 of the solenoid 160.

The radial space formed between the shaft hole 34 of the outer sleeve 30 and the inner sleeve 40 functions as a hydraulic oil supply passage 25 that communicates with the hydraulic oil supply source 350 in a state where the outer sleeve 30 is fixed to the end 321 of the camshaft 320. The hydraulic oil supply passage 25 communicates with the shaft hole 322 of the camshaft 320 shown in fig. 1, and guides the hydraulic oil supplied from the hydraulic oil supply source 350 to the retard-side supply port SP1 and the advance-side supply port SP 2. A filter member 200 is disposed in the hydraulic oil supply passage 25. A description about the configuration of the filter member 200 will be described later. As shown in fig. 3, the outer retard angle port 21 and the inner retard angle port 23 constitute a retard angle port 27, and communicate with the retard angle chamber 141 via a retard angle oil passage 137 shown in fig. 2. As shown in fig. 3, the outer advance angle port 22 and the inner advance angle port 24 constitute an advance angle port 28, and communicate with an advance angle chamber 142 via an advance angle oil passage 138 shown in fig. 2.

As shown in fig. 3, at least a portion of the outer sleeve 30 and the inner sleeve 40 in the axial direction AD is sealed to suppress leakage of the working oil. More specifically, the retard side wall 43 seals between the retard side supply port SP1 and the recirculation port 47 and the retard port 27, and the advance side wall 44 seals between the advance side supply port SP2 and the recirculation port 47 and the advance port 28. Further, the hydraulic oil supply passage 25 and the outside of the hydraulic oil control valve 10 are sealed by the closing wall 45. That is, the range from the retarded angle side projecting wall 43 to the closing wall 45 in the axial direction AD is set as the sealing range SA. In the present embodiment, the inner diameter of the body portion 31 of the outer sleeve 30 is configured to be substantially constant within the sealing range SA.

The valve element 50 is disposed radially inward of the inner sleeve 40. The spool 50 is driven by a solenoid 160 disposed in contact with one end thereof, and slides in the axial direction AD. The valve body 50 includes a valve body portion 51, a valve body bottom portion 52, and a spring receiving portion 56. Further, a shaft hole is formed in the valve body 50 along the axial direction AD. The shaft hole constitutes a part of an oil discharge passage 53 described later. Further, the valve body 50 is formed with a drain inflow portion 54 and a drain outflow portion 55 which communicate with the shaft holes, respectively.

The valve body 51 has a substantially cylindrical external shape. On the outer peripheral surface of the valve body tube portion 51, the retard side seal portion 57, the advance side seal portion 58, and the lock portion 59 are arranged in this order from the camshaft 320 side in the axial direction AD, and are formed so as to protrude outward in the radial direction and extend over the entire periphery. The retard-side seal portion 57 blocks communication between the recirculation port 47 and the retard angle port 27 in a state where the spool 50 is closest to the solenoid portion 162 of the solenoid 160 as shown in fig. 3, and blocks communication between the retard-side supply port SP1 and the retard angle port 27 in a state where the spool 50 is farthest from the solenoid portion 162 as shown in fig. 8. The advance side seal portion 58 blocks communication between the advance side supply port SP2 and the advance port 28 in a state where the valve body 50 is closest to the solenoid portion 162 as shown in fig. 3, and blocks communication between the recirculation port 47 and the advance port 28 in a state where the valve body 50 is farthest from the solenoid portion 162 as shown in fig. 8. "cut off communication" corresponds to sealing. At a portion where the sealability is required, a gap in a radial direction between the inner sleeve 40 and the valve core 50 is minimized. As shown in fig. 3, the engagement portion 59 abuts against the fixing member 70 to define a sliding limit of the valve body 50 in a direction approaching the solenoid portion 162 of the solenoid 160.

The valve body bottom portion 52 is formed integrally with the valve body portion 51 and closes the end portion of the valve body portion 51 on the solenoid 160 side. The valve body bottom portion 52 is configured to be able to protrude further toward the solenoid 160 than the sleeve 20 in the axial direction AD. The valve element bottom portion 52 functions as a base end portion of the valve element 50.

The space surrounded by the valve body portion 51, the valve body bottom portion 52, the body portion 41 of the inner sleeve 40, and the bottom portion 42 functions as an oil drain passage 53. Therefore, the interior of the valve body 50 functions as at least a part of the oil discharge passage 53. The hydraulic oil discharged from the retard chamber 141 and the advance chamber 142 flows through the oil discharge passage 53.

