WO2020196454A1 - Hydraulic oil control valve and valve timing adjustment device - Google Patents

Abstract

A hydraulic oil control valve (10, 10a) arranged on a rotary shaft (AX) of a valve timing adjustment device (100) that adjusts the valve timing of a valve (330) that is driven to open and close by a driven shaft (320) to which power is transmitted from a drive shaft (310) includes a tubular sleeve (20) and a spool (50, 50a) that slides in the axial direction (AD) on the radially inner side of the sleeve, wherein the sleeve has an inner sleeve (40, 40a) arranged on the radially outer side of the sleeve, and an outer sleeve (30, 30a) that is arranged on the radially outer side of the inner sleeve and can be fixed to one shaft end by applying an axial force in the axial direction, and in a state where no axial force is applied, a minimum radial clearance (CL1) between the outer sleeve and the inner sleeve is larger than the minimum radial clearance (CL2) between the inner sleeve and the spool.

Description

Hydraulic oil control valve and valve timing adjuster Cross-reference of related applications

This application is based on Japanese Application No. 2019-055892 filed on March 25, 2019, and the contents of the description are incorporated herein by reference.

The present disclosure relates to a hydraulic oil control valve used in a valve timing adjusting device.

Conventionally, a hydraulic valve timing adjusting device that can adjust the valve timing of the intake valve and the exhaust valve of an internal combustion engine has been known. In the hydraulic valve timing adjusting device, the hydraulic oil is supplied to each hydraulic chamber formed by the vane rotor in the housing and the hydraulic oil is discharged from each hydraulic chamber, which is a hydraulic oil control valve provided in the center of the vane rotor. May be realized by. Patent Document 1 has a sleeve having a double structure of a tubular outer sleeve and an inner sleeve, the outer sleeve is fastened to the end of a camshaft, and the spool slides inside the inner sleeve to obtain oil. A hydraulic oil control valve that switches the path is disclosed.

Japanese Unexamined Patent Publication No. 2018-115618

Since the hydraulic oil control valve described in Patent Document 1 has a sleeve having a double structure, hydraulic oil may leak not only between the inner sleeve and the spool but also between the outer sleeve and the inner sleeve. .. Therefore, the amount of hydraulic oil leaked from the hydraulic oil control valve as a whole may increase. Therefore, the inventor of the present invention envisions designing by reducing the radial gap between the outer sleeve and the inner sleeve in order to suppress such an increase in the amount of leakage. However, the inventor of the present application has found that when the outer sleeve is fastened to the end of the cam shaft, the outer sleeve shrinks in the radial direction due to the axial force of the fastening, and the slidability of the spool may deteriorate due to this. It was. Therefore, there is a demand for a technique capable of suppressing an increase in the amount of hydraulic oil leakage while suppressing deterioration of spool slidability.

This disclosure was made to solve at least a part of the above-mentioned problems, and can be realized in the following forms.

According to one form of the present disclosure, a hydraulic oil control valve is provided. This hydraulic oil control valve is fixed to the end of one of the drive shaft and the driven shaft that drives the valve to open and close by transmitting power from the drive shaft, and adjusts the valve timing of the valve. In the device, it is a hydraulic oil control valve that is arranged and used on the rotating shaft of the valve timing adjusting device to control the flow of hydraulic oil supplied from the hydraulic oil supply source, and has a tubular sleeve and its own. A spool driven by an actuator arranged in contact with one end and sliding axially inside the sleeve in the radial direction, the sleeve being an inner arranged radially outside the spool. An outer sleeve in which a sleeve and a shaft hole along the axial direction are formed, the inner sleeve is inserted into at least a part of the shaft hole in the axial direction, and an axial force in the axial direction is applied. With an outer sleeve that can be fixed to the end of one of the shafts, and in a state where the axial force is not applied, the minimum radial gap between the outer sleeve and the inner sleeve is the said. It is larger than the minimum radial clearance between the inner sleeve and the spool.

According to the hydraulic oil control valve of this form, the minimum radial gap between the outer sleeve and the inner sleeve is the minimum radial gap between the inner sleeve and the spool when no axial force is applied. Greater than. Generally, in a hydraulic oil control valve that changes the oil passage by sliding the spool, different parts along the axial direction are sealed according to the stroke of the spool. Therefore, the length along the axial direction in the minimum radial gap between the inner sleeve and the spool is set shorter than the stroke of the spool. Therefore, hydraulic oil is likely to leak from the minimum radial gap between the inner sleeve and the spool. Further, the inner sleeve does not move relative to the outer sleeve in the axial direction. Therefore, the length along the axial direction in the minimum radial gap between the outer sleeve and the inner sleeve is set to be relatively long. Therefore, hydraulic oil is less likely to leak from the minimum radial gap between the outer sleeve and the inner sleeve. From these facts, we secured a radial gap that can suppress the deterioration of spool slidability even if the outer sleeve elastically deforms due to the axial force that fixes the hydraulic oil control valve and shrinks in the radial direction. In this case, it is possible to suppress an increase in the amount of hydraulic oil leakage as compared with a configuration in which the magnitude relationship of the radial gap is different from that of the present application. Therefore, it is possible to suppress an increase in the amount of hydraulic oil leakage while suppressing deterioration of spool slidability.

According to another form of the present disclosure, a hydraulic oil control valve is provided. This hydraulic oil control valve is fixed to the end of one of the drive shaft and the driven shaft that drives the valve to open and close by transmitting power from the drive shaft, and adjusts the valve timing of the valve. In the device, it is a hydraulic oil control valve that is arranged and used on the rotating shaft of the valve timing adjusting device to control the flow of hydraulic oil supplied from the hydraulic oil supply source, and has a tubular sleeve and its own. A spool driven by an actuator arranged in contact with one end and sliding axially inside the sleeve in the radial direction, the sleeve being an inner arranged radially outside the spool. An outer sleeve in which a sleeve and a shaft hole along the axial direction are formed, the inner sleeve is inserted into at least a part of the shaft hole in the axial direction, and an axial force in the axial direction is applied. The outer sleeve and the inner sleeve have an outer sleeve that can be fixed to the end of one of the shafts, and the outer sleeve and the inner sleeve are in a state where predetermined conditions including the application of the axial force are satisfied. , Contact in the radial direction.

According to the hydraulic oil control valve of this form, the outer sleeve and the inner sleeve come into radial contact with each other in a state where predetermined conditions including the application of axial force are satisfied, so that the outer sleeve and the inner sleeve come into contact with each other in the radial direction. It is possible to suppress an increase in the amount of hydraulic oil leaking from the radial gap between the two. Further, since the inner sleeve can be suppressed from expanding in the radial direction due to the radial contact between the outer sleeve and the inner sleeve, it is possible to suppress the expansion of the radial gap between the inner sleeve and the spool, and the gap between the inner sleeve and the spool can be prevented from expanding. It is possible to suppress an increase in the amount of hydraulic oil that leaks. Therefore, even in a configuration in which a minimum radial gap between the inner sleeve and the spool, which can suppress deterioration of spool slidability, can be suppressed, an increase in hydraulic oil leakage amount can be suppressed, so that spool slidability deteriorates. It is possible to suppress an increase in the amount of hydraulic oil leakage while suppressing it.

This disclosure can also be realized in various forms. For example, it can be realized in the form of a method for manufacturing a hydraulic oil control valve, a valve timing adjusting device including a hydraulic oil control valve, a method for manufacturing such a valve timing adjusting device, and the like.

