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 2020-03-23 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、10b、10c、10e)具备套筒(20)、阀芯(50、50b、50e)、移动限制部(80、80b、80c)以及固定构件(70、70b、70d、70e、70f),套筒具有内套筒(40、40b、40c、40e)和外套筒(30、30a、30b、30c、30e),固定构件被固定于外套筒的致动器侧的端部,构成为能够限制内套筒相对于外套筒在周向上旋转、且能够分别限制内套筒和阀芯从外套筒在轴向上向致动器侧脱落。(The hydraulic control valve (10, 10a, 10b, 10c, 10e) disposed on a rotary shaft (AX) of a valve timing adjustment device (100) is provided with a sleeve (20) having inner sleeves (40, 40b, 40c, 40e) and outer sleeves (30, 30a, 30b, 30c, 30e), a movement restriction portion (80, 80b, 80c), and a fixing member (70, 70b, 70d, 70e, 70f) that is fixed to an actuator-side end portion of the outer sleeve, and is configured so as to be able to restrict rotation of the inner sleeve in the circumferential direction with respect to the outer sleeve and to restrict the inner sleeve and the valve element from coming off from the outer sleeve in the axial direction to the actuator side.)

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, 10a, 10b, 10c, 10e) that is used by a rotating shaft (AX) disposed in the valve timing adjustment device and that controls the flow of hydraulic oil supplied from a hydraulic oil supply source (350) is characterized by comprising:

a cylindrical sleeve (20);

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

a movement restricting unit (80, 80b, 80 c); and

a fixing member (70, 70b, 70d, 70e, 70f),

the sleeve has:

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

an outer sleeve (30, 30a, 30b, 30c, 30e) having a shaft hole (34) formed along the axial direction, the inner sleeve being inserted into at least a part of the shaft hole in the axial direction,

the movement restricting portion is configured to restrict movement of the inner sleeve in the axial direction toward a side opposite to the actuator side,

the fixing member is fixed to the actuator-side end portion of the outer sleeve, and is configured to be capable of restricting the inner sleeve from rotating in the circumferential direction with respect to the outer sleeve and to be capable of restricting the inner sleeve and the valve body from coming off from the outer sleeve in the axial direction toward the actuator side.

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

the inner sleeve further has a first abutting portion (CP1) capable of abutting against the fixing member and a second abutting portion (CP2) capable of abutting against the movement restricting portion,

gaps in the axial direction are formed at least one of between the fixing member and the first abutting portion and between the movement restricting portion and the second abutting portion.

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

the fixing member has a flat plate portion (71) formed in a flat plate shape intersecting the axial direction and fitting protrusions (73, 73b) formed to protrude from the flat plate portion in a direction intersecting the radial direction,

the inner sleeve has a fitting portion (48, 48b) that fits into the fitting protrusion at the actuator-side end portion.

4. The working oil control valve according to claim 3,

positioning portions (82, 82b) that abut against the fixing member in the axial direction are formed in the outer sleeve.

5. The working oil control valve according to claim 3 or 4,

a first engaging portion (78f) that restricts the fixing member from rotating in the circumferential direction with respect to the outer sleeve is formed on the fixing member,

the outer sleeve is formed with a second engaging portion that engages with the first engaging portion.

6. The working oil control valve according to any one of claims 3 to 5,

the fixing member further has caulking portions (74, 74d) for being caulked and fixed to the outer sleeve at an end surface on the actuator side.

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

the swaged portion is formed with irregularities (75) in a direction intersecting the radial direction.

8. The working oil control valve according to claim 6 or 7,

the outer sleeve has tool engagement portions (38, 38e) for fixing the outer sleeve to an end of the one shaft, the tool engagement portions being formed at the actuator-side end of the outer sleeve and having the circumferential crest (39) formed to have the radially thick portion,

the riveted portion is riveted at a position corresponding to the apex portion in the circumferential direction.

9. The working oil control valve according to any one of claims 3 to 8,

the outer sleeve has a diameter-enlarged portion (36) with an enlarged inner diameter at the end portion on the actuator side,

the inner sleeve has a flange portion (45) formed toward the outside in the radial direction at an end portion on the actuator side and arranged at the diameter-enlarged portion,

the fitting portion is formed in the flange portion.

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

the fixing member is formed of a rod-shaped pin and is disposed so as to penetrate the outer sleeve and the inner sleeve.

11. The working oil control valve according to any one of claims 1 to 10,

the inner diameter of the outer sleeve is fixed in the axial direction within a range (SA) in which the inner sleeve and the outer sleeve are sealed.

12. The working oil control valve according to any one of claims 1 to 11,

the outer sleeve has a non-arrangement portion (37, 37a) where the inner sleeve is not arranged on the radial inner side,

the inner diameter of the non-arrangement portion is formed larger than the inner diameter of the inner sleeve,

the shaft hole is formed to penetrate the outer sleeve in the axial direction.

13. The working oil control valve according to any one of claims 1 to 12,

a projecting portion (35) projecting outward in the radial direction is formed on the outer sleeve, and a phase changing portion (130) provided in the valve timing adjusting device is sandwiched in the axial direction between the projecting portion and the one shaft,

the movement restricting portion is provided closer to the actuator than the protruding portion in the axial direction.

14. A valve timing adjusting apparatus provided with the hydraulic oil control valve according to any one of claims 1 to 13.