The drain inflow portion 54 is formed between the retard-angle-side seal portion 57 and the advance-angle-side seal portion 58 in the axial direction AD in the valve body cylinder portion 51. The drain inflow portion 54 communicates the outer peripheral surface and the inner peripheral surface of the valve body portion 51. The drain inflow portion 54 guides the hydraulic oil discharged from the retard chamber 141 and the advance chamber 142 to the drain oil passage 53. The drain inflow portion 54 communicates with the supply ports SP1 and SP2 via the recirculation port 47.

The drain outlet 55 is formed to open radially outward at the valve body bottom 52, which is one end of the valve body 50. The drain outflow portion 55 discharges the hydraulic oil in the drain oil passage 53 to the outside of the hydraulic oil control valve 10. As shown in fig. 1, the working oil discharged from the drain outflow portion 55 is collected in an oil pan 352.

As shown in fig. 3, the end portion of the spring receiving portion 56 on the camshaft 320 side of the valve body portion 51 is formed to have an inner diameter larger than the other portions of the valve body portion 51. The other end of the spring 60 abuts against the spring receiving portion 56.

In the present embodiment, the outer sleeve 30 and the valve body 50 are formed of iron, and the inner sleeve 40 is formed of aluminum. The material is not limited to these materials, and may be formed of any metal material, resin material, or the like.

The spring 60 is formed of a compression coil spring, and its ends are disposed so as to abut against the bottom portion 42 of the inner sleeve 40 and the spring receiving portion 56 of the valve element 50, respectively. The spring 60 biases the spool 50 toward the solenoid 160 in the axial direction AD.

The fixing member 70 is fixed to the end of the outer sleeve 30 on the solenoid 160 side. As shown in fig. 4, the fixing member 70 has a flat plate portion 71 and a plurality of fitting projection portions 73.

The flat plate portion 71 is formed in a flat plate shape along the radial direction. The flat plate portion 71 is not limited to the radial direction, and may be formed along a direction intersecting the axial direction AD. An opening 72 is formed substantially at the center of the flat plate portion 71. As shown in fig. 3, a valve element bottom portion 52 as one end of the valve element 50 is inserted into the opening 72.

As shown in fig. 4, the plurality of fitting projections 73 project from the flat plate portion 71 in the axial direction AD and are arranged in the circumferential direction. The fitting projection 73 may be formed to project in any direction intersecting the radial direction, not limited to the axial direction AD. The fitting projections 73 are fitted to the fitting portions 48 of the inner sleeve 40.

As shown in fig. 3, after the valve body 50 is inserted into the inner sleeve 40 and assembled so that the fitting projection 73 fits into the fitting portion 48, the fixing member 70 is fixed to the outer sleeve 30 by caulking. The outer edge portion of the end surface of the fixing member 70 on the solenoid 160 side functions as a caulked portion that is caulked and fixed to the outer sleeve 30.

The fixing member 70 is fixed to the outer sleeve 30 in a state where the fitting projection 73 is fitted to the fitting portion 48, thereby restricting the inner sleeve 40 from rotating in the circumferential direction with respect to the outer sleeve 30. Further, the fixation member 70 is fixed to the outer sleeve 30, and thereby the inner sleeve 40 and the valve body 50 are restricted from coming off from the outer sleeve 30 toward the solenoid 160 in the axial direction AD.

The check valve 90 suppresses the reverse flow of the working oil. The check valve 90 is constituted to include 2 supply check valves 91 and a recirculation check valve 92. As shown in fig. 4, each of the supply check valve 91 and the recirculation check valve 92 is formed by annularly winding a band-shaped thin plate, and is elastically deformed in the radial direction. As shown in fig. 3, each supply check valve 91 is disposed so as to abut against the inner peripheral surface of the tube portion 41 at a position corresponding to the retard-side supply port SP1 and the advance-side supply port SP 2. The supply check valves 91 receive the pressure of the hydraulic oil from the radial outside, and the overlapping portion of the band-shaped thin plates is enlarged and reduced in the radial direction. The recirculation check valve 92 is disposed in contact with the outer peripheral surface of the cylinder portion 41 at a position corresponding to the recirculation port 47. The recirculation check valve 92 receives the pressure of the working oil from the radially inner side, and thus the overlapping portion of the band-shaped thin plates becomes small and expands in the radial direction.

The filter member 200 is disposed in the hydraulic oil supply passage 25, and traps foreign matter contained in the hydraulic oil supplied from the hydraulic oil supply source 350. The filter member 200 is formed of metal and has a ring-like external shape as shown in fig. 5. As shown in fig. 6 and 7, the filter member 200 has a cross-sectional view shape substantially like japanese コ in a cross section along the radial direction. The filter member 200 includes a fixing portion 210, an outer edge portion 220, and a catching portion 230.

As shown in fig. 5 to 7, the fixing portion 210 constitutes an inner peripheral surface of the filter member 200 and is formed along the axial direction AD. The fixing portion 210 is fixed to the inner sleeve 40 as described later. The outer edge portion 220 constitutes the outer peripheral surface of the filter member 200 and is formed along the axial direction AD. The outer edge portion 220 faces the outer sleeve 30 and is not fixed to the outer sleeve 30. Outer rim portion 220 has a filter end 222. The filter end 222 is located on the side of the outer edge 220 closest to the solenoid 160 in the axial direction AD, that is, closest to the cam shaft 320. The catching portion 230 is connected to the fixing portion 210 and the outer edge portion 220, respectively, and is formed in a radial direction. The catching portion 230 is formed at a position closer to the solenoid 160 than the filter end portion 222 in the axial direction AD. The catching part 230 is formed with a plurality of small through holes and configured to catch foreign matter contained in the hydraulic oil. In the present embodiment, the through-hole is formed by etching, but may be formed by any method such as pressing.

As shown in fig. 3, the filter member 200 is disposed in the hydraulic oil supply passage 25 at a position overlapping the valve element 50 and the spring 60, which are internal members disposed inside the inner sleeve 40 when viewed in the radial direction. The arrangement of the filter member 200 is described in detail below with reference to fig. 7.

The filter fixing portion 242, the support portion 244, and the filter stopper 246 are formed on the outer peripheral surface of the cylindrical portion 41 of the inner sleeve 40 over the entire circumference. The outer diameter of the filter fixing portion 242 is formed substantially the same as the inner diameter of the fixing portion 210 of the filter member 200. Thereby, the filter fixing portion 242 and the fixing portion 210 are press-fitted and fixed. Alternatively, the fixing may be performed by using an adhesive or the like instead of press-fitting. The support portion 244 is formed on the solenoid 160 side in the axial direction AD relative to the filter fixing portion 242. The outer diameter of the support portion 244 is formed larger than the outer diameter of the filter fixing portion 242. Thereby, the support portion 244 supports the filter member 200. The portion of the filter member 200 that is supported by the support 244 by contacting the support 244 is also referred to as a supported portion 232. In the present embodiment, the supported portion 232 is located at the catching portion 230. The filter stopper 246 is formed closer to the camshaft 320 than the filter fixing portion 242 in the axial direction AD. The outer diameter of the filter stopper 246 is formed to be slightly larger than the outer diameter of the filter fixing portion 242. The position in the axial direction AD of the filter member 200 is determined by the support portion 244 and the filter stopper 246.

As shown in fig. 3, the space functioning as the hydraulic oil supply passage 25 is formed over the entire circumference of the portion where the filter member 200 is disposed. The annular filter member 200 is inserted into the space from the inner sleeve end 248 side and assembled. Therefore, the outer diameter of the inner sleeve end 248 is formed smaller than the inner diameter of the fixing portion 210 of the filter member 200.

As shown in fig. 7, a clearance CL in the radial direction is formed between the outer sleeve 30 and the outer edge portion 220. The clearance CL is formed to be smaller than the size of foreign matter to be captured contained in the hydraulic oil. In other words, the size of the clearance CL is set smaller than the size of a plurality of small through holes formed in the trap part 230, which is the mesh size (pore diameter) of the filter member 200. In addition, a linear dimension L1 from the filter end 222 to the supported portion 232 in a cross section along the axial direction AD is formed larger than a dimension L2 in the radial direction between the outer sleeve 30 and the support portion 244.

The hydraulic oil in the hydraulic oil supply passage 25 flows in the axial direction AD from the crankshaft 310 side to the solenoid 160 side as indicated by the hollow arrow in fig. 7. The filter member 200 is sometimes deformed by the pressure of the supplied working oil. More specifically, the outer edge portion 220 may be deformed toward the solenoid 160 in the axial direction AD, which is the downstream side of the supplied hydraulic oil, with the support portion 244 as a fulcrum. However, since the linear dimension L1 from the filter end 222 to the supported portion 232 is formed larger than the dimension L2 in the radial direction between the outer sleeve 30 and the supporting portion 244, in the case where the outer edge portion 220 side of the filter member 200 deforms toward the downstream side of the supplied working oil, the filter end 222 collides with the shaft hole 34. Therefore, the radial clearance CL between the shaft hole 34 of the outer sleeve 30 and the outer edge 220 can be prevented from being enlarged, and foreign matter can be prevented from passing through the clearance CL. Thus, a performance decrease of the filter member 200 can be suppressed.

In the present embodiment, the crankshaft 310 corresponds to a lower concept of the drive shaft in the present disclosure, the camshaft 320 corresponds to a lower concept of the driven shaft in the present disclosure, and the intake valve 330 corresponds to a lower concept of the valve in the present disclosure. In addition, the solenoid 160 corresponds to a subordinate concept of the actuator in the present disclosure. The valve element 50 and the spring 60 correspond to a lower concept of an internal member disposed inside the inner sleeve in the present disclosure, the inner sleeve 40 corresponds to a lower concept of a first sleeve in the present disclosure, and the outer sleeve 30 corresponds to a lower concept of a second sleeve in the present disclosure.

A-2. operation of the valve timing adjusting device:

as shown in fig. 1, the hydraulic oil supplied from the hydraulic oil supply source 350 to the supply hole 326 flows through the shaft hole 322 to the hydraulic oil supply passage 25. In a state where the solenoid 160 is not energized and the spool 50 is closest to the solenoid portion 162 of the solenoid 160 as in the state shown in fig. 3, the retard angle port 27 communicates with the retard side supply port SP 1. Accordingly, the hydraulic oil in the hydraulic oil supply passage 25 is supplied to the retard chamber 141, the vane rotor 130 rotates relative to the housing 120 in the retard direction, and the relative rotational phase of the camshaft 320 with respect to the crankshaft 310 changes toward the retard side. In this state, the advance port 28 communicates with the recirculation port 47, not the advance side supply port SP 2. Thereby, the hydraulic oil discharged from the advance chamber 142 is returned to the retard-side supply port SP1 via the recirculation port 47 and recirculated. Part of the hydraulic oil discharged from the advance chambers 142 flows into the drain oil passage 53 through the drain inflow portion 54, passes through the drain outflow portion 55, and returns to the oil pan 352.

As shown in fig. 8, in a state where the solenoid 160 is energized and the spool 50 is farthest from the solenoid portion 162 of the solenoid 160, that is, in a state where the spool 50 abuts on the stopper 49, the advance port 28 communicates with the advance-side supply port SP 2. Accordingly, the hydraulic oil in the hydraulic oil supply passage 25 is supplied to the advance chamber 142, the vane rotor 130 rotates relative to the housing 120 in the advance direction, and the relative rotational phase of the camshaft 320 with respect to the crankshaft 310 changes to the advance side. In this state, the retard angle port 27 communicates with the recirculation port 47, not the retard side supply port SP 1. Thereby, the hydraulic oil discharged from the retard chamber 141 is returned to the advance side supply port SP2 via the recirculation port 47 and recirculated. A part of the hydraulic oil discharged from the retard chamber 141 flows into the drain oil passage 53 through the drain inflow portion 54, passes through the drain outflow portion 55, and returns to the oil pan 352.

In a state in which the solenoid 160 is energized and the spool 50 is positioned substantially at the center of the sliding range as shown in fig. 9, the retard port 27 communicates with the retard-side supply port SP1, and the advance port 28 communicates with the advance-side supply port SP 2. Accordingly, the hydraulic oil in the hydraulic oil supply passage 25 is supplied to both the retarded angle chamber 141 and the advanced angle chamber 142, and the relative rotation of the vane rotor 130 with respect to the housing 120 is suppressed, and the relative rotational phase of the camshaft 320 with respect to the crankshaft 310 is maintained.

Thus, the spool 50 slides in the axial direction AD by energization of the solenoid 160. The sliding range 520 of the valve body 50 is set to a range from a position where the valve body 50 abuts against the fixing member 70 to a position where the valve body abuts against the stopper 49.

The hydraulic oil supplied to the retarded angle chamber 141 or the advanced angle chamber 142 flows into the housing hole 132 through the retarded angle chamber-side pin control oil passage 133 or the advanced angle chamber-side pin control oil passage 134. Therefore, a sufficient hydraulic pressure is applied to the retarded angle chamber 141 or the advanced angle chamber 142, and if the lock pin 150 is disengaged from the fitting recess 128 against the biasing force of the spring 151 by the hydraulic oil flowing into the housing hole 132, the relative rotation of the vane rotor 130 with respect to the housing 120 is permitted.

When the relative rotation phase of the camshaft 320 is advanced relative to the target value, the valve timing adjusting apparatus 100 relatively rotates the vane rotor 130 in the retarded direction relative to the housing 120 by reducing the amount of current supplied to the solenoid 160. Thereby, the relative rotational phase of the camshaft 320 with respect to the crankshaft 310 changes to the retard side, and the valve timing is retarded. In the valve timing adjusting apparatus 100, when the relative rotation phase of the camshaft 320 is on the retarded side with respect to the target value, the amount of current supplied to the solenoid 160 is made relatively large, and the vane rotor 130 is rotated relative to the housing 120 in the advanced direction. Thereby, the relative rotational phase of the camshaft 320 with respect to the crankshaft 310 is changed to the advanced angle side, and the valve timing is advanced. When the relative rotation phase of the camshaft 320 coincides with the target value, the valve timing adjusting apparatus 100 suppresses the relative rotation of the vane rotor 130 with respect to the housing 120 by setting the amount of current supplied to the solenoid 160 to a medium level. Thereby, the relative rotational phase of the camshaft 320 with respect to the crankshaft 310 is maintained, and the valve timing is maintained.

According to the hydraulic control valve 10 provided in the valve timing adjusting apparatus 100 according to the first embodiment described above, the filter member 200 is disposed in the hydraulic oil supply passage 25 at a position overlapping the valve element 50 and the spring 60, which are internal members disposed inside the inner sleeve 40 when viewed in the radial direction. Therefore, the size of the inner sleeve 40 along the axial direction AD can be suppressed from being increased by the arrangement of the filter member 200.

Further, since the increase in the dimension of the inner sleeve 40 in the axial direction AD can be suppressed, the increase in the dimension of the outer sleeve 30 in the axial direction AD can be suppressed, and the degree of freedom in designing the structure of the outer sleeve 30 on the camshaft 320 side, that is, on the valve fixing portion 32 side can be suppressed from decreasing. Therefore, the length of the outer sleeve 30, the shape of the valve fixing portion 32 side, and the like can be changed without affecting other members. Further, when the outer sleeve 30 is designed to have a configuration closer to the camshaft 320 than the mounting position of the filter member 200 in the axial direction AD, the mounting position of the filter member 200 does not need to be changed, and therefore, an increase in the manufacturing cost of the hydraulic control valve 10 can be suppressed.

Further, since the space functioning as the hydraulic oil supply passage 25 is formed over the entire circumference of the portion where the filter member 200 is disposed, the annular filter member 200 can be disposed. Therefore, the filter member 200 can be prevented from being complicated in structure, and an increase in cost required for manufacturing the filter member 200 can be prevented.

Further, since the outer diameter of the inner sleeve end 248 is formed smaller than the inner diameter of the fixing portion 210 of the filter member 200, the filter member 200 can be assembled by being inserted from the inner sleeve end 248 side. Therefore, the filter member 200 and the inner sleeve 40 can be prevented from becoming complicated in structure for assembly, the assembly process can be simplified, and an increase in cost required for manufacturing the filter member 200 and the inner sleeve 40 can be prevented.

The fixing portion 210 of the filter member 200 is fixed to the filter fixing portion 242 of the inner sleeve 40, and the outer edge portion 220 of the filter member 200 is not fixed to the axial hole 34 of the outer sleeve 30. Therefore, a gap CL in the radial direction can be formed between the outer sleeve 30 and the outer edge portion 220, and the axial misalignment of the outer sleeve 30 and the inner sleeve 40 can be absorbed by the gap CL. Therefore, the dimensional accuracy of the filter member 200 can be relaxed, and an increase in cost required for manufacturing the filter member 200 can be suppressed. Further, the size of the clearance CL is set smaller than the size of the plurality of small through holes formed in the trap part 230 of the filter member 200, so that the deterioration of the foreign matter trapping performance of the filter member 200 can be suppressed.

Further, a support portion 244 is formed on the outer peripheral surface of the inner sleeve 40, and the filter member 200 is fixed to the inner sleeve 40. Therefore, the support portions 244 can be easily formed on the outer peripheral surface of the inner sleeve 40, as compared with a structure in which the support portions are formed on the inner peripheral surface of the outer sleeve 30 and the filter member 200 is fixed to the inner peripheral surface of the outer sleeve 30. Further, since the inner sleeve 40 and the filter member 200 are press-fitted and fixed, the assembly process can be prevented from being complicated as compared with a structure in which fixing is performed using an adhesive member or the like.

Further, since the linear dimension L1 from the filter end 222 to the supported portion 232 is formed to be larger than the dimension L2 in the radial direction between the outer sleeve 30 and the supporting portion 244, the filter end 222 collides with the shaft hole 34 when the filter member 200 is deformed by the oil pressure of the hydraulic oil. Therefore, the radial clearance CL between the shaft hole 34 of the outer sleeve 30 and the outer edge 220 can be prevented from being enlarged, and foreign matter can be prevented from passing through the clearance CL. Thus, a performance decrease of the filter member 200 can be suppressed.

Further, since the sleeve 20 has a double structure including the outer sleeve 30 and the inner sleeve 40, the working oil supply passage 25 can be easily realized by the radial space between the outer sleeve 30 and the inner sleeve 40. Therefore, the application of hydraulic pressure to the valve body 50 for supplying the hydraulic oil can be suppressed, and deterioration in the sliding property of the valve body 50 can be suppressed. Further, a complicated structure such as the ports SP1, SP2, 23, 24, and 47, and a structure for communicating the retard-angle-side supply port SP1 with the advance-angle-side supply port SP2 can be easily formed in the inner sleeve 40. Therefore, workability of the sleeve 20 can be improved, and complication of the manufacturing process of the sleeve 20 can be suppressed. Further, since the workability can be improved, the degree of freedom in designing the ports SP1, SP2, 27, 28, 47, and the like can be improved, and mountability of the hydraulic oil control valve 10 and the valve timing adjusting apparatus 100 can be improved.

B. Second embodiment:

the hydraulic oil control valve 10a according to the second embodiment shown in fig. 10 differs from the hydraulic oil control valve 10 according to the first embodiment in that an outer sleeve 30a is provided instead of the outer sleeve 30. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted.

In the outer sleeve 30a provided in the hydraulic oil control valve 10a according to the second embodiment, a plurality of supply holes 328 are formed in the axial direction AD on the camshaft 320 side of the position where the filter member 200 is disposed. The plurality of supply holes 328 are formed in a circumferential direction in a row, and communicate the outer circumferential surface of the body portion 31 with the shaft hole 34. The working oil is supplied to each supply hole 328 from a working oil supply source 350 shown in fig. 1.

According to the hydraulic oil control valve 10a of the second embodiment described above, the same effects as those of the hydraulic oil control valve 10 of the first embodiment are obtained.

C. The third embodiment:

the hydraulic oil control valve 10b according to the third embodiment shown in fig. 11 differs from the hydraulic oil control valve 10 according to the first embodiment in that an outer sleeve 30b is provided instead of the outer sleeve 30. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted.

The outer sleeve 30b included in the hydraulic oil control valve 10b according to the third embodiment includes a valve fixing portion 32b instead of the valve fixing portion 32, and a reduced diameter portion 327 that connects between the body portion 31 and the valve fixing portion 32b in the axial direction AD.

The valve fixing portion 32b is formed larger in size in the axial direction AD than the valve fixing portion 32 of the first embodiment. The valve fixing portion 32b is formed to have a smaller outer diameter than the body portion 31. A supply hole 328b is formed in the valve fixing portion 32 b. The supply hole 328b communicates the outer peripheral surface of the valve fixing portion 32b with the shaft hole 34 b. The supply hole 328b is supplied with working oil from a working oil supply source 350 shown in fig. 1. The reduced diameter portion 327 is formed to have a smaller inner diameter than the body portion 31. More specifically, the reduced diameter portion 327 is formed so as to gradually decrease in inner diameter from the solenoid 160 side toward the camshaft 320 side.

According to the hydraulic oil control valve 10b of the third embodiment described above, the same effects as those of the hydraulic oil control valve 10 of the first embodiment are obtained.

D. Fourth embodiment:

the hydraulic oil control valve 10c according to the fourth embodiment shown in fig. 12 differs from the hydraulic oil control valve 10 according to the first embodiment in that an outer sleeve 30c is provided instead of the outer sleeve 30. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted.

The outer sleeve 30c provided in the hydraulic oil control valve 10c according to the fourth embodiment is formed to have a smaller dimension in the axial direction AD than the outer sleeve 30 according to the first embodiment. Therefore, the inner sleeve end 248 protrudes further toward the camshaft 320 than the outer sleeve 30c in the axial direction AD.

According to the hydraulic oil control valve 10c of the fourth embodiment described above, the same effects as those of the hydraulic oil control valve 10 of the first embodiment are obtained. In addition, since the inner sleeve end 248 protrudes further toward the camshaft 320 than the outer sleeve 30c in the axial direction AD, the outer sleeve 30 can be prevented from being increased in size along the axial direction AD. Therefore, the size of the shaft hole 322 formed in the end 321 of the camshaft 320, that is, the shaft hole 322 having the shaft fixing portion 323 formed on the inner peripheral surface thereof for fixing the hydraulic oil control valve 10 can be prevented from increasing in the axial direction AD. Therefore, the increase in the length of the camshaft 320 can be suppressed, and the increase in the size of the internal combustion engine 300 including the solenoid 160 and the camshaft 320 in the axial direction AD can be suppressed. Further, since the outer sleeve 30 can be prevented from being increased in size along the axial direction AD, mountability of the hydraulic oil control valve 10 and the valve timing adjusting apparatus 100 can be improved.

E. Fifth embodiment:

the hydraulic oil control valve 10d according to the fifth embodiment shown in fig. 13 differs from the hydraulic oil control valve 10 according to the first embodiment in that a filter member 200d is provided in place of the filter member 200. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted. Fig. 13 shows a cross section along the radial direction of the same region as fig. 7.

The filter member 200d included in the hydraulic oil control valve 10d according to the fifth embodiment has an annular external shape and a substantially V-shaped cross-sectional view shape in a cross section along the radial direction. The filter member 200d has a fixing portion 210 and a catching portion 230 d. The catching portion 230d is connected to the fixing portion 210 and formed along a direction intersecting the axial direction AD. The catching portion 230d is located closer to the solenoid 160 in the axial direction AD as going radially inward. The catching portion 230d has a filter end 222 d. The filter end 222d constitutes an outer edge portion of the catching part 230d, and is located on the side of the catching part 230d that is the most opposite side to the solenoid 160 in the axial direction AD, that is, on the side of the cam shaft 320. The filter end 222d faces the outer sleeve 30.

According to the hydraulic oil control valve 10d of the fifth embodiment described above, the same effects as those of the hydraulic oil control valve 10 of the first embodiment are obtained. In addition, since the filter member 200d has a substantially V-shaped cross-sectional view shape in a cross section along the radial direction, the area of the trap portion 230d can be increased. Therefore, the pressure loss of the hydraulic oil flowing through the hydraulic oil supply passage 25 and passing through the trap portion 230d can be suppressed.

F. Sixth embodiment:

the hydraulic oil control valve 10e according to the sixth embodiment shown in fig. 14 differs from the hydraulic oil control valve 10 according to the first embodiment in that a filter member 200e is provided in place of the filter member 200. Since other configurations are the same as those of the first embodiment, the same reference numerals are given to the same configurations, and detailed description thereof will be omitted. Fig. 14 shows a cross section along the radial direction of the same region as fig. 7.

The filter member 200e included in the hydraulic oil control valve 10e according to the sixth embodiment has an annular external shape, and has a substantially I-shaped cross-sectional view shape in a cross section along the radial direction. The filter member 200e includes a fixing portion 210, an outer edge portion 220e, and a catching portion 230 e. The outer edge portion 220e is formed larger in dimension in the axial direction AD than the fixing portion 210. The catching portion 230e is formed in the radial direction so as to be continuous with substantially the center of the fixing portion 210 and substantially the center of the outer edge portion 220e in the axial direction AD, respectively.

In the present embodiment, the outer diameter of the support portion 244e is formed to be slightly smaller than the outer diameter of the support portion 244 of the first embodiment. The supported portion 232e of the filter member 200e is located at the end of the fixing portion 210 on the solenoid 160 side in the axial direction AD.

According to the hydraulic oil control valve 10e of the sixth embodiment described above, the same effects as those of the hydraulic oil control valve 10 of the first embodiment are obtained.

G. Other embodiments are as follows:

(1) in each of the above embodiments, the filter members 200, 200d, and 200e are disposed at positions overlapping the valve body 50 and the spring 60 when viewed in the radial direction in the hydraulic oil supply passage 25, but may be disposed at positions overlapping only the valve body 50 when viewed in the radial direction, or may be disposed at positions overlapping only the spring 60. For example, the check valve may be disposed at a position overlapping the supply check valve 91 disposed inside the inner sleeve 40 when viewed in the radial direction. That is, in general, the filter members 200, 200d, and 200e may be disposed in a radial space between the axial holes 34 and 34b of the outer sleeves 30 and 30a to 30c and the inner sleeve 40 at a position overlapping at least one of the inner members disposed inside the inner sleeve 40 when viewed in the radial direction. With this configuration, the same effects as those of the above embodiments are obtained.

(2) The structure of the filter members 200, 200d, and 200e in the above embodiments is always an example, and various modifications are possible. For example, the hydraulic oil supply passage 25 may have an appearance such as a C-shape instead of a ring shape. In the above-described embodiment, the radial space between the shaft holes 34, 34b of the outer sleeves 30, 30 a-30 c and the inner sleeve 40 may be formed over the entire circumference, or may be partially closed in the circumferential direction. For example, 2 filter elements formed in a semi-ring shape may be assembled to the outer peripheral surface of the inner sleeve 40 and then connected to each other. In the above manner, the outer diameter of the inner sleeve end 248 may be formed larger than the inner diameter of the filter member 200, 200d, 200 e. For example, the present invention may be formed of any material such as a resin material, not limited to a metal material, or may be formed of a material having elasticity. According to the above aspect, even when the filter members 200, 200d, 200e are fixed to both the outer peripheral surface of the inner socket 40 and the outer peripheral surfaces of the outer sleeves 30, 30a to 30c, the axial misalignment between the inner socket 40 and the outer sleeves 30, 30a to 30c can be absorbed. For example, the fixing portion 210 may be omitted. With such a configuration, the same effects as those of the above embodiments are obtained.

(3) In the above embodiments, the filter members 200, 200d, and 200e are fixed to the outer peripheral surface of the inner socket 40, but may be fixed to the inner peripheral surfaces of the outer sleeves 30 and 30a to 30c in addition to the inner socket 40, or may be fixed to the inner peripheral surfaces of the outer sleeves 30 and 30a to 30c instead of the inner socket 40. In the above-described embodiment, the outer edge portions 220, 220e function as fixing portions to be fixed to the filter fixing portions of the outer sleeves 30, 30a to 30c as the first sleeves. The radial clearances CL between the outer sleeves 30, 30a to 30c and the outer edge portions 220, 220e may be omitted, or radial clearances may be formed between the inner sleeve 40 as the second sleeve and the fixing portion 210. With such a configuration, the same effects as those of the above embodiments are obtained.

(4) In each of the above embodiments, the linear dimension L1 from the filter end 222 to the supported portions 232 and 232e is formed to be larger than the dimension L2 in the radial direction between the outer sleeves 30 and 30a to 30c and the supporting portions 244 and 244e, but may be formed to be equal to or smaller than the dimension L2. In each of the above embodiments, the support portions 244 and 244e and the stopper 246 are formed in the inner sleeve 40 to which the filter members 200, 200d, and 200e are fixed, but at least one of the support portions 244 and 244e and the stopper 246 may be omitted. With such a configuration, the same effects as those of the above embodiments are obtained.

(5) The configuration of the hydraulic oil control valves 10 and 10a to 10e in the above embodiments is always an example, and various modifications are possible. For example, a recirculation mechanism using the recirculation port 47 may also be omitted. For example, the male screw portion 33 and the female screw portion 324 may be fixed to the end 321 of the camshaft 320 by any fixing method such as welding. The solenoid 160 is not limited to the above, and may be driven by any actuator such as an electric motor or an air cylinder. With such a configuration, the same effects as those of the above embodiments are obtained.

(6) In each of the above embodiments, the valve timing adjusting apparatus 100 adjusts the valve timing of the intake valve 330 that is driven to open and close by the camshaft 320, but the valve timing of the exhaust valve 340 may be adjusted. The camshaft may be used by being fixed to an end 321 of a camshaft 320 as a driven shaft to which power is transmitted from a crankshaft 310 as a driving shaft via an intermediate shaft, or may be used by being fixed to one end of a driving shaft or a driven shaft provided in a dual-structured camshaft.

The present disclosure is not limited to the above embodiments, and can be implemented in various configurations without departing from the spirit thereof. For example, technical features in the embodiments corresponding to technical features in the embodiments described in the section of the summary of the invention may be appropriately exchanged and combined to solve a part or all of the technical problems described above or achieve a part or all of the effects described above. In addition, if this technical feature is not described as an essential technical feature in the present specification, it can be appropriately deleted.