The above objectives and other objectives, features and advantages of the present disclosure will be clarified by the following detailed description with reference to the accompanying drawings. The drawing is
FIG. 1 is a cross-sectional view showing a schematic configuration of a valve timing adjusting device including the hydraulic oil control valve of the first embodiment. FIG. 2 is a cross-sectional view showing a cross section taken along the line II-II of FIG. FIG. 3 is a cross-sectional view showing a detailed configuration of the hydraulic oil control valve. FIG. 4 is an exploded perspective view showing the detailed configuration of the hydraulic oil control valve in an exploded manner. FIG. 5 is a cross-sectional view showing a state in which the spool is in contact with the stopper. FIG. 6 is a cross-sectional view showing a state in which the spool is located substantially in the center of the sliding range. FIG. 7 is a cross-sectional view showing a schematic configuration of the hydraulic oil control valve of another embodiment 3.

A. First Embodiment:
A-1. Device configuration:
The valve timing adjusting device 100 shown in FIG. 1 adjusts the valve timing of a valve driven to open and close by a camshaft 320 to which power is transmitted from a crankshaft 310 in an internal combustion engine 300 included in a vehicle (not shown). The valve timing adjusting device 100 is provided in the power transmission path from the crankshaft 310 to the camshaft 320. More specifically, the valve timing adjusting device 100 is fixedly arranged at the end portion 321 of the cam shaft 320 in the direction along the rotation axis AX of the cam shaft 320 (hereinafter, also referred to as “axial direction AD”). .. The rotation shaft AX of the valve timing adjusting device 100 substantially coincides with the rotation shaft AX of the cam shaft 320. The valve timing adjusting device 100 of the present embodiment adjusts the valve timing of the intake valve 330 among the intake valve 330 and the exhaust valve 340 as valves.

A shaft hole portion 322 and a supply hole portion 326 are formed at the end portion 321 of the cam shaft 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, which will be described later, is formed on the inner peripheral surface of the shaft hole portion 322. A female screw portion 324 is formed on the shaft fixing portion 323. The female screw portion 324 is screwed with the male screw portion 33 formed in the fixing portion 32 of the hydraulic oil control valve 10. The supply hole portion 326 is formed in the radial direction and communicates the outer peripheral surface of the cam shaft 320 with the shaft hole portion 322. Hydraulic oil is supplied to the supply hole portion 326 from the hydraulic oil supply source 350. The hydraulic oil supply source 350 has an oil pump 351 and an oil pan 352. The oil pump 351 pumps the hydraulic oil stored in the oil pan 352.

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

As shown in FIG. 1, the housing 120 has a sprocket 121 and a case 122. The sprocket 121 is fitted to the end 321 of the cam shaft 320 and is rotatably supported. The sprocket 121 is formed with a fitting recess 128 at a position corresponding to the lock pin 150 described later. An annular 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 case 122 by a plurality of bolts 129. Therefore, the housing 120 rotates in conjunction with the crankshaft 310. The case 122 has a bottomed tubular appearance shape, and the opening end is closed by the sprocket 121. As shown in FIG. 2, the case 122 has a plurality of partition walls 123 formed side by side in the circumferential direction toward the inside in the radial direction. The partition walls 123 adjacent to each other in the circumferential direction function as hydraulic chambers 140, respectively. As shown in FIG. 1, an opening 124 is formed in the central portion of the bottom of the case 122.

The vane rotor 130 is housed inside the housing 120 and rotates relative to the housing 120 in the retard or advance 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 vane rotor 130 has a plurality of vanes 131 and a boss 135.

As shown in FIG. 2, the plurality of vanes 131 project radially outward from the boss 135 located at the center of the vane rotor 130, and are formed side by side in the circumferential direction. Each vane 131 is housed in each hydraulic chamber 140, and each hydraulic chamber 140 is divided into a retard chamber 141 and an advance chamber 142 in the circumferential direction. The retard chamber 141 is located on one side in the circumferential direction with respect to the vane 131. The advance chamber 142 is located on the other side of the vane 131 in the circumferential direction. A housing hole 132 is formed in one of the plurality of vanes 131 in the axial direction. The accommodating hole 132 communicates with the retard chamber 141 via the retard chamber side pin control oil passage 133 formed in the vane 131, and communicates with the advance chamber 142 via the advance chamber side pin control oil passage 134. are doing. A lock pin 150 capable of reciprocating in the axial direction AD is arranged in the accommodating hole 132. The lock pin 150 regulates the relative rotation of the vane rotor 130 with respect to the housing 120 and prevents the housing 120 and the vane rotor 130 from colliding in the circumferential direction when the hydraulic pressure is insufficient. The lock pin 150 is urged in the axial direction AD toward the fitting recess 128 formed in the sprocket 121 by the spring 151.

The boss 135 has a tubular appearance shape and is fixed to the end portion 321 of the cam shaft 320. Therefore, the vane rotor 130 on which the boss 135 is formed is fixed to the end portion 321 of the cam shaft 320 and rotates integrally with the cam shaft 320. A through hole 136 penetrating in the axial direction AD is formed in the central portion of the boss 135. A hydraulic oil control valve 10 is arranged in the through hole 136. A plurality of retard angle oil passages 137 and a plurality of advance angle oil passages 138 are formed in the boss 135 so as to penetrate in the radial direction. Each retarded oil passage 137 and each advanced angle oil passage 138 are formed side by side in the axial direction AD. Each retarded oil passage 137 communicates the retarded port 27 of the hydraulic oil control valve 10, which will be described later, with the retarded chamber 141. Each advance angle oil passage 138 communicates the advance angle port 28 of the hydraulic oil control valve 10, which will be described later, with the advance angle chamber 142. In the through hole 136, each retard oil passage 137 and each advance angle oil passage 138 are sealed by an outer sleeve 30 of a hydraulic oil control valve 10 described later.

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

As shown in FIG. 1, the hydraulic oil control valve 10 is arranged and used on the rotary shaft AX of the valve timing adjusting device 100, and controls the flow of hydraulic oil supplied from the hydraulic oil supply source 350. The operation of the hydraulic oil control valve 10 is controlled by 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 arranged on the side opposite to the cam shaft 320 side in the axial direction AD. The solenoid 160 has an electromagnetic unit 162 and a shaft 164. The solenoid 160 displaces the shaft 164 in the axial direction AD by energizing the electromagnetic unit 162 according to the instruction of the ECU described above, thereby causing the spool 50 of the hydraulic oil control valve 10 described later to resist the urging force of the spring 60. Presses toward the cam shaft 320 side. As will be described later, the spool 50 slides in the axial direction AD by pressing, so that the oil passage communicating with the retard chamber 141 and the oil passage communicating with the advance chamber 142 can be switched.

As shown in FIGS. 3 and 4, the hydraulic oil control valve 10 includes a sleeve 20, a spool 50, a spring 60, a fixing member 70, and a check valve 90. Note that FIG. 3 shows a cross section along the rotation axis AX.

The sleeve 20 has an outer sleeve 30 and an inner sleeve 40. Both the outer sleeve 30 and the inner sleeve 40 have a substantially tubular appearance shape. The sleeve 20 has a schematic configuration in which the inner sleeve 40 is inserted into the shaft hole 34 formed in the outer sleeve 30.

The outer sleeve 30 constitutes the outer shell of the hydraulic oil control valve 10 and is arranged on the outer side in the radial direction of the inner sleeve 40. The outer sleeve 30 has a main body portion 31, a fixing portion 32, a protruding portion 35, a diameter-expanding portion 36, a movement restricting portion 80, and a tool engaging portion 38. A shaft hole 34 along the axial direction AD is formed in the main body portion 31 and the fixed portion 32. The shaft hole 34 is formed so as to penetrate the outer sleeve 30 in the axial direction AD.

The main body 31 has a tubular external shape and is arranged in the through hole 136 of the vane 131 as shown in FIG. As shown in FIG. 4, a plurality of outer retard angle ports 21 and a plurality of outer advance angle ports 22 are formed in the main body 31. The plurality of outer retard angle ports 21 are formed side by side in the circumferential direction, and each communicates the outer peripheral surface of the main body 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 port 21 in the axial direction AD. The plurality of outer advance angle ports 22 are formed side by side in the circumferential direction, and each communicates the outer peripheral surface of the main body 31 with the shaft hole 34.

The fixed portion 32 has a tubular appearance shape, and is formed so as to be connected to the main body portion 31 in the axial direction AD. The fixing portion 32 is formed to have substantially the same diameter as the main body portion 31, and is inserted into the shaft fixing portion 323 of the cam shaft 320 as shown in FIG. A male screw portion 33 is formed on the fixing portion 32. The male screw portion 33 is screwed with the female screw portion 324 formed on the shaft fixing portion 323. The outer sleeve 30 is configured so that it can be fixed to the end portion 321 of the cam shaft 320 by applying an axial force in the axial direction AD toward the cam shaft 320 side by fastening the male screw portion 33 and the female screw portion 324. By applying axial force and fixing, it is possible to prevent the hydraulic oil control valve 10 and the end 321 of the cam shaft 320 from being displaced due to the eccentric force of the cam shaft 320 by pushing the intake valve 330, and the hydraulic oil Leakage can be suppressed.

The protruding portion 35 is formed so as to protrude outward in the radial direction from the main body portion 31. As shown in FIG. 1, the protruding portion 35 sandwiches the vane rotor 130 with the end portion 321 of the cam shaft 320 in the axial direction AD.

As shown in FIG. 3, a diameter-expanded portion 36 is formed at the end of the main body 31 on the solenoid 160 side. The diameter-expanded portion 36 is formed so that the inner diameter is enlarged as compared with other portions of the main body portion 31. The flange portion 46 of the inner sleeve 40, which will be described later, is arranged in the enlarged diameter portion 36.

The movement restricting portion 80 is configured as a step in the radial direction formed by the enlarged diameter portion 36 on the inner peripheral surface of the outer sleeve 30. The movement restricting portion 80 sandwiches the flange portion 46 of the inner sleeve 40, which will be described later, with the fixing member 70 in the axial direction AD. As a result, the movement restricting unit 80 restricts the movement of the inner sleeve 40 in the direction away from the electromagnetic unit 162 of the solenoid 160 along the axial direction AD.

The tool engaging portion 38 is formed on the solenoid 160 side of the protruding portion 35 in the axial direction AD. The tool engaging portion 38 is configured to be engageable with a tool such as a hexagon socket (not shown), and is used for fastening and fixing the hydraulic oil control valve 10 including the outer sleeve 30 to the end portion 321 of the cam shaft 320.

The inner sleeve 40 has a tubular portion 41, a bottom portion 42, a plurality of retard side protrusion walls 43, a plurality of advance angle side protrusion walls 44, a sealing wall 45, a flange portion 46, and a stopper 49. ..

The tubular portion 41 has a substantially tubular external shape, and is located inside the outer sleeve 30 in the radial direction over the main body portion 31 and the fixing portion 32 of the outer sleeve 30. As shown in FIGS. 3 and 4, the tubular portion 41 is formed with a retard side supply port SP1, an advance angle side supply port SP2, and a recycling port 47, respectively. The retard angle side supply port SP1 is formed on the bottom portion 42 side of the retard angle side protruding wall 43 in the axial direction AD, and communicates the outer peripheral surface and the inner peripheral surface of the tubular portion 41. In the present embodiment, a plurality of retard angle side supply ports SP1 are formed side by side over a half circumference in the circumferential direction, but may be formed over the entire circumference or may be a single number. The advance angle side supply port SP2 is formed on the solenoid 160 side of the advance angle side protrusion wall 44 in the axial direction AD, and communicates the outer peripheral surface and the inner peripheral surface of the tubular portion 41. In the present embodiment, a plurality of advance angle side supply ports SP2 are formed side by side over a half circumference in the circumferential direction, but may be formed over the entire circumference or may be a single number. The retard side supply port SP1 and the advance angle side supply port SP2 communicate with each other with the shaft hole portion 322 of the camshaft 320 shown in FIG. As shown in FIGS. 3 and 4, the recycling port 47 is formed between the retard side protruding wall 43 and the advance side protruding wall 44 in the axial direction AD, and forms the outer peripheral surface and the inner peripheral surface of the tubular portion 41. I'm communicating. The recycle port 47 communicates with the retard side supply port SP1 and the advance angle side supply port SP2, respectively. Specifically, the recycling port 47 is a space between the inner peripheral surface of the main body 31 of the outer sleeve 30 and the outer peripheral surface of the tubular portion 41 of the inner sleeve 40, and is a retarded side adjacent to each other in the circumferential direction. The spaces between the projecting walls 43 and the advancing side projecting walls 44 adjacent to each other in the circumferential direction communicate with the supply ports SP1 and SP2. Therefore, the recycling port 47 functions as a recycling 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, a plurality of recycling ports 47 are formed side by side in the circumferential direction, but may be a single number. The operation of the valve timing adjusting device 100 including the operation of switching the oil passage by sliding the spool 50 will be described later.

As shown in FIG. 3, the bottom portion 42 is formed integrally with the tubular portion 41 and is opposite to the solenoid 160 side in the axial direction AD of the tubular portion 41 (hereinafter, also referred to as “camshaft 320 side” for convenience of explanation). It is blocking the end of the. One end of the spring 60 is in contact with the bottom portion 42.

As shown in FIG. 4, the plurality of retard angle side projecting walls 43 are formed side by side in the circumferential direction so as to project radially outward from the tubular portion 41. The retarded-angle side protruding walls 43 adjacent to each other in the circumferential direction communicate with the shaft hole portion 322 of the cam shaft 320 shown in FIG. 1, and the hydraulic oil supplied from the hydraulic oil supply source 350 flows through. As shown in FIGS. 3 and 4, an inner retard angle port 23 is formed on each retard angle side projecting wall 43. Each inner retard angle port 23 communicates with the outer peripheral surface and the inner peripheral surface of the retard angle side protruding wall 43, respectively. As shown in FIG. 3, each inner retard angle port 23 communicates with each outer retard angle port 21 formed on the outer sleeve 30. The axis of the inner retard port 23 deviates from the axis of the outer retard port 21 in the axial direction AD.

As shown in FIG. 4, each of the plurality of advance angle side protrusion walls 44 is formed on the solenoid 160 side of the retard angle side protrusion wall 43 in the axial direction AD. The plurality of advance angle side projecting walls 44 are formed so as to project radially outward from the tubular portion 41 so as to be arranged side by side in the circumferential direction. The advance angle side protruding walls 44 adjacent to each other in the circumferential direction communicate with the shaft hole portion 322 shown in FIG. 1, and the hydraulic oil supplied from the hydraulic oil supply source 350 flows through. As shown in FIGS. 3 and 4, an inner advance port 24 is formed on each advance side protruding wall 44. Each inner advance port 24 communicates the outer peripheral surface and the inner peripheral surface of the advance side protruding wall 44, respectively. As shown in FIG. 3, each inner advance port 24 communicates with each outer advance port 22 formed on the outer sleeve 30. The axis of the inner advance port 24 is deviated from the axis of the outer advance port 22 in the axial direction AD.

The sealing wall 45 is formed so as to project outward in the radial direction over the entire circumference of the tubular portion 41 on the solenoid 160 side of the advance angle side supply port SP2 in the axial direction AD. The sealing wall 45 seals the inner peripheral surface of the main body 31 of the outer sleeve 30 and the outer peripheral surface of the tubular portion 41 of the inner sleeve 40, so that the hydraulic oil flowing through the hydraulic oil supply oil passage 25 described later is a solenoid. Suppresses leakage to the 160 side. The outer diameter of the sealing wall 45 is formed to be substantially the same as the outer diameter of the retard side protruding wall 43 and the advance side protruding wall 44.

The collar portion 46 is formed at the end of the inner sleeve 40 on the solenoid 160 side so as to project outward in the radial direction over the entire circumference of the tubular portion 41. The collar portion 46 is arranged in 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 collar portion 46. The plurality of fitting portions 48 are formed side by side in the circumferential direction at the outer edge portion of the flange portion 46. In the present embodiment, each fitting portion 48 is formed by cutting off the outer edge portion of the flange portion 46 in a straight line, but the fitting portion 48 may be formed not only in a straight line but also in a curved shape. Each fitting portion 48 is fitted with each fitting protrusion 73 of the fixing member 70, which will be described later.

The stopper 49 shown in FIG. 3 is an end portion of the inner sleeve 40 in the axial direction AD and is formed at the end portion on the camshaft 320 side. The stopper 49 is formed so that the inner diameter is smaller than that of the other portion of the tubular portion 41 so that the end portion of the spool 50 on the camshaft 320 side can be brought into contact with the stopper 49. The stopper 49 defines the sliding limit of the spool 50 in the direction away from the electromagnetic portion 162 of the solenoid 160.

The space between the shaft hole 34 formed in the outer sleeve 30 and the inner sleeve 40 functions as a hydraulic oil supply oil passage 25. The hydraulic oil supply oil passage 25 communicates with the shaft hole portion 322 of the camshaft 320 shown in FIG. 1, and supplies hydraulic oil supplied from the hydraulic oil supply source 350 to the retard side supply port SP1 and the advance angle side supply port. Lead to SP2. As shown in FIG. 3, the outer retard angle port 21 and the inner retard angle port 23 form a retard angle port 27 and communicate with the retard angle chamber 141 via the retard angle oil passage 137 shown in FIG. As shown in FIG. 3, the outer advance angle port 22 and the inner advance angle port 24 form an advance angle port 28, and communicate with the advance angle chamber 142 via the advance angle oil passage 138 shown in FIG.

As shown in FIG. 3, the outer sleeve 30 and the inner sleeve 40 are sealed at least in a part of the axial AD in order to suppress leakage of hydraulic oil. More specifically, the retard side protrusion wall 43 seals between the retard side supply port SP1 and the recycling port 47 and the retard port 27, and the advance side protrusion wall 44 seals the advance angle side supply port SP2. And between the recycle port 47 and the advance port 28 is sealed. Further, the sealing wall 45 seals the hydraulic oil supply oil passage 25 and the outside of the hydraulic oil control valve 10. That is, in the axial direction AD, the range from the retard side protruding wall 43 to the sealing wall 45 is set as the sealing range SA. In the seal range SA, the radial gap between the outer sleeve 30 and the inner sleeve 40 is minimized. Further, in the present embodiment, the inner diameter of the main body 31 of the outer sleeve 30 is configured to be substantially constant in the seal range SA.

The spool 50 is arranged inside the inner sleeve 40 in the radial direction. The spool 50 is driven by a solenoid 160 arranged in contact with one end of the spool 50 and slides in the axial direction AD. The spool 50 has a spool cylinder portion 51, a spool bottom portion 52, and a spring receiving portion 56. Further, the spool 50 is formed with at least a part of the drain oil passage 53, a drain inflow portion 54, and a drain outflow portion 55.

The spool cylinder portion 51 has a substantially tubular appearance shape. On the outer peripheral surface of the spool cylinder portion 51, a retard side seal portion 57, an advance angle side seal portion 58, and a locking portion 59 are arranged in this order from the camshaft 320 side in the axial direction AD, respectively, in the radial direction. It protrudes outward and is formed over the entire circumference. The retard side seal portion 57 and the advance angle side seal portion 58 seal a part of the ports SP1, SP2, 27, 28, and 47 according to the sliding position of the spool 50, respectively. More specifically, the retard angle side seal portion 57 cuts off the communication between the recycle port 47 and the retard angle port 27 in a state where the spool 50 is closest to the electromagnetic portion 162 of the solenoid 160 as shown in FIG. As shown in FIG. 5, when the spool 50 is farthest from the electromagnetic unit 162, the communication between the retard angle side supply port SP1 and the retard angle port 27 is cut off. As shown in FIG. 3, the advance angle side seal portion 58 cuts off the communication between the advance angle side supply port SP2 and the advance angle port 28 in a state where the spool 50 is closest to the electromagnetic portion 162, and as shown in FIG. When the spool 50 is farthest from the electromagnetic unit 162, the communication between the recycle port 47 and the advance angle port 28 is cut off. "Cut off communication" is equivalent to sealing. The radial gap between the inner sleeve 40 and the spool 50 is minimized in the portion where such sealing property is required. Since different portions along the axial AD are sealed according to the stroke of the spool 50, the sealing lengths of the portions required for such sealing properties along the axial AD are shorter than the stroke of the spool 50. Here, the "stroke of the spool 50" means the length of movement from the position where the spool is closest to the electromagnetic portion 162 of the solenoid 160 to the position where it is farthest away. As shown in FIG. 3, the locking portion 59 defines the sliding limit of the spool 50 in the direction of approaching the electromagnetic portion 162 of the solenoid 160 by abutting against the fixing member 70.

The spool bottom portion 52 is integrally formed with the spool cylinder portion 51, and closes the end portion of the spool cylinder portion 51 on the solenoid 160 side. The spool bottom portion 52 is configured to be able to project toward the solenoid 160 side from the sleeve 20 in the axial direction AD. The spool bottom portion 52 functions as a base end portion of the spool 50.

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

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

The drain outflow portion 55 is formed so as to open radially outward at the spool bottom portion 52, which is one end of the spool 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 hydraulic oil discharged from the drain outflow portion 55 is collected in the oil pan 352.

As shown in FIG. 3, the spring receiving portion 56 is formed at the end portion of the spool cylinder portion 51 on the camshaft 320 side with an inner diameter enlarged as compared with the other portion of the spool cylinder portion 51. The other end of the spring 60 is brought into contact with the spring receiving portion 56.

In the present embodiment, the outer sleeve 30 and the spool 50 are each made of iron, and the inner sleeve 40 is made of aluminum. Therefore, the coefficient of linear expansion of the inner sleeve 40 is larger than the coefficient of linear expansion of the outer sleeve 30 and the spool 50. Further, the outer sleeve 30 and the spool 50 are harder than the inner sleeve 40. Such hardness may be defined by the hardness measured by using an arbitrary hardness measuring method such as Rockwell hardness and Vickers hardness.

The spring 60 is composed of a compression coil spring, and its end is arranged in contact with the bottom 42 of the inner sleeve 40 and the spring receiving portion 56 of the spool 50, respectively. The spring 60 urges the spool 50 toward the solenoid 160 along 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 protrusions 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 in the substantially center of the flat plate portion 71. As shown in FIG. 3, the spool bottom 52, which is one end of the spool 50, is inserted into the opening 72.

As shown in FIG. 4, the plurality of fitting protrusions 73 project from the flat plate portion 71 in the axial direction AD, and are formed side by side in the circumferential direction. The fitting protrusion 73 is not limited to the axial direction AD, and may be formed so as to protrude in any direction intersecting the radial direction. Each fitting protrusion 73 fits with each fitting portion 48 of the inner sleeve 40, respectively.

As shown in FIG. 3, the fixing member 70 is assembled so that the spool 50 is inserted into the inner sleeve 40 and the fitting protrusion 73 and the fitting portion 48 are fitted, and then the outer sleeve 30 is assembled. It is fixed by caulking. The outer edge portion of the end surface of the fixing member 70 on the solenoid 160 side functions as a caulking portion to be caulked and fixed to the outer sleeve 30.

By fixing the fixing member 70 to the outer sleeve 30 in a state where the fitting protrusion 73 and the fitting portion 48 are fitted, the inner sleeve 40 is restricted from rotating in the circumferential direction with respect to the outer sleeve 30. To. Further, by fixing the fixing member 70 to the outer sleeve 30, the inner sleeve 40 and the spool 50 are restricted from coming off from the outer sleeve 30 to the solenoid 160 side in the axial direction AD.

The check valve 90 suppresses the backflow of hydraulic oil. The check valve 90 includes two supply check valves 91 and a recycling check valve 92. As shown in FIG. 4, each supply check valve 91 and a recycling check valve 92 are elastically deformed in the radial direction by being formed by winding a strip-shaped thin plate in an annular shape. As shown in FIG. 3, each supply check valve 91 is arranged in contact with the inner peripheral surface of the tubular portion 41 at a position corresponding to the retard side supply port SP1 and the advance angle side supply port SP2. Each supply check valve 91 receives the pressure of the hydraulic oil from the outside in the radial direction, so that the overlapping portion of the strip-shaped thin plates becomes large and shrinks in the radial direction. The recycle check valve 92 is arranged in contact with the outer peripheral surface of the tubular portion 41 at a position corresponding to the recycle port 47. The recycle check valve 92 receives the pressure of the hydraulic oil from the inside in the radial direction, so that the overlapping portion of the strip-shaped thin plates becomes small and expands in the radial direction.

In the hydraulic oil control valve 10 of the present embodiment, when the fixing portion 32 is screwed into the shaft fixing portion 323, an axial force in the axial direction AD toward the cam shaft 320 side is applied to the end portion 321 of the cam shaft 320. Is fixed to. The outer sleeve 30 elastically deforms due to the applied axial force and shrinks in the radial direction. Therefore, it is necessary to secure a radial gap capable of suppressing deterioration of the slidability of the spool 50.

In the present embodiment, the diameter between the outer sleeve 30 and the inner sleeve 40 is not applied to the outer sleeve 30, that is, before the hydraulic oil control valve 10 is fixed to the cam shaft 320. The minimum clearance CL1, which is the minimum value of the directional clearance, is designed to be larger than the minimum clearance CL2, which is the minimum value of the radial clearance between the inner sleeve 40 and the spool 50. More specifically, the radial direction between the inner peripheral surface of the main body 31 of the outer sleeve 30 and the outer peripheral surface of the retard side protruding wall 43, the advance angle side protruding wall 44 and the sealing wall 45 of the inner sleeve 40. The minimum gap CL1 is in the radial direction between the inner peripheral surface of the tubular portion 41 of the inner sleeve 40 and the outer peripheral surfaces of the retard side seal portion 57, the advance angle side seal portion 58 and the locking portion 59 of the spool 50. It is set larger than the minimum gap CL2. The reason for such a setting will be described below.

In the hydraulic oil control valve 10 of the present embodiment, different parts along the axial direction AD are sealed according to the stroke of the spool 50. Therefore, the length along the axial AD in the minimum radial gap CL2 between the inner sleeve 40 and the spool 50 is shorter than the stroke of the spool 50. Therefore, hydraulic oil leaks easily from the minimum gap CL2. Further, the inner sleeve 40 does not move relative to the outer sleeve 30 in the axial direction AD. Therefore, the length along the axial AD in the minimum radial gap CL1 between the outer sleeve 30 and the inner sleeve 40 is set to be relatively long. Therefore, leakage of hydraulic oil is unlikely to occur from the minimum gap CL1. Therefore, by setting the minimum gap CL1 in which hydraulic oil leakage is unlikely to occur larger than the minimum gap CL2 in which hydraulic oil leakage is likely to occur, the deterioration of the slidability of the spool 50 can be suppressed in the radial direction. When a gap is secured, an increase in the amount of hydraulic oil leakage can be suppressed as compared with a configuration in which the magnitude relationship of the gap in the radial direction is different from that of the present embodiment.

In the present embodiment, the magnitude relationship between the minimum clearance CL1 and the minimum clearance CL2 is maintained even in a state where an axial force is applied to the outer sleeve 30 and the camshaft 320 is fixed to the end portion 321.

In the present embodiment, the crankshaft 310 corresponds to the subordinate concept of the drive shaft in the present disclosure, the camshaft 320 corresponds to the subordinate concept of the driven shaft in the present disclosure, and the intake valve 330 corresponds to the subordinate concept of the valve in the present disclosure. Corresponds to the concept. Further, the solenoid 160 corresponds to the subordinate concept of the actuator in the present disclosure.

A-2. Operation of valve timing adjuster:
As shown in FIG. 1, the hydraulic oil supplied from the hydraulic oil supply source 350 to the supply hole portion 326 flows to the hydraulic oil supply oil passage 25 through the shaft hole portion 322. As shown in FIG. 3, the retard angle port 27 communicates with the retard angle side supply port SP1 in a state where the solenoid 160 is not energized and the spool 50 is closest to the electromagnetic portion 162 of the solenoid 160. As a result, the hydraulic oil in the hydraulic oil supply oil 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 rotation phase of the cam shaft 320 with respect to the crankshaft 310. Changes to the retard side. Further, in this state, the advance angle port 28 does not communicate with the advance angle side supply port SP2, but communicates with the recycle port 47. As a result, the hydraulic oil discharged from the advance chamber 142 is returned to the retard side supply port SP1 via the recycling port 47 and recirculated. Further, a part of the hydraulic oil discharged from the advance chamber 142 flows into the drain oil passage 53 through the drain inflow portion 54, and is returned to the oil pan 352 through the drain outflow portion 55.

As shown in FIG. 5, when the solenoid 160 is energized and the spool 50 is farthest from the electromagnetic portion 162 of the solenoid 160, that is, when the spool 50 is in contact with the stopper 49, the advance port 28 is set. It communicates with the advance side supply port SP2. As a result, the hydraulic oil in the hydraulic oil supply oil 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 rotation phase of the cam shaft 320 with respect to the crankshaft 310. Changes to the advance side. Further, in this state, the retard angle port 27 does not communicate with the retard angle side supply port SP1 but communicates with the recycling port 47. As a result, the hydraulic oil discharged from the retarded chamber 141 is returned to the advancing side supply port SP2 via the recycling port 47 and recirculated. Further, a part of the hydraulic oil discharged from the retarded chamber 141 flows into the drain oil passage 53 through the drain inflow section 54, and is returned to the oil pan 352 through the drain outflow section 55.

Further, as shown in FIG. 6, when the solenoid 160 is energized and the spool 50 is located substantially in the center of the sliding range, the retard angle port 27 and the retard angle side supply port SP1 communicate with each other and advance. The port 28 and the advance side supply port SP2 communicate with each other. As a result, the hydraulic oil in the hydraulic oil supply passage 25 is supplied to both the retard chamber 141 and the advance chamber 142, the relative rotation of the vane rotor 130 with respect to the housing 120 is suppressed, and the cam shaft 320 with respect to the crankshaft 310 is suppressed. The relative rotation phase of is maintained.

The hydraulic oil supplied to the retard chamber 141 or the advance chamber 142 flows into the accommodating hole 132 via the retard chamber side pin control oil passage 133 or the advance chamber side pin control oil passage 134. Therefore, sufficient hydraulic pressure is applied to the retard chamber 141 or the advance chamber 142, and the lock pin 150 escapes from the fitting recess 128 against the urging force of the spring 151 by the hydraulic oil flowing into the accommodating hole 132. Then, the relative rotation of the vane rotor 130 with respect to the housing 120 is allowed.

When the relative rotation phase of the camshaft 320 is on the advance side of the target value, the valve timing adjusting device 100 retards the vane rotor 130 with respect to the housing 120 by relatively reducing the amount of electricity supplied to the solenoid 160. Rotate relative to the direction. As a result, the relative rotation phase of the camshaft 320 with respect to the crankshaft 310 changes to the retard side, and the valve timing is retarded. Further, in the valve timing adjusting device 100, when the relative rotation phase of the cam shaft 320 is on the retard side of the target value, the vane rotor 130 is attached to the housing 120 by relatively increasing the amount of electricity supplied to the solenoid 160. Relative rotation in the advance direction. As a result, the relative rotation phase of the cam shaft 320 with respect to the crank shaft 310 changes to the advance angle side, and the valve timing advances. Further, when the relative rotation phase of the camshaft 320 matches the target value, the valve timing adjusting device 100 suppresses the relative rotation of the vane rotor 130 with respect to the housing 120 by setting the amount of energization to the solenoid 160 to a medium level. As a result, the relative rotation phase of the camshaft 320 with respect to the crankshaft 310 is maintained, and the valve timing is maintained.

According to the hydraulic oil control valve 10 provided in the valve timing adjusting device 100 of the first embodiment described above, the minimum radial gap between the outer sleeve 30 and the inner sleeve 40 is not applied. CL1 is larger than the minimum radial clearance CL2 between the inner sleeve 40 and the spool 50. Here, in the hydraulic oil control valve 10 of the present embodiment, different portions along the axial direction AD are sealed according to the stroke of the spool 50. Therefore, the length along the axial AD in the minimum radial gap CL2 between the inner sleeve 40 and the spool 50 is shorter than the stroke of the spool 50. Therefore, hydraulic oil leaks easily from the minimum radial gap CL2 between the inner sleeve 40 and the spool 50. Further, the inner sleeve 40 does not move relative to the outer sleeve 30 in the axial direction AD. Therefore, the length along the axial AD in the minimum radial gap CL1 between the outer sleeve 30 and the inner sleeve 40 is set to be relatively long. Therefore, leakage of hydraulic oil is unlikely to occur from the minimum radial gap CL1 between the outer sleeve 30 and the inner sleeve 40. Therefore, by setting the minimum clearance CL1 in which hydraulic oil leakage is unlikely to occur larger than the minimum clearance CL2 in which hydraulic oil leakage is likely to occur, the outer is caused by the axial force for fixing the hydraulic oil control valve 10. When a radial gap that can suppress deterioration of the slidability of the spool 50 is secured even if the sleeve 30 is elastically deformed and reduced in the radial direction, the magnitude relationship of the radial gap is different from that of the present embodiment. It is possible to suppress an increase in the amount of hydraulic oil leakage as compared with the configuration. Therefore, it is possible to suppress an increase in the amount of hydraulic oil leakage while suppressing deterioration of the slidability of the spool 50.

Further, since the increase in the amount of hydraulic oil leakage is suppressed by appropriately allocating the total value of the sizes of the minimum gap CL1 and the minimum gap CL2 to the minimum gap CL1 and the minimum gap CL2, the outer sleeve 30 and the inner sleeve Compared with a configuration in which a sealing material or the like for suppressing leakage of hydraulic oil is arranged in the minimum clearance CL1 in the radial direction with 40, an increase in the number of parts can be suppressed and an increase in the assembly process can be suppressed. Therefore, it is possible to suppress an increase in the cost required for manufacturing the hydraulic oil control valve 10. Further, since the sealing material or the like can be omitted, it is possible to suppress deterioration of the slidability of the spool 50 due to the protrusion of the sealing material or the like.

Further, since the coefficient of linear expansion of the inner sleeve 40 is larger than the coefficient of linear expansion of the outer sleeve 30, the outer sleeve 30 and the inner sleeve 40 are caused by the temperature rise of the hydraulic oil control valve 10 when the valve timing adjusting device 100 is driven. The minimum clearance CL1 in the radial direction with and can be reduced. Therefore, it is possible to further suppress an increase in the amount of hydraulic oil leaking from the minimum gap CL1.

Further, since the outer sleeve 30 is harder than the inner sleeve 40, the workability of the inner sleeve 40 can be improved while ensuring the fixing strength of the outer sleeve 30 to the end portion 321 of the cam shaft 320. Therefore, the workability of the ports SP1, SP2, 27, 28, 47 of the sleeve 20 can be improved, and it is possible to suppress the complexity of the manufacturing process for forming the ports SP1, SP2, 27, 28, 47. , The increase in manufacturing cost can be suppressed.

Further, since the outer sleeve 30 is made of iron and the inner sleeve 40 is made of aluminum, the linear expansion coefficient of the inner sleeve 40 is larger than the linear expansion coefficient of the outer sleeve 30, and the outer sleeve 30 is the inner sleeve. A configuration harder than 40 can be easily realized at the same time.

Further, since the sleeve 20 has a double structure of the outer sleeve 30 and the inner sleeve 40, the hydraulic oil supply oil passage 25 can be easily realized by the radial gap between the outer sleeve 30 and the inner sleeve 40. Therefore, it is possible to suppress the application of hydraulic pressure to the spool 50 due to the supply of hydraulic oil, and it is possible to suppress deterioration of the slidability of the spool 50. Further, since the sleeve 20 has a double structure, the workability of each port SP1, SP2, 27, 28, 47 can be improved, and the manufacturing process can be suppressed from becoming complicated. Further, since such workability can be improved, the degree of freedom in designing each port SP1, SP2, 27, 28, 47 can be improved, and the mountability of the hydraulic oil control valve 10 and the valve timing adjusting device 100 can be improved.

B. Second embodiment:
The hydraulic oil control valve 10 of the second embodiment is different from the hydraulic oil control valve of the first embodiment in the dimensional relationship between the minimum clearance CL1 and the minimum clearance CL2. Since the other configurations are the same as those in the first embodiment, the same configurations are designated by the same reference numerals, and detailed description thereof will be omitted.

When the hydraulic oil control valve 10 of the second embodiment is fastened to the end portion 321 of the cam shaft 320, the outer sleeve 30 elastically deforms due to the application of axial force and shrinks in the radial direction, and the outer sleeve 30 and the outer sleeve 30 The inner sleeve 40 comes into contact with the inner sleeve 40 in the radial direction. In other words, the minimum radial clearance CL1 between the outer sleeve 30 and the inner sleeve 40 becomes zero by fastening the outer sleeve 30. Therefore, it is possible to suppress an increase in hydraulic oil leaking from the minimum radial gap CL1 between the outer sleeve 30 and the inner sleeve 40.

Further, also in the hydraulic oil control valve 10 of the second embodiment, the outer sleeve 30 and the spool 50 are each formed of iron and the inner sleeve 40 is formed of aluminum, as in the hydraulic oil control valve 10 of the first embodiment. Has been done. Therefore, the coefficient of linear expansion of the inner sleeve 40 is larger than the coefficient of linear expansion of the outer sleeve 30, and the inner sleeve 40 thermally expands more than the outer sleeve 30. However, when the temperature of the hydraulic oil control valve 10 rises due to the drive of the valve timing adjusting device 100, the outer sleeve 30 and the inner sleeve 40 are already in radial contact with each other, so that the inner sleeve 40 is in the radial direction. Expansion is suppressed. Therefore, it is possible to suppress the expansion of the minimum radial clearance CL2 between the inner sleeve 40 and the spool 50 as the temperature of the hydraulic oil control valve 10 rises, and the amount of hydraulic oil leaking from the minimum clearance CL2 increases. Can be suppressed. Further, since the linear expansion coefficient of the spool 50 is the same as the linear expansion coefficient of the outer sleeve 30, it is possible to suppress a change in the size of the minimum gap CL2 due to the temperature rise of the hydraulic oil control valve 10. Therefore, deterioration of the slidability of the spool 50 can be suppressed. The phrase "the coefficient of linear expansion of the spool 50 is equivalent to the coefficient of linear expansion of the outer sleeve 30" is not limited to the case where the coefficient of linear expansion of the spool 50 matches the coefficient of linear expansion of the outer sleeve 30, for example, the outer sleeve 30. The coefficient of linear expansion of the spool 50 may be in the range of plus or minus about 20% or less based on the coefficient of linear expansion of. Further, since the linear expansion coefficient of the spool 50 is smaller than the linear expansion coefficient of the inner sleeve 40, it is possible to prevent the minimum gap CL2 from being excessively reduced as the temperature of the hydraulic oil control valve 10 rises, and the spool 50 slides. The deterioration of sexuality can be suppressed.

In the present embodiment, the state in which the outer sleeve 30 is fastened to the end portion 321 of the cam shaft 320 is a subordinate concept of the present disclosure in which the predetermined conditions including the application of the axial force are satisfied. Equivalent to.

According to the hydraulic oil control valve 10 of the second embodiment described above, the outer sleeve 30 and the inner sleeve 40 come into contact with each other in the radial direction when the axial force is applied, so that the outer sleeve 30 and the inner sleeve 40 come into contact with each other. It is possible to suppress an increase in the amount of hydraulic oil leaking from the minimum radial gap CL1. Further, since the inner sleeve 40 can be suppressed from expanding in the radial direction due to the radial contact between the outer sleeve 30 and the inner sleeve 40, the minimum radial clearance CL2 between the inner sleeve 40 and the spool 50 is expanded. It is possible to suppress an increase in the amount of hydraulic oil leaking from the minimum gap CL2. Therefore, even in a configuration in which the minimum radial clearance CL2 between the inner sleeve 40 and the spool 50, which can suppress the deterioration of the slidability of the spool 50, can be secured, an increase in the amount of hydraulic oil leakage can be suppressed, so that the spool 50 can be slid. It is possible to suppress an increase in the amount of hydraulic oil leakage while suppressing deterioration of motility.

Further, since the linear expansion coefficient of the spool 50 is the same as the linear expansion coefficient of the outer sleeve 30, it is possible to suppress the change in the size of the minimum gap CL2 due to the temperature rise of the hydraulic oil control valve 10, and the slidability of the spool 50. Deterioration can be suppressed. Further, since the outer sleeve 30 and the spool 50 are formed of iron and the inner sleeve 40 is made of aluminum, the coefficient of linear expansion of the inner sleeve 40 is larger than the coefficient of linear expansion of the outer sleeve 30, and the wire of the spool 50. At the same time, it is possible to easily realize a configuration in which the expansion coefficient is equivalent to the linear expansion coefficient of the outer sleeve 30. Further, since the spool 50 is made of iron, it is possible to suppress a decrease in the strength of the spool 50. Therefore, in the contact portion between the spool bottom 52 of the spool 50 and the shaft 164 of the solenoid 160, it is omitted to arrange a member different from the spool 50 in order to suppress wear due to rotation of the hydraulic oil control valve 10. it can. Therefore, it is possible to suppress an increase in the number of parts of the hydraulic oil control valve 10 and to prevent the assembly process from becoming complicated, so that it is possible to suppress an increase in the cost required for manufacturing the hydraulic oil control valve 10.

C. Third Embodiment:
The hydraulic oil control valve 10 of the third embodiment is different from the hydraulic oil control valve of the second embodiment in the dimensional relationship between the minimum clearance CL1 and the minimum clearance CL2. Since other configurations are the same as those of the second embodiment, the same configurations are designated by the same reference numerals, and detailed description thereof will be omitted.

In the hydraulic oil control valve 10 of the third embodiment, the outer sleeve 30 and the inner sleeve 40 come into radial contact with each other as the temperature rises when the valve timing adjusting device 100 is driven. In other words, the minimum radial clearance CL1 between the outer sleeve 30 and the inner sleeve 40 becomes zero as the temperature of the internal combustion engine 300 rises. Therefore, it is possible to suppress an increase in hydraulic oil leaking from the minimum radial gap CL1 between the outer sleeve 30 and the inner sleeve 40. The temperature difference between the valve timing adjusting device 100 during driving and before driving may be, for example, 100 ° C. or lower, about 150 ° C., or 200 ° C. or higher.

Further, also in the hydraulic oil control valve 10 of the third embodiment, the outer sleeve 30 and the spool 50 are each formed of iron and the inner sleeve 40 is formed of aluminum, as in the hydraulic oil control valve 10 of the second embodiment. Has been done. Therefore, the coefficient of linear expansion of the inner sleeve 40 is larger than the coefficient of linear expansion of the outer sleeve 30, and the inner sleeve 40 thermally expands more than the outer sleeve 30. However, when the temperature of the hydraulic oil control valve 10 rises due to the drive of the valve timing adjusting device 100, the outer sleeve 30 and the inner sleeve 40 come into contact with each other in the radial direction, so that the inner sleeve 40 is prevented from expanding in the radial direction. Will be done. Therefore, it is possible to suppress the expansion of the minimum radial clearance CL2 between the inner sleeve 40 and the spool 50 as the temperature of the hydraulic oil control valve 10 rises, and the amount of hydraulic oil leaking from the minimum clearance CL2 increases. Can be suppressed. Further, since the linear expansion coefficient of the spool 50 is the same as the linear expansion coefficient of the outer sleeve 30, it is possible to suppress a change in the size of the minimum gap CL2 due to the temperature rise of the hydraulic oil control valve 10. Therefore, deterioration of the slidability of the spool 50 can be suppressed.

In the present embodiment, the state in which the temperature rises when the valve timing adjusting device 100 is driven is the environment of the environment in which the valve timing adjusting device is used more than before the axial force is applied and the axial force is applied in the present disclosure. It corresponds to the subordinate concept of a state in which predetermined conditions including that the temperature has risen are satisfied. Further, the temperature of the internal combustion engine 300 corresponds to a subordinate concept of the environmental temperature of the environment in which the valve timing adjusting device is used.

According to the hydraulic oil control valve 10 of the third embodiment described above, the same effect as that of the hydraulic oil control valve 10 of the second embodiment is obtained. In addition, when an axial force is applied to the hydraulic oil control valve 10 and the temperature is higher than before the axial force is applied, the outer sleeve 30 and the inner sleeve 40 come into contact with each other in the radial direction. It is possible to suppress excessive application of a radial load.

D. Other embodiments:
(1) In each of the above embodiments, the outer sleeve 30 and the spool 50 are each made of iron, and the inner sleeve 40 is made of aluminum, but the present disclosure is not limited thereto. For example, the inner sleeve 40 may be formed of any other metal material, or may be formed of a resin material such as polyphenylene sulfide resin, nylon, or phenol resin, and is the same material as the outer sleeve 30 and the spool 50. It may be formed by. In the embodiment in which the inner sleeve 40 is made of resin, the outer sleeve 30 can be easily configured to be harder than the inner sleeve 40. Further, for example, the outer sleeve 30 and the spool 50 may be formed of any metal material such as stainless steel, or the outer sleeve 30 and the spool 50 may be formed of different materials. Further, for example, the linear expansion coefficient of the inner sleeve 40 does not have to be larger than the linear expansion coefficient of the outer sleeve 30, and the outer sleeve 30 does not have to be harder than the inner sleeve 40. Further, the coefficient of linear expansion of the spool 50 does not have to be equal to the coefficient of linear expansion of the outer sleeve 30. Even with such a configuration, the same effect as that of each of the above-described embodiments can be obtained.

(2) In the first embodiment, the magnitude relationship between the minimum clearance CL1 and the minimum clearance CL2 is maintained even in a state where an axial force is applied to the outer sleeve 30 and the camshaft 320 is fixed to the end portion 321. However, it does not have to be maintained. Even with such a configuration, the same effect as that of the first embodiment is obtained.

(3) The configuration of the hydraulic oil control valve 10 in each of the above embodiments is merely an example and can be variously changed. For example, like the hydraulic oil control valve 10a of the other embodiment 3 shown in FIG. 7, an opening 402 is formed at the end 401 of the inner sleeve 40a on the camshaft 320 side, and the tip of the spool 50a is formed in the opening 402. The part 510 may be inserted. Further, the stopper 49 of the inner sleeve 40a may be omitted, and the stopper 85 may be formed at a position of the outer sleeve 30a facing the tip 510 of the spool 50. With such a configuration, the drain outflow portion 55a may be formed at the end of the outer sleeve 30a on the camshaft 320 side, and the inside of the shaft hole 34a on the camshaft 320 side of the stopper 85 is together with the inside of the spool 50. It may function as a drain oil passage 53a. Further, in such a configuration, a supply hole 328 for supplying hydraulic oil from the hydraulic oil supply source 350 shown in FIG. 1 may be formed in the main body portion 31a of the outer sleeve 30a. Further, the spool bottom 52a of the spool 50a may not protrude toward the solenoid 160 from the fixing member 70, and the enlarged diameter portion 36 of the outer sleeve 30a may be omitted, instead of the flange portion 46 of the inner sleeve 40a. A locking end portion 46a having substantially the same outer diameter as the sealing wall 45 may be formed. Even with such a configuration, the same effect as that of each of the above-described embodiments can be obtained.

Further, for example, the recycling mechanism by the recycling port 47 may be omitted. Further, for example, the inside of the spool 50 may be configured as the hydraulic oil supply oil passage 25, and the space between the shaft hole 34 of the outer sleeve 30 and the outer peripheral surface of the inner sleeve 40 is configured as the drain oil passage 53. You may be. Further, for example, the fastening is not limited to the fastening of the male screw portion 33 and the female screw portion 324, and the axial force in the axial direction AD may be applied and fixed to the end portion 321 of the cam shaft 320 by any fixing method such as welding. .. Further, the solenoid 160 may be driven by any actuator such as an electric motor or an air cylinder. Even with such a configuration, the same effect as that of each of the above-described embodiments can be obtained.

(4) In each of the above embodiments, the valve timing adjusting device 100 adjusts the valve timing of the intake valve 330 that opens and closes the cam shaft 320, but the valve timing of the exhaust valve 340 may be adjusted. Further, it may be used by being fixed to the end 321 of the camshaft 320 as the driven shaft in which power is transmitted from the crankshaft 310 as the drive shaft via the intermediate shaft, and the camshaft has a double structure. It may be used by being fixed to one end of a drive shaft and a driven shaft.

The present disclosure is not limited to each of the above-described embodiments, and can be realized with various configurations within a range not deviating from the purpose. For example, the technical features in each embodiment corresponding to the technical features in the embodiments described in the column of the outline of the invention may be used to solve some or all of the above-mentioned problems, or one of the above-mentioned effects. It is possible to replace or combine as appropriate to achieve a part or all. Further, if the technical feature is not described as essential in the present specification, it can be appropriately deleted.

Claims (9)

1. The valve timing of the valve is fixed to the end (321) of one of the drive shaft (310) and the driven shaft (320) that opens and closes the valve (330) by transmitting power from the drive shaft. In the valve timing adjusting device (100) to be adjusted, the hydraulic oil is arranged and used on the rotation shaft (AX) of the valve timing adjusting device to control the flow of the hydraulic oil supplied from the hydraulic oil supply source (350). A control valve (10, 10a)
   Cylindrical sleeve (20) and
   Spools (50, 50a) driven by an actuator (160) arranged in contact with one end of the sleeve and sliding axially (AD) inside the sleeve in the radial direction.
   With
   The sleeve
   An inner sleeve (40, 40a) arranged on the outer side of the spool in the radial direction, and
   An outer sleeve (30, 30a) in which a shaft hole (34, 34a) is formed along the axial direction, and the inner sleeve is inserted into at least a part of the shaft hole in the axial direction. An outer sleeve that can be fixed to the end of one of the shafts by applying the axial force of
   Have,
   In the state where the axial force is not applied, the minimum radial gap (CL1) between the outer sleeve and the inner sleeve is the minimum radial gap (CL1) between the inner sleeve and the spool. Larger than CL2),
   Hydraulic oil control valve.
2. In the hydraulic oil control valve according to claim 1,
   The coefficient of linear expansion of the inner sleeve is larger than the coefficient of linear expansion of the outer sleeve.
   Hydraulic oil control valve.
3. In the hydraulic oil control valve according to claim 1 or 2.
   The outer sleeve is harder than the inner sleeve.
   Hydraulic oil control valve.
4. The hydraulic oil control valve according to any one of claims 1 to 3.
   The outer sleeve is made of iron
   The inner sleeve is made of aluminum or resin.
   Hydraulic oil control valve.
5. The valve timing of the valve is fixed to the end (321) of one of the drive shaft (310) and the driven shaft (320) that opens and closes the valve (330) by transmitting power from the drive shaft. In the valve timing adjusting device (100) to be adjusted, the hydraulic oil is arranged and used on the rotation shaft (AX) of the valve timing adjusting device to control the flow of the hydraulic oil supplied from the hydraulic oil supply source (350). The control valve (10, 10a)
   Cylindrical sleeve (20) and
   Spools (50, 50a) driven by an actuator (160) arranged in contact with one end of the sleeve and sliding axially (AD) inside the sleeve in the radial direction.
   With
   The sleeve
   An inner sleeve (40, 40a) arranged on the outer side of the spool in the radial direction, and
   An outer sleeve (30, 30a) in which a shaft hole (34, 34a) is formed along the axial direction, and the inner sleeve is inserted into at least a part of the shaft hole in the axial direction. An outer sleeve that can be fixed to the end of one of the shafts by applying the axial force of
   Have,
   The outer sleeve and the inner sleeve come into contact with each other in the radial direction in a state in which predetermined conditions including the application of the axial force are satisfied.
   Hydraulic oil control valve.
6. In the hydraulic oil control valve according to claim 5,
   The predetermined conditions include that the environmental temperature of the environment in which the valve timing adjusting device is used is higher than before the axial force is applied and the axial force is applied.
   Hydraulic oil control valve.
7. In the hydraulic oil control valve according to claim 5 or 6.
   The coefficient of linear expansion of the inner sleeve is larger than the coefficient of linear expansion of the outer sleeve.
   The coefficient of linear expansion of the spool is equivalent to the coefficient of linear expansion of the outer sleeve.
   Hydraulic oil control valve.
8. In the hydraulic oil control valve according to claim 7,
   The outer sleeve and the spool are made of iron.
   The inner sleeve is made of aluminum or resin.
   Hydraulic oil control valve.
9. The hydraulic oil control valve according to any one of claims 1 to 8 is provided.
   Valve timing adjuster.

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