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. The following working oil control valves are disclosed in the specifications of international publication No. 2015/141245 and german patent application publication No. 102012200682: 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 described in international publication No. 2015/141245, a plate-shaped member is disposed at an end portion of the hydraulic oil control valve on the actuator side in order to prevent the inner sleeve and the spool from coming off to the actuator side, and a convex portion provided on an outer peripheral surface of the inner sleeve is fitted into a concave portion provided on an inner peripheral surface of the outer sleeve in order to restrict rotation of the inner sleeve with respect to the outer sleeve. In the hydraulic control valve described in german patent application publication No. 102012200682, a projection projecting radially inward is formed at an end portion of the outer sleeve on the actuator side in order to prevent the inner sleeve and the valve body from coming off to the actuator side, and a hole formed in the projection in the axial direction is fitted to the projection formed in the inner sleeve in order to restrict rotation of the inner sleeve with respect to the outer sleeve.

Disclosure of Invention

In the hydraulic oil control valve described in international publication No. 2015/141245, it is not easy to provide a recess in the inner peripheral surface of a bottomed cylindrical outer sleeve, and there is a possibility that the manufacturing cost of the outer sleeve increases due to the processing of the recess. In the hydraulic oil control valve described in german patent application publication No. 102012200682, since it is necessary to form a protruding portion at an end portion of the outer sleeve and to perform hole machining on the protruding portion, there is a possibility that workability of the outer sleeve is poor and manufacturing cost of the outer sleeve is increased. Therefore, a technique capable of suppressing an increase in cost required for preventing the inner sleeve and the valve element from coming off to the actuator side and preventing the inner sleeve from rotating with respect to the outer sleeve 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 movement restricting section; and a fixing member, the sleeve having: an inner sleeve disposed outside the valve element in the radial direction; and an outer sleeve in which a shaft hole is formed along the axial direction, the inner sleeve being inserted into at least a part of the shaft hole in the axial direction, wherein the movement restricting unit is configured to restrict movement of the inner sleeve in a direction away from the actuator along the axial direction, and wherein the fixing member is fixed to an end portion of the outer sleeve on the actuator side, and is configured to restrict rotation of the inner sleeve relative to the outer sleeve in the circumferential direction and to restrict the inner sleeve and the valve body from coming off from the outer sleeve in the axial direction toward the actuator side.

According to the hydraulic control valve of this aspect, the fixing member is fixed to the actuator-side end portion of the outer sleeve, and the inner sleeve is configured to be able to restrict the rotation of the outer sleeve in the circumferential direction and to be able to restrict the inner sleeve and the valve element from coming off from the outer sleeve in the axial direction toward the actuator side.

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

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

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 view from the direction a of figure 3,

FIG. 6 is a perspective view showing a schematic structure of the inner sleeve,

FIG. 7 is a perspective view showing a schematic structure of a fixing member,

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 a schematic configuration of a hydraulic oil control valve according to a second embodiment,

fig. 11 is a sectional view showing a schematic configuration of a hydraulic oil control valve according to a third embodiment,

FIG. 12 is a perspective view showing a schematic structure of an inner sleeve in the third embodiment,

FIG. 13 is a perspective view showing a schematic structure of a fixing member in the third embodiment,

fig. 14 is a sectional view showing a schematic configuration of a hydraulic oil control valve according to a fourth embodiment,

FIG. 15 is a front view showing a schematic structure of a fixing member in the fifth embodiment,

fig. 16 is a perspective view showing a schematic configuration of a hydraulic oil control valve according to a sixth embodiment,

fig. 17 is a perspective view showing a schematic structure of a fixing member in the seventh 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 fixed portion 32 of the hydraulic oil control valve 10. The supply hole portion 326 is formed in the radial direction so that the outer circumferential surface of the camshaft 320 communicates with the shaft hole portion 322. 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 conversion unit that converts 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. 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 element 50, a spring 60, a fixing member 70, and a check valve 90. 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 has a main body portion 31, a protruding portion 35, a fixing portion 32, an enlarged diameter portion 36, a movement restricting portion 80, a positioning portion 82, and a tool engaging portion 38. A shaft hole 34 is formed along the axial direction AD in the body portion 31 and the 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 vane rotor 130 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 protruding portion 35 is formed to protrude radially outward from the main body portion 31. The protruding portion 35 sandwiches the vane rotor 130 shown in fig. 1 in the axial direction AD between the protruding portion and the end portion 321 of the camshaft 320. Therefore, the protrusion 35 abuts against the vane rotor 130 in the axial direction AD, and generates an axial force.

The fixing portion 32 has a cylindrical external shape and is formed to be continuous with the main body portion 31 in the axial direction AD. The fixing portion 32 is formed to have substantially the same diameter as the body portion 31, and is inserted into a shaft fixing portion 323 of the camshaft 320 as shown in fig. 1. The 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.

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. In other words, the movement restricting portion 80 is configured to restrict the movement of the inner sleeve 40 in the axial direction AD to the side opposite to the solenoid 160 side. In the present embodiment, the movement restricting portion 80 is provided on the solenoid 160 side of the protruding portion 35 in the axial direction AD.

The positioning portion 82 is formed by a radial step formed by the enlarged diameter portion 36 on the inner circumferential surface of the outer sleeve 30. That is, the height difference functions as the movement restricting portion 80 in a part in the circumferential direction and functions as the positioning portion 82 in the other part in the circumferential direction. The positioning portion 82 abuts on an end portion of a fitting projection 73 of the fixing member 70 described later in the axial direction AD. By the abutment of the positioning portion 82 with the fixing member 70, the position in the axial direction AD of the fixing member 70 when the fixing member 70 is assembled to the outer sleeve 30 is determined.

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.

As shown in fig. 5, the tool engagement portion 38 has a hexagonal cross-sectional view shape in a cross section perpendicular to the rotation axis AX. Therefore, 6 peak portions 39 formed to be thick in the radial direction are formed in the tool engagement portion 38.

As shown in fig. 3, the outer sleeve 30 of the present embodiment further includes a non-disposed portion 37 where the inner sleeve 40 is not disposed radially inward. The non-disposed portion 37 constitutes an end portion of the fixed portion 32 on the camshaft 320 side. In the present embodiment, the inner diameter of the non-disposed portion 37 is formed larger than the inner diameter of the inner sleeve 40. Thus, the minimum value of the inner diameter of the outer sleeve 30 is greater than the maximum value of the inner diameter of the inner sleeve 40.

As shown in fig. 3 and 6, 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, and a stopper 49.

The cylindrical portion 41 has a substantially cylindrical external shape, and is located radially inward of the outer sleeve 30 over the main body portion 31 and the fixing portion 32 of the outer sleeve 30. 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. 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 6, 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. As shown in fig. 6, 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 end portion of the cylindrical portion 41 on the opposite side to the solenoid 160 (hereinafter, also referred to as "the camshaft 320 side" for convenience of description) in the axial direction AD. One end of the spring 60 abuts the bottom 42.

As shown in fig. 6, 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 side projecting walls 43 adjacent to each other in the circumferential direction communicate with the shaft hole 322 of the camshaft 320 shown in fig. 1, and the hydraulic oil supplied from the hydraulic oil supply source 350 flows therethrough. As shown in fig. 6, 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. 6, 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 shaft hole 322 shown in fig. 1, and the working oil supplied from the working oil supply source 350 flows therethrough. As shown in fig. 6, the advanced side wall 44 is formed with an inner advanced port 24. 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. 6, 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. In the present embodiment, the end surface of the flange portion 46 on the solenoid 160 side functions as the first contact portion CP 1. The first contact portion CP1 is configured to be able to contact the fixed member 70. The end surface of the flange portion 46 on the camshaft 320 side functions as the second contact portion CP 2. The second contact portion CP2 is configured to be able to contact the movement restricting portion 80.

As shown in fig. 3, the stopper 49 is formed at an end portion on the camshaft 320 side, which is 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.

A space formed between the shaft hole 34 of the outer sleeve 30 and the inner sleeve 40 functions as the hydraulic oil supply passage 25. 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. 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, at least a part of the drain oil passage 53, a drain inflow portion 54, and a drain outflow portion 55 are formed in the valve body 50.

As shown in fig. 3 and 4, the valve body portion 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. The engagement portion 59 comes into contact with 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, at least a part of the oil discharge passage 53 is formed inside the valve body 50. 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. The fixing member 70 is configured to be able to restrict the inner sleeve 40 from rotating in the circumferential direction with respect to the outer sleeve 30 and to be able to restrict the inner sleeve 40 and the valve body 50 from coming off from the outer sleeve 30 in the axial direction AD toward the solenoid 160. The fixing member 70 has a flat plate portion 71 and a plurality of fitting projections 73.

As shown in fig. 7, 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. 7, 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. As shown in fig. 5, the outer edge portion of the end surface of the fixing member 70 on the solenoid 160 side functions as a caulked portion 74 caulked and fixed to the outer sleeve 30. The caulked portion 74 is caulked at a position corresponding to the top portion 39 of the tool engagement portion 38 of the outer sleeve 30 in the circumferential direction. Thereby, the caulking piece F is formed at a position corresponding to the top portion 39 of the caulked portion 74. In the present embodiment, the fixing member 70 is fixed by caulking at a position corresponding to 3 peak portions 39 intermittently in the circumferential direction among 6 peak portions 39 of the tool engagement portion 38. At the time of caulking, the end portions of the plurality of fitting protrusions 73 of the fixing member 70 on the camshaft 320 side abut against the positioning portions 82 formed on the outer sleeve 30. Thereby, the position in the axial direction AD of the fixing member 70 is determined.

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.

In a state where the fixing member 70 is caulked and fixed to the outer sleeve 30, a gap in the axial direction AD is formed at least one of between the fixing member 70 and the first contact portion CP1 and between the movement restricting portion 80 and the second contact portion CP 2. In other words, in a state where the fixed member 70 is swaged and fixed to the outer sleeve 30, the dimension in the axial direction AD from the end surface on the first contact portion CP1 side in the flat plate portion 71 of the fixed member 70 to the end surface on the second contact portion CP2 side of the movement restricting portion 80 is formed to be slightly larger than the dimension in the axial direction AD from the first contact portion CP1 to the second contact portion CP2 of the inner sleeve 40, that is, the thickness of the flange portion 46.

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.

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. The solenoid 160 corresponds to a subordinate concept of the actuator in the present disclosure, and the vane rotor 130 corresponds to a subordinate concept of the phase shifting portion 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.

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 adjustment device 100 according to the first embodiment described above, the fixing member 70 fixed to the outer sleeve 30 is configured to be able to restrict the inner sleeve 40 from rotating in the circumferential direction with respect to the outer sleeve 30 and to restrict the inner sleeve 40 and the valve body 50 from coming off from the outer sleeve 30 in the axial direction AD toward the solenoid 160. Therefore, prevention of rotation of the inner sleeve 40, prevention of dropping of the inner sleeve 40, and prevention of dropping of the valve body 50 can be achieved by using one component. Therefore, as compared with a structure in which the prevention of the rotation of the inner sleeve 40, the prevention of the drop-out of the inner sleeve 40, and the prevention of the drop-out of the valve element 50 are realized by different members, an increase in the number of components of the hydraulic control valve 10 can be suppressed. Further, as compared with a structure in which the prevention of the rotation of the inner sleeve 40, the prevention of the drop-out of the inner sleeve 40, and the prevention of the drop-out of the valve element 50 are realized by using 2 or more different mechanisms, complication of the manufacturing process of the hydraulic control valve 10 can be suppressed. Further, since the prevention of the rotation of the inner sleeve 40, the prevention of the drop-out of the inner sleeve 40, and the prevention of the drop-out of the valve element 50 can be achieved by the fixing member 70, the complication of the shape of the outer sleeve 30 can be suppressed. Therefore, it is possible to suppress an increase in cost required to prevent the inner sleeve 40 and the valve body 50 from falling off to the solenoid 160 side and to prevent the inner sleeve 40 from rotating with respect to the outer sleeve 30.

Further, since the fixing member 70 is fixed to the outer sleeve 30, it is possible to suppress an excessive load from being applied to the inner sleeve 40 for fixing the fixing member 70. Therefore, deformation of the inner sleeve 40 can be suppressed, and therefore deterioration of the slidability of the valve body 50 can be suppressed.

Further, since the gap in the axial direction AD is formed at least one of between the fixing member 70 and the first contact portion CP1 and between the movement restricting portion 80 and the second contact portion CP2, it is possible to suppress the load from being applied from the inner sleeve 40 to the fixing member 70 and the movement restricting portion 80 due to a temperature change in the case of the mode in which the linear expansion coefficient of the inner sleeve 40 is larger than the linear expansion coefficient of the outer sleeve 30. Therefore, the reliability of the function of the fixing member 70 and the function of the movement restricting portion 80 can be suppressed from being lowered. In addition, the gap can be formed, and thus it is possible to suppress the caulking load applied to the fixing member 70 from being applied to the inner sleeve 40 at the time of assembly. Therefore, deformation of the inner sleeve 40 due to the caulking load can be suppressed, and deterioration of the slidability of the valve body 50 can be suppressed. On the other hand, during engine operation, the inner sleeve 40 is pushed toward the fixing member 70 by the hydraulic pressure supplied from the supply hole 326. By setting the pressing force generated according to the supplied hydraulic pressure and the area of the inner sleeve pressure receiving portion to be larger than the load generated by the spring 60 or the solenoid 160, the inner sleeve 40 can be pressed against the fixed member 70. Therefore, performance variation of the valve timing adjusting apparatus 100 due to the backlash can be suppressed.

Further, since the positioning portion 82 that abuts the fixing member 70 in the axial direction AD is formed in the outer sleeve 30, the position of the fixing member 70 in the axial direction AD can be specified. Therefore, a gap in the axial direction AD can be easily formed at least one of between the fixing member 70 and the first contact portion CP1 and between the movement restricting portion 80 and the second contact portion CP2, and the load in the axial direction AD can be suppressed from being applied to the inner sleeve 40. Further, since the radial step formed by the enlarged diameter portion 36 on the inner peripheral surface of the outer sleeve 30 functions as both the movement restricting portion 80 and the positioning portion 82, the structure for realizing the movement restricting portion 80 and the positioning portion 82 can be suppressed from being complicated.

Further, since the inner diameter of the body portion 31 of the outer sleeve 30 is configured to be substantially constant within the seal range SA, it is possible to suppress complication of the inner surface processing of the body portion 31 of the outer sleeve 30 in the seal range SA where dimensional accuracy is required. Therefore, since the inner surface of the main body portion 31 of the outer sleeve 30 can be machined by grinding, reaming, or the like, an increase in the number of machining steps can be suppressed, and an increase in the manufacturing cost of the outer sleeve 30 can be suppressed. Further, since the shaft hole 34 of the outer sleeve 30 is formed to penetrate the outer sleeve 30 in the axial direction AD and the inner diameter of the non-arrangement portion 37 of the outer sleeve 30 is formed to be larger than the inner diameter of the inner sleeve 40, the outer sleeve 30 can be easily manufactured by forging or the like, and in addition, the outer sleeve can be easily manufactured using a tubular material. Therefore, the number of processing steps of the outer sleeve 30 can be suppressed from increasing, and the manufacturing cost of the outer sleeve 30 can be suppressed from increasing.

Further, since the fixing member 70 having the flat plate portion 71 and the fitting projection portion 73 is provided, the structure of the fixing member 70 can be suppressed from being complicated, and an increase in the manufacturing cost of the fixing member 70 can be suppressed. Further, since the flange portion 46 of the inner sleeve 40 is disposed in the enlarged diameter portion 36 of the outer sleeve 30, the step generated in the enlarged diameter portion 36 can function as the movement restricting portion 80, and the movement of the inner sleeve 40 in the axial direction AD to the side opposite to the solenoid 160 side can be restricted. Further, since the inner sleeve 40 can be prevented from dropping out to the solenoid 160 side and restricted from moving to the camshaft 320 side by sandwiching the flange portion 46 of the inner sleeve 40, complication of positioning at the time of assembly can be suppressed, and assembly accuracy can be improved. Further, since the movement restricting portion 80 is provided on the solenoid 160 side of the protruding portion 35 of the outer sleeve 30 in the axial direction AD, the shape of the fixing portion 32 can be easily changed in accordance with the shapes of the end portion 321 of the cam shaft 320 and the shaft hole portion 322 without providing the movement restricting portion to the fixing portion 32 of the outer sleeve 30.

Further, since the fixing member 70 has the caulked portion 74, the fixing member 70 can be fixed to the outer sleeve 30 by caulking. Therefore, as compared with the fixing method by press fitting or the like, the dimensional accuracy of the fixing member 70 and the outer sleeve 30 can be relaxed, and an increase in manufacturing cost can be suppressed. Further, the caulked portion 74 of the fixing member 70 is caulked at a position corresponding to the top portion 39 of the tool engagement portion 38 of the outer sleeve 30 in the circumferential direction, so that deformation of the tool engagement portion 38 due to caulking 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 space formed between the shaft hole 34 of the outer sleeve 30 and the inner sleeve 40. Therefore, as compared with a structure in which the inside of the valve body functions as a hydraulic oil supply passage, the application of hydraulic pressure to the valve body 50 for supplying hydraulic oil can be suppressed, and deterioration in the sliding property of the valve body 50 can be suppressed. Further, since the sleeve 20 has a double structure, the ports SP1, SP2, 23, 24, and 47 can be easily formed in the inner sleeve 40. Therefore, the workability of the ports SP1, SP2, 27, 28, and 47 in the sleeve 20 can be improved, and the complexity 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, and 47 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.

The outer sleeve 30a included in the hydraulic oil control valve 10a according to the second embodiment has a supply portion 327 between the body portion 31 and the fixing portion 32a in the axial direction AD. At least a part of the supply portion 327 in the axial direction AD constitutes a non-arrangement portion 37a where the inner sleeve 40 is not arranged on the inner side in the radial direction. The supply portion 327 has a supply hole 328 that opens in the radial direction and communicates the outer peripheral surface of the supply portion 327 with the axial hole 34 a. The supply hole 328 is supplied with working oil from a working oil supply source 350. The fixing portion 32a has a columnar shape, and the shaft hole 34a is omitted. Therefore, the shaft hole 34a does not penetrate the outer sleeve 30a in the axial direction AD. In the present embodiment, the supply portion 327 and the fixing portion 32a are formed to have outer diameters smaller than those of the body portion 31, respectively, but may be formed to have substantially the same outer diameter.

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. In addition, since the supply portion 327 having the supply hole 328 is provided, the length of the supply portion 327 in the axial direction AD can be adjusted to match the structure of the camshaft 320, and the degree of freedom in designing the hydraulic oil control valve 10 can be increased.

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 it includes an outer sleeve 30b, an inner sleeve 40b, a valve element 50b, and a fixing member 70b instead of the outer sleeve 30, the inner sleeve 40, the valve element 50, and the fixing member 70. 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 is formed so that the axial direction AD of the enlarged diameter portion 36b is short, and includes a movement restricting portion 80b instead of the movement restricting portion 80. That is, the radial step formed by the enlarged diameter portion 36b on the inner circumferential surface of the outer sleeve 30b does not function as the movement restricting portion 80, but only functions as the positioning portion 82 b. The movement restricting portion 80b is formed to have a smaller inner diameter than the other portion of the body portion 31 on the camshaft 320 side of the retarded-angle side projecting wall 43 of the inner sleeve 40b in the axial direction AD. The positioning portion 82b abuts on an end portion of the fitting projection 73b of the fixing member 70b in the axial direction AD.

As shown in fig. 12, the inner sleeve 40b has a locking end 46b at the end on the solenoid 160 side instead of the flange 46. The locking end portion 46b is formed to have an outer diameter smaller than the inner diameter of the body portion 31 of the outer sleeve 30b and to be substantially the same as the outer diameters of the retarded side wall 43, the advanced side wall 44, and the closing wall 45, respectively. The end surface of the latching end 46b on the solenoid 160 side functions as a first contact portion CP 1. The first contact portion CP1 is configured to be able to contact the fixed member 70 b. The engagement end 46b is formed with a fitting portion 48 b. In the present embodiment, the fitting portion 48b is formed by being recessed at one circumferential portion in the outer edge portion of the end surface of the latching end portion 46b on the solenoid 160 side. The fitting portion 48b is fitted to the fitting projection 73b of the fixing member 70 b. As shown in fig. 11, the end surface of the retarded side wall 43 of the inner sleeve 40b on the camshaft 320 side functions as the second contact portion CP 2. The second contact portion CP2 is configured to be able to contact the movement restricting portion 80 b.

The valve body 50b has a valve body bottom portion 52b and a locking portion 59b instead of the valve body bottom portion 52 and the locking portion 59. The spool bottom 52b is located closer to the camshaft 320 than the fixed member 70 b. The engagement portion 59b is formed on the valve body bottom portion 52b to protrude radially outward.

As shown in fig. 13, the fixing member 70b has a thin plate-like external shape, and has one fitting projection 73b instead of the plurality of fitting projections 73. The fitting projection 73b is formed by bending a part of the flat plate portion 71 so as to project from the flat plate portion 71 in the axial direction AD. The fitting projection 73b is fitted to the fitting portion 48b of the inner sleeve 40 b.

In a state where the fixing member 70b is caulked and fixed to the outer sleeve 30b, a gap in the axial direction AD is formed at least one of between the fixing member 70b and the first contact portion CP1 and between the movement restricting portion 80b and the second contact portion CP 2. In other words, in a state where the fixed member 70b is swaged and fixed to the outer sleeve 30b, the dimension in the axial direction AD from the end surface on the first contact portion CP1 side in the flat plate portion 71 of the fixed member 70b to the end surface on the second contact portion CP2 side of the movement restricting portion 80b is formed to be slightly larger than the dimension in the axial direction AD from the first contact portion CP1 to the second contact portion CP2 of the inner sleeve 40 b.

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. In addition, since the flange portion 46 of the inner socket 40b is omitted, cutting work or the like for forming the flange portion 46 can be omitted, and an increase in manufacturing cost of the inner socket 40b can be suppressed. Further, since the thin plate-shaped fixing member 70b is provided, the structure of the fixing member 70b can be simplified, and an increase in the manufacturing cost of the fixing member 70b can be suppressed.

D. Fourth embodiment:

the hydraulic oil control valve 10c according to the fourth embodiment shown in fig. 14 differs from the hydraulic oil control valve 10b according to the third embodiment in the structures of the hydraulic oil supply mechanism, the hydraulic oil discharge mechanism, and the movement restricting portion 80 c. More specifically, the present invention is different from the hydraulic oil control valve 10b of the third embodiment in that an outer sleeve 30c and an inner sleeve 40c are provided instead of the outer sleeve 30b and the inner sleeve 40 b. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.

The outer sleeve 30c provided in the hydraulic oil control valve 10c according to the fourth embodiment includes a body portion 31c and a fixed portion 32c instead of the body portion 31 and the fixed portion 32, and includes a reduced diameter portion 327c that extends in the axial direction AD between the body portion 31c and the fixed portion 32 c.

In the body portion 31c, a supply hole 328c that communicates the outer peripheral surface and the inner peripheral surface of the body portion 31c is formed on the camshaft 320 side of the outer retard angle port 21 in the axial direction AD. The supply hole 328c is supplied with working oil from the working oil supply source 350.

The fixing portion 32c is formed to have an outer diameter and an inner diameter smaller than those of the body portion 31c, respectively. The inside of the fixing portion 32c functions as an oil discharge passage 53 c. A second drain outflow portion 55c is formed at the end portion of the fixing portion 32c on the camshaft 320 side. The second drain outflow portion 55c discharges the hydraulic oil in the drain oil passage 53c to the outside of the hydraulic oil control valve 10c through the shaft hole portion 322 formed in the camshaft 320.

The reduced diameter portion 327c is formed to have an outer diameter and an inner diameter smaller than those of the body portion 31 c. The reduced diameter portion 327c includes a sealing portion S, a movement restricting portion 80c, a stopper 49c, and a spring contact portion 69 c. The seal portion S, the movement restricting portion 80c, the stopper 49c, and the spring contact portion 69c are arranged in this order from the solenoid 160 side in the axial direction AD, and the inner diameter of the reduced diameter portion 327c is formed to be reduced in a stepwise manner.

The seal portion S separates the hydraulic oil supply passage 25 from the drain oil passage 53 c. The inner diameter of the seal portion S is formed to be substantially the same as the outer diameter of the end portion of the inner sleeve 40c on the camshaft 320 side. The movement restricting portion 80c is configured to be able to abut against a second contact portion CP2 that is an end surface of the inner sleeve 40c on the camshaft 320 side. The movement restricting portion 80c restricts movement of the inner sleeve 40c in the axial direction AD to the side opposite to the solenoid 160 side. The stopper 49c is configured to be able to abut against the end portion of the valve body 50b on the camshaft 320 side. The stopper 49c defines a sliding limit of the valve element 50b in a direction away from the solenoid portion 162 of the solenoid 160. One end of the spring 60 abuts on the spring abutment portion 69 c. The inside of the reduced diameter portion 327c functions as an oil discharge passage 53 c.

The bottom 42 is omitted from the inner sleeve 40 c. Therefore, an opening portion TH penetrating in the axial direction AD is formed in the end portion of the inner sleeve 40c on the camshaft 320 side. The end portion of the valve body 50b on the camshaft 320 side is inserted into the opening TH. In the present embodiment, the length of the inner sleeve 40c along the axial direction AD is formed to be substantially the same as the length of the valve element 50b, but may be formed to be shorter than the length of the valve element 50b or longer than the length of the valve element 50b within a range in which the function of the seal portion S can be ensured.

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 10b of the third embodiment are obtained. In addition, since the opening TH is formed without omitting the bottom portion 42 of the inner socket 40c, the length of the inner socket 40c in the axial direction AD can be shortened. Therefore, the degree of freedom in designing the hydraulic oil control valve 10c can be increased, and mountability of the hydraulic oil control valve 10c can be improved.

E. Fifth embodiment:

as shown in fig. 15, the fixing member 70d provided in the hydraulic oil control valve according to the fifth embodiment differs from the fixing member 70 provided in the hydraulic oil control valve 10 according to the first embodiment in that the fixing member 70d includes a crimped portion 74d instead of the crimped portion 74. 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. 15 shows a front view of the fixing member 70D as viewed from the solenoid 160 side, as in fig. 5.

The swaged portion 74D of the fixing member 70D has an irregularity 75 in the axial direction AD. In the present embodiment, a plurality of irregularities 75 having a substantially quadrangular cross-sectional view shape are formed in a portion including a position corresponding to the top 39 of the tool engagement portion 38 of the outer sleeve 30 in the circumferential direction. The irregularities 75 may be formed in a direction intersecting the radial direction, not only in the axial direction AD, but also in a plurality of directions, and a single irregularity 75 may be formed.

The hydraulic oil control valve including the fixing member 70d according to the fifth embodiment described above achieves the same effects as those of the hydraulic oil control valve 10 according to the first embodiment. In addition, since the axial direction AD of the swaged portion 74d of the fixing member 70d is formed with the irregularities 75, the fixing member 70d can be prevented from rotating in the circumferential direction with respect to the outer sleeve 30 in a state where the fixing member 70d is swaged and fixed to the outer sleeve 30. Therefore, the inner sleeve 40 can be suppressed from rotating in the circumferential direction with respect to the outer sleeve 30, and the fixing strength in the circumferential direction can be increased.

F. Sixth embodiment:

a hydraulic oil control valve 10e according to a sixth embodiment shown in fig. 16 is different from the hydraulic oil control valve 10 according to the first embodiment in that a fixing member 70e is provided instead of the fixing member 70, the fixing member 70e also functions as a movement restricting portion, and a fixing mechanism of the fixing member 70e is provided. The fixing mechanism of the fixing member 70e is different from the hydraulic oil control valve 10 of the first embodiment in that an outer sleeve 30e and an inner sleeve 40e are provided instead of the outer sleeve 30 and the inner sleeve 40. 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 fixing member 70e is constituted by a rod-shaped pin. The fixing member 70e is disposed to penetrate the outer sleeve 30e and the inner sleeve 40e at a position closer to the solenoid 160 side than both the protruding portion 35 of the outer sleeve 30e and the locking portion 59 of the valve body 50 in the axial direction AD. In the present embodiment, the fixing member 70e has a substantially cylindrical external shape, but is not limited to a substantially cylindrical shape, and may have an arbitrary rod-like external shape such as a substantially quadrangular prism shape.

An outer through hole 78 is formed in the tool engagement portion 38e of the outer sleeve 30 e. The outer through hole 78 communicates the outer peripheral surface and the inner peripheral surface of the outer sleeve 30 e. The fixing member 70e is inserted into and fixed to the outer through hole 78. In the present embodiment, the enlarged diameter portion 36 of the outer sleeve 30e is omitted. Therefore, the inner diameter of the outer sleeve 30e is formed substantially the same throughout the axial direction AD.

The inner sleeve 40e has a locking end portion 45e instead of the flange portion 46. The locking end portion 45e is formed to have an outer diameter smaller than the inner diameter of the outer sleeve 30e and to be substantially the same as the outer diameters of the retarded side wall 43 and the advanced side wall 44, respectively. The locking end portion 45e is formed with an inner through hole 79. The inner through hole 79 communicates the outer peripheral surface and the inner peripheral surface of the inner sleeve 40 e. The fixing member 70e is inserted into the inner through hole 79.

In the present embodiment, the cross-sectional shapes of the outer through hole 78 and the inner through hole 79 are substantially circular, but the cross-sectional shapes are not limited to substantially circular, and may be any shapes according to the cross-sectional shape of the fixing member 70 e.

In the hydraulic oil control valve 10e according to the sixth embodiment, the fixing member 70e also functions as a movement restricting portion. The fixing member 70e is disposed so as to penetrate the outer sleeve 30e and the inner sleeve 40e, whereby the rotation of the inner sleeve 40e can be restricted, the inner sleeve 40e can be restricted from dropping out to the solenoid 160 side, and the inner sleeve 40e can be restricted from moving to the camshaft 320 side. In the present embodiment, the inner peripheral surface of the inner through hole 79 formed in the inner sleeve 40e functions as the first contact portion CP1 and the second contact portion CP 2. Further, a gap in the axial direction AD is formed between the inner peripheral surface of the inner through hole 79 and the outer peripheral surface of the fixing member 70e inserted into the inner through hole 79.

The fixing member 70e is disposed so as to penetrate the outer sleeve 30e and the inner sleeve 40e at a position closer to the solenoid 160 than the locking portion 59 of the valve element 50, and thereby the valve element 50 can be restricted from falling off to the solenoid 160. That is, the sliding of the valve body 50 in the direction approaching the solenoid portion 162 of the solenoid 160 is restricted by the fixing member 70e abutting against the locking portion 59.

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. In addition, since the fixing member 70e is configured by a rod-shaped pin and also functions as a movement restricting portion, it is possible to use one component to restrict movement of the inner sleeve 40e along the axial direction AD to the side opposite to the solenoid 160 side in addition to preventing rotation of the inner sleeve 40e, preventing dropping of the inner sleeve 40e, and preventing dropping of the valve body 50 e. Therefore, an increase in the manufacturing cost of the hydraulic oil control valve 10e can be further suppressed.

Further, since the fixing member 70e is formed of a rod-shaped pin and is disposed so as to penetrate the outer sleeve 30e and the inner sleeve 40e, the shapes of the outer sleeve 30e and the inner sleeve 40e can be suppressed from being complicated, respectively. Further, since the inner diameter of the outer sleeve 30e is formed to be substantially the same throughout the axial direction AD, complication of the inner surface processing of the body portion 31 of the outer sleeve 30 can be further suppressed. Further, since the flange portion 46 of the inner sleeve 40e is omitted, cutting work or the like for forming the flange portion 46 can be omitted, and an increase in manufacturing cost of the inner sleeve 40e can be suppressed. Further, since the fixing member 70e as the movement restricting portion is provided on the solenoid 160 side with respect to the protruding portion 35 of the outer sleeve 30 in the axial direction AD, the shape of the fixing portion 32 can be easily changed in accordance with the shapes of the end portion 321 of the camshaft 320 and the shaft hole portion 322 without providing the movement restricting portion to the fixing portion 32 of the outer sleeve 30.

G. The seventh embodiment:

as shown in fig. 17, the fixing member 70f provided in the hydraulic oil control valve according to the seventh embodiment further includes a first engaging portion 78f, which is different from the fixing member 70b provided in the hydraulic oil control valve 10b according to the third embodiment. Since other configurations are the same as those of the third embodiment, the same reference numerals are given to the same configurations, and detailed description thereof is omitted.

The first engaging portion 78f is formed as a convex portion that protrudes radially outward from the flat plate portion 71. The first engaging portion 78f engages with a second engaging portion, not shown, formed at the end of the outer sleeve 30b on the solenoid 160 side. The second engaging portion may be formed of a recess formed to be recessed radially outward. The first engaging portion 78f formed on the fixing member 70f may be formed as a concave portion, and the second engaging portion formed on the outer sleeve 30b may be formed as a convex portion, or may be formed in any shape that can engage with each other.

The hydraulic oil control valve including the fixing member 70f according to the seventh embodiment described above achieves the same effects as those of the hydraulic oil control valve 10b according to the third embodiment. In addition, since the first engagement portion 78f formed in the fixed member 70f engages with the second engagement portion formed in the outer sleeve 30b, the fixed member 70f can be restricted from rotating in the circumferential direction with respect to the outer sleeve 30 b. Further, since the first engaging portion 78f is formed by the convex portion, complication of the processing for forming the second engaging portion in the outer sleeve can be suppressed.

H. Other embodiments are as follows:

in the first, second, and fifth embodiments, the plurality of fitting projections 73 are formed on the fixing members 70 and 70d, respectively, but the number is not limited to a plurality, and one fitting projection 73 may be formed. In the third and fourth embodiments, the fixing member 70b is provided with one fitting projection 73b, but the number is not limited to one, and a plurality of fitting projections 73b may be provided. In the third and fourth embodiments, the fitting portion 48b of the inner sleeves 40b and 40c is formed on the outer edge portion of the end surface of the latching end portion 46b on the solenoid 160 side, but the fitting portion is not limited to the outer edge portion, and may be formed at any position on the end surface of the latching end portion 46b on the solenoid 160 side. The first engaging portion 78f formed in the fixing member 70f in the seventh embodiment may be formed in the fixing members 70 and 70d of the first, second, and fifth embodiments. With such a configuration, the same effects as those of the above embodiments are obtained.

In the first to fifth embodiments, the fixing members 70, 70b, and 70d are caulked at positions corresponding to the top portions 39 of the tool engagement portions 38, but the fixing members are not limited to positions corresponding to the top portions 39 and may be caulked at arbitrary positions in the circumferential direction. The fixing members 70, 70b, 70d may be fixed to the outer sleeves 30, 30a, 30b, 30c by welding or the like, without being limited to the caulking fixation. With this configuration, the same effects as those of the first to fifth embodiments are obtained.

In the third and sixth embodiments, the gaps in the axial direction AD are formed at least one of between the fixing members 70b and 70e and the first contact portion CP1 and between the movement restricting portion 80b and the second contact portion CP2, but the gaps may be omitted. In the above embodiments, the inner diameters of the main bodies 31, 31c of the outer sleeves 30, 30a, 30b, 30c, 30e are configured to be fixed at least within the sealing range SA, but may not be fixed. In the first, third, and sixth embodiments, the minimum value of the inner diameters of the outer sleeves 30, 30e is configured to be larger than the maximum value of the inner diameters of the inner sleeves 40, 40b, 40e, but may be configured to be smaller than the maximum value. With such a configuration, the same effects as those of the above embodiments are obtained.

The configuration of the hydraulic oil control valves 10, 10a, 10b, 10c, and 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 insides of the valve bodies 50, 50b, 50e may be configured as the hydraulic oil supply oil passages 25, and the radial clearances between the outer sleeves 30, 30a, 30b, 30c, 30e and the inner sleeves 40, 40b, 40c, 40e may be configured as the drain oil passages 53, 53 c. 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.

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.