JP2019210812A - Fluid control valve - Google Patents

Abstract

To provide a valve timing adjustment device which is improved in responsiveness.SOLUTION: A fluid control valve 10 comprises: a cylindrical sleeve 12; an annular first valve attachment groove 21 formed at an inner wall of the sleeve 12; a retardance supply opening part 35 penetrating from a groove bottom face 25 of the first valve attachment groove 21 up to an outer wall of the sleeve 12; a retardance connection opening part 38 penetrating the inside and outside of the sleeve 12 in a position in an axial direction different from the first valve attachment groove 21; a spool 13 movable to the axial direction in the sleeve 12; and a first check valve 31. The spool 13 switches the communication and block of the first valve attachment groove 21 and the retardance connection opening part 38 according to the position in the axial direction. The first check valve 31 is composed of an annular elastic body arranged at the first valve attachment groove 21, and valve-opened by the contraction of its diameter. The groove bottom face 25 of the first valve attachment groove 21 is decentered with respect to a slide face 53. An angle formed of a displacement direction Dd and an eccentric direction De at a cross section is within ±90°.SELECTED DRAWING: Figure 9

Description

  The present invention relates to a fluid control valve.

  2. Description of the Related Art Conventionally, a spool-type fluid control valve that controls a flow of fluid supplied from a fluid supply source to a fluid supply target is known. This type of fluid control valve has a cylindrical sleeve having a supply opening and a connection opening, and a spool movable in the axial direction within the sleeve. The spool switches between communication and blocking between the openings of the sleeve in accordance with the axial position.

  In patent document 1, the check valve which can open and close a supply opening part is provided. The check valve is provided in an annular groove on the inner wall of the sleeve, and opens by reducing the diameter by the flow of fluid from a supply opening that opens at the groove bottom surface of the annular groove. The movement of the check valve in the axial direction is restricted by the side surface of the annular groove. When the check valve is opened, the check valve is displaced to the inner side of the opening side of the annular groove (that is, the side opposite to the groove bottom surface), so that the pressure loss is greatly reduced and the necessary flow rate can be secured. .

U.S. Pat. No. 9,422,840

  In recent years, for the purpose of improving responsiveness, it has been required to reduce the amount of opening of the check valve (that is, the amount of movement of the valve body when the valve is opened) while ensuring the necessary flow rate. On the other hand, the opening amount of the check valve for ensuring the required flow rate can be reduced by making the annular groove shallow. However, when the annular groove is shallow, there is a possibility that the check valve may be inclined or the check valve may be detached from the annular groove.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a valve timing adjusting device with improved responsiveness.

  The fluid control valve of the present invention includes a cylindrical sleeve (12, 122, 123, 124, 125, 126, 127, 128, 129), an annular valve mounting groove (21, 22, 212), and a supply opening. (35, 36, 352, 354, 355, 356, 357), a connection opening (38, 39), a spool (13), and a check valve (31, 32). The valve mounting groove is an annular groove formed in the inner wall of the sleeve. The supply opening is formed so as to penetrate from the groove bottom surface (25, 26) of the valve mounting groove to the outer wall of the sleeve. The connection opening is formed so as to penetrate the sleeve inward and outward at an axial position different from the valve mounting groove. The spool is movable in the axial direction within the sleeve, and switches between communication and blocking between the valve mounting groove and the connection opening according to the axial position. The check valve is made of an annular elastic body provided in the valve mounting groove. The check valve is opened by reducing the diameter, allowing the flow of fluid from the supply opening to the connection opening, and closing by expanding the diameter. Thus, the flow of fluid from the connection opening to the supply opening is blocked.

  Of the inner wall surface of the sleeve, the surface on which the spool slides is defined as a sliding surface (53). The bottom surface of the valve mounting groove is eccentric with respect to the sliding surface. A cross section perpendicular to the axis (AX1) of the sliding surface is defined as a transverse cross section. The direction in which the check valve is displaced by the flow of fluid from the supply opening is defined as the displacement direction (Dd). A direction from the shaft center toward the eccentric shaft center (AX2) of the groove bottom surface is defined as an eccentric direction (De). In the cross section, the angle formed by the displacement direction and the eccentric direction is within ± 90 °.

  Accordingly, the check valve can be displaced inward at a relatively shallow portion of the valve mounting groove, and the required flow rate can be ensured by reducing the pressure loss with a small valve opening amount. Further, the check valve can be held at a relatively deep portion of the valve mounting groove, and the check valve can be prevented from being inclined and coming off from the annular groove of the check valve. Therefore, the check valve responsiveness can be improved by reducing the amount of opening of the check valve for securing the required flow rate.

It is a figure which shows the valve timing adjustment apparatus to which the fluid control valve of each embodiment was applied. It is the II-II sectional view taken on the line of FIG. 1, Comprising: It is a cross-sectional view of a valve timing adjustment apparatus. It is a perspective view of a 1st check valve. FIG. 2 is an enlarged view of the fluid control valve of FIG. 1, showing a state where a spool is positioned at one end of a stroke range. FIG. 2 is an enlarged view of the fluid control valve of FIG. 1, showing a state where a spool is positioned in the middle of a stroke range. FIG. 2 is an enlarged view of the fluid control valve of FIG. 1, showing a state where a spool is positioned at the other end of the stroke range. It is a figure which expands and shows the vicinity of the 1st valve attachment groove | channel among the fluid control valves by 1st Embodiment. It is a VII-VII line sectional view of Drawing 7, and is a figure showing the valve closing state of the 1st check valve. It is a figure corresponding to FIG. 8, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 2nd Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing containing the 1st valve attachment groove | channel of the fluid control valve by 3rd Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 4th Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 5th Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 6th Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 7th Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 8th Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve. It is sectional drawing including the 1st valve attachment groove | channel of the fluid control valve by 9th Embodiment, Comprising: It is a figure which shows the valve opening state of a 1st check valve.

  Hereinafter, a plurality of embodiments will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted.

  Hereinafter, a plurality of embodiments of a fluid control valve will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted. The fluid control valve is applied to, for example, a valve timing adjusting device for adjusting a valve timing of an intake valve or an exhaust valve of an internal combustion engine.

  First, as a matter common to each embodiment, the configuration of the valve timing adjusting device will be described with reference to FIGS. The valve timing adjusting device 90 in FIG. 1 adjusts the valve timing of the intake valve 91, but can be similarly applied to the exhaust valve.

  As shown in FIGS. 1 and 2, the valve timing adjusting device 90 is provided in a power transmission path from the crankshaft 92 to the camshaft 93. The valve timing adjusting device 90 includes a housing 81, a vane rotor 82, and the fluid control valve 10.

  The housing 81 includes a sprocket 83 fitted to the camshaft 93 and a cup-shaped case 84 that rotates integrally with the sprocket 83. The sprocket 83 is connected to the crankshaft 92 via the timing chain 94 and rotates in conjunction with the crankshaft 92. The case 84 forms a plurality of partition walls 85 protruding radially inward from the cylindrical portion.

  The vane rotor 82 is provided in the housing 81 so as to be rotatable relative to the housing 81, and includes a boss portion 86 and a plurality of vane portions 87. The boss 86 is cylindrical and is fixed to the end of the cam shaft 93. The vane portion 87 protrudes radially outward from the boss portion 86 and partitions the space between the partition walls 85 into a retard chamber 88 and an advance chamber 89. The vane rotor 82 rotates relative to the housing 81 in the retard direction or the advance direction according to the hydraulic pressure in the advance chamber 89 and the retard chamber 88.

  The fluid control valve 10 is a spool type valve that controls the flow of the fluid supplied from the oil pump 95 of the fluid supply source to the hydraulic chambers 88 and 89 to be supplied with fluid. The fluid control valve 10 includes an outer sleeve 11, a sleeve 12, and a spool 13. The outer sleeve 11 has a cylindrical shape, and a threaded portion 14 is formed at one end, and a bolt head 15 is formed at the other end. The outer sleeve 11 is inserted through the central portion of the vane rotor 82 and is screwed to the shaft hole portion 96 of the cam shaft 93. That is, the outer sleeve 11 functions as a bolt for fixing the vane rotor 82 to the cam shaft 93.

  The outer sleeve 11 is formed with a retard opening 16 and an advance opening 17 penetrating in the radial direction. The retard opening 16 communicates with the retard chamber 88 via the retard channel 71 of the vane rotor 82. The advance opening 17 is formed at a different axial position from the retard opening 16 and communicates with the advance chamber 89 via the advance channel 72 of the vane rotor 82.

  The oil pump 95 is connected to the supply hole 97 of the cam shaft 93. The oil pump 95 pumps up the hydraulic oil stored in the oil pan 98 which is an oil discharge part, and supplies it to the shaft hole part 96 through the supply hole part 97.

  The sleeve 12 has a bottomed cylindrical shape and is fitted inside the outer sleeve 11. The sleeve 12 is disposed so that the bottom 18 is positioned on the camshaft 93 side. The sleeve 12 cannot move relative to the outer sleeve 11.

  An annular first valve mounting groove 21 and second valve mounting groove 22 are formed on the inner wall of the sleeve 12. An annular third valve mounting groove 23 is formed on the outer wall of the sleeve 12. A first check valve 31 is provided in the first valve mounting groove 21. A second check valve 32 is provided in the second valve mounting groove 22. A third check valve 33 is provided in the third valve mounting groove 23.

  The check valves 31 and 32 are made of a ring-shaped elastic body (see FIG. 3). The check valves 31 and 32 are opened by reducing the diameter, permitting the flow of hydraulic oil from the outside in the radial direction, and closed by increasing the diameter. Thus, the flow of hydraulic oil from the radially inner side to the outer side is prevented. The third check valve 33 is made of an annular elastic body, opens by expanding the diameter, permits the flow of hydraulic oil from the radially inner side to the outer side, and closes the valve by reducing the diameter to radially outward. Block the flow of hydraulic oil from the inside to the outside.

  In the sleeve 12, a retard supply opening 35, a retard connection opening 36, a recycle opening 37, an advance connection opening 38, and an advance supply opening 39 that penetrate in the radial direction are formed in order in the axial direction. ing.

  The retard supply opening 35 penetrates from the groove bottom surface 25 of the first valve mounting groove 21 to the outer wall of the sleeve 12. The advance angle supply opening 39 penetrates from the groove bottom surface 26 of the second valve mounting groove 22 to the outer wall of the sleeve 12. The recycle opening 37 penetrates from the groove bottom surface 27 of the third valve mounting groove 23 to the inner wall of the sleeve 12. The retard connection opening 36 communicates with the retard opening 16. The advance angle connection opening 38 communicates with the advance angle opening 17.

  The retard supply opening 35, the third valve mounting groove 23, and the advance supply opening 39 communicate with each other through an axial flow path 41 between the inner wall of the outer sleeve 11 and the outer wall of the sleeve 12. . The axial flow path 41 communicates with the shaft hole 96. A filter 42 is provided between the axial flow path 41 and the shaft hole 96.

  The spool 13 has a cylindrical shape and is fitted inside the sleeve 12. The spool 13 can move relative to the sleeve 12 in the axial direction. A spring 43 is provided between the spool 13 and the bottom portion 18 of the sleeve 12. The spring 43 biases the spool 13 to the side opposite to the bottom portion 18.

  A locking portion 44 is provided inside the bolt head portion 15. The locking portion 44 restricts movement of the spool 13 to the side opposite to the bottom portion 18. The spool 13 is movable in the axial direction from a position where it comes into contact with the locking portion 44 (see FIG. 4) to a position where it comes into contact with the bottom 18 (see FIG. 6).

  One end portion 45 of the spool 13 protrudes out of the outer sleeve 11 through a central hole of the locking portion 44. A linear solenoid 47 is provided on the opposite side of the spool 13 from the cam shaft 93. The axial position of the spool 13 is determined by the balance between the biasing force of the spring 43 and the driving force of the linear solenoid 47.

  The spool 13 communicates and blocks the first valve mounting groove 21 and the retard connection opening 36 according to the axial position, communicates and blocks the retard connection opening 36 and the recycle opening 37, and the second valve. The connection and blocking between the mounting groove 22 and the advance connection opening 38 and the communication and blocking between the advance connection opening 38 and the recycling opening 37 are switched.

  Specifically, as shown in FIG. 4, when the spool 13 is in contact with the locking portion 44, the first valve mounting groove 21 and the retard connection opening 36 are communicated with each other, and the advance connection opening is provided. 38 and the recycle opening 37 are communicated with each other. Further, the second valve mounting groove 22 and the advance connection opening 38 are blocked, and the retard connection opening 36 and the recycle opening 37 are blocked.

  At this time, the hydraulic oil in the shaft hole 96 flows through the axial flow path 41, the retard supply opening 35, the first valve mounting groove 21, the retard connection opening 36, the retard opening 16, and the retard flow path. 71 is supplied to the retarding angle chamber 88 (see FIG. 2). Further, the hydraulic oil in the advance chamber 89 (see FIG. 2) passes through the advance passage 72, the advance opening 17, and the advance connection opening 38, and the recycle opening 37 or the first drain hole 48 of the spool 13. To leak. The hydraulic oil in the recycle opening 37 is returned to the axial flow path 41 through the third valve mounting groove 23. The hydraulic oil in the first drain hole 48 is discharged to the outside through the in-spool flow path 49 of the spool 13, the second drain hole 51, and the third drain hole 53 of the locking portion 44. As a result, the vane rotor 82 rotates relative to the housing 81 in the retard direction. Hereinafter, this state is referred to as a retarded operation state.

  As shown in FIG. 5, when the spool 13 is positioned between the locking portion 44 and the bottom portion 18, the first valve mounting groove 21 and the retard connection opening 36 are communicated with each other, and the second valve The mounting groove 22 and the advance connection opening 38 are communicated with each other. Further, the retard connection opening 36 and the recycle opening 37 are blocked, and the advance connection opening 38 and the recycle opening 37 are blocked.

  At this time, the hydraulic oil in the shaft hole 96 is supplied to the retard chamber 88 through the same path as in the retard operation state. Further, the hydraulic oil in the shaft hole 96 is passed through the axial flow path 41, the advance supply opening 39, the second valve mounting groove 22, the advance connection opening 38, the advance opening 17, and the advance flow path 72. To the advance chamber 89 (see FIG. 2). Thereby, the relative rotational position of the vane rotor 82 is maintained. Hereinafter, this state is referred to as a holding operation state.

  As shown in FIG. 6, when the spool 13 is in contact with the bottom 18, the second valve mounting groove 22 and the advance connection opening 38 communicate with each other, and the retard connection opening 36 and the recycle opening 37 Is communicated. Further, the first valve mounting groove 21 and the retard connection opening 36 are blocked, and the advance connection opening 38 and the recycle opening 37 are blocked.

  At this time, the hydraulic oil in the shaft hole 96 is supplied to the advance chamber 89 through the same path as in the holding operation state. The hydraulic oil in the retard chamber 88 (see FIG. 2) passes through the retard channel 71, the retard opening 16, and the retard connection opening 36, and the recycle opening 37 or the first drain hole 48 of the spool 13. To leak. As a result, the vane rotor 82 rotates relative to the housing 81 in the advance direction. Hereinafter, this state is referred to as an advance operation state.

[First Embodiment]
Next, the configuration of the fluid control valve 10 of the first embodiment will be described with reference to FIGS. Below, the structure of the 1st valve attachment groove | channel 21 and the 1st check valve 31 is demonstrated. The second valve mounting groove 22 and the second check valve 32 have the same configuration, but the description thereof is omitted.

  As shown in FIGS. 7 to 9, the groove bottom surface 25 of the first valve mounting groove 21 is a cylindrical surface and is eccentric with respect to the sliding surface 53 of the sleeve 12. The sliding surface 53 is a cylindrical surface on the inner wall surface of the sleeve 12 on which the spool 13 slides.

  Hereinafter, as shown in FIGS. 8 and 9, a cross section orthogonal to the axis AX1 of the sliding surface 53 is referred to as a “cross section”. An imaginary straight line connecting the axis AX1 of the sliding surface 53 and the eccentric axis AX2 of the sliding surface 53 in the cross section is defined as an “eccentric direction line L1”. A virtual straight line that passes through the axis AX1 and is orthogonal to the eccentric direction line L1 in the cross section is defined as an “orthogonal line L2”. A portion of the groove bottom surface 25 located on the side of the eccentric axis AX2 with respect to the orthogonal line L2 is referred to as a “deep bottom portion 55”. A portion of the groove bottom surface 25 located on the side opposite to the eccentric axis AX2 with respect to the orthogonal line L2 is referred to as a “shallow bottom portion 56”.

  In the first embodiment, three retard angle supply openings 35 are formed, and all of them are open to the shallow bottom portion 56. That is, the retard supply opening 35 is formed at a relatively shallow portion of the sleeve 12 in the first valve mounting groove 21, but is formed at a relatively deep portion of the sleeve 12 in the first valve mounting groove 21. It has not been. As a result, the total opening area of the retard supply opening 35 in the shallow bottom portion 56 is larger than the total opening area of the retard supply opening 35 in the deep bottom portion 55. In the first embodiment, the total opening area of the retard supply opening 35 in the deep bottom 55 is zero.

  Each retardation supply opening 35 has an average distance from the axis AX1 to each retardation supply opening 35 so as to be shorter than an average distance (for the entire circumference) from the axis AX1 to the groove bottom surface 25. A sleeve 12 is formed.

  When the first check valve 31 is displaced so as to reduce its diameter in response to the flow of hydraulic oil from the retard supply opening 35, the first check valve 31 is in a direction opposite to the retard supply opening 35, that is, shallow. Displacement is directed from the bottom 56 toward the deep bottom 55.

  As shown in FIG. 9, the direction in which the first check valve 31 is displaced by the flow of hydraulic oil from the retard supply opening 35 is referred to as “displacement direction Dd”. A direction from the axis AX1 toward the eccentric axis AX2 of the groove bottom surface 25 is defined as an “eccentric direction De”. . In the cross section, the angle formed by the displacement direction Dd and the eccentric direction De is within ± 90 °. In the first embodiment, the displacement direction Dd and the eccentric direction De are the same. Therefore, the angle formed by the displacement direction Dd and the eccentric direction De is 0 °.

(effect)
As described above, in the first embodiment, the groove bottom surface 25 of the first valve mounting groove 21 is eccentric with respect to the sliding surface 53. In the cross section, the angle formed by the displacement direction Dd and the eccentric direction De is within ± 90 °. As a result, as shown in FIG. 9, the first check valve 31 is displaced inward at a relatively shallow portion of the first valve mounting groove 21 to reduce the pressure loss with a small valve opening amount and ensure the necessary flow rate. Can do. In addition, the first check valve 31 can be held at a relatively deep location in the first valve mounting groove 21 to avoid the tilting of the first check valve 31 and the detachment of the first check valve 31 from the annular groove. Therefore, it is possible to reduce the valve opening amount of the first check valve 31 for securing the necessary flow rate, and to realize an improvement in the responsiveness of the first check valve 31.

  In the first embodiment, the total opening area of the retard supply opening 35 in the shallow bottom portion 56 is larger than the total opening area of the retard supply opening 35 in the deep bottom portion 55. Thereby, when hydraulic fluid flows inward from the retard supply opening 35, the first check valve 31 can be displaced toward the deep bottom 55 from the shallow bottom 56. That is, the first check valve 31 is opened so as to be pressed from a deep portion of the first valve mounting groove 21 toward a shallow portion.

[Second Embodiment]
In the second embodiment, as shown in FIG. 10, a first valve mounting groove 212 is formed in the sleeve 122. Three retard angle supply openings 35 are formed. Two retardation supply openings 35 are open only in the shallow bottom portion 562. One retard supply opening 35 opens in both the shallow bottom 562 and the deep bottom 552. As a result, the total opening area of the retard supply opening 35 in the shallow bottom 562 is larger than the total opening area of the retard supply opening 35 in the deep bottom 552. In the cross section, the angle formed by the displacement direction Dd and the eccentric direction De is + 45 °. In the second embodiment, the configuration other than the above is the same as that of the first embodiment, and the same effect as that of the first embodiment is achieved.

[Third Embodiment]
In the third embodiment, as shown in FIG. 11, the sleeve 123 has seven retard angle supply openings 35 formed therein. The three retard supply openings 35 are open only in the shallow bottom portion 56. Two retardation supply openings 35 are open only in the deep bottom 55. Two retard angle supply openings 35 are open to both the shallow bottom portion 56 and the deep bottom portion 55. As a result, the total opening area of the retard supply opening 35 in the shallow bottom portion 56 is larger than the total opening area of the retard supply opening 35 in the deep bottom portion 55. In the cross section, the angle formed by the displacement direction Dd and the eccentric direction De is 0 °. In the third embodiment, the configuration other than the above is the same as that of the first embodiment, and the same effects as those of the first embodiment are achieved.

[Fourth Embodiment]
In the fourth embodiment, as shown in FIG. 12, the sleeve 124 is formed with eight retard angle supply openings. The three retard supply openings 35 are open only in the shallow bottom portion 56. Three retard angle supply openings 352 open only to the deep bottom 55. Two retard angle supply openings 35 are open to both the shallow bottom portion 56 and the deep bottom portion 55. The cross-sectional area of the retard supply opening 352 and 353 is smaller than the cross-sectional area of the retard supply opening 35. Thereby, the total opening area of the retard supply opening in the shallow bottom portion 56 is larger than the total opening area of the retard supply opening in the deep bottom 55. In the cross section, the angle formed by the displacement direction Dd and the eccentric direction De is 0 °. The configuration of the fourth embodiment is the same as that of the first embodiment except for the above, and has the same effect as the first embodiment.

[Fifth Embodiment]
In the fifth embodiment, as shown in FIG. 13, the sleeve 125 has eight retard angle supply openings. Three retard angle supply openings 354 are open only in the shallow bottom portion 56. The three retard supply openings 35 are open only in the deep bottom 55. Two retard angle supply openings 35 are open to both the shallow bottom portion 56 and the deep bottom portion 55. The channel cross-sectional area of the retard supply opening 354 is the same as the channel cross-sectional area of the retard supply opening 35. The retard supply opening 35 extends in the radial direction, while the retard supply opening 354 extends in a direction intersecting the radial direction. As a result, the total opening area of the retard supply opening in the shallow bottom portion 56 is larger than the total opening area of the retard supply opening in the deep bottom 55. In the cross section, the angle formed by the displacement direction Dd and the eccentric direction De is 0 °. The configuration of the fourth embodiment is the same as that of the first embodiment except for the above, and has the same effect as the first embodiment.

[Sixth Embodiment]
In the sixth embodiment, as shown in FIG. 14, the sleeve 126 has four retard angle supply openings. Two retard angle supply openings 35 are open only in the shallow bottom part 56. Two retardation supply openings 35 are open only in the deep bottom 55. The total opening area of the retardation supply opening in the shallow bottom portion 56 is the same as the total opening area of the retardation supply opening in the deep bottom portion 55.

  The sleeve 126 is provided with a fixing pin 61 as a fixing portion. The fixing pin 61 fixes a part of the first check valve 31 in the circumferential direction to the groove bottom surface 25. In the sixth embodiment, the distal end portion of the fixing pin 61 is provided so as to protrude radially inward from the deepest portion of the deep bottom portion 55 and is press-fitted into the first check valve 31. Thereby, when hydraulic fluid flows inward from the retard supply opening 35, the first check valve 31 can be displaced toward the deep bottom 55 from the shallow bottom 56. That is, the first check valve 31 is opened so as to be pressed from a deep portion of the first valve mounting groove 21 toward a shallow portion. Therefore, the same effect as that of the first embodiment is obtained.

[Seventh Embodiment]
In the seventh embodiment, as shown in FIG. 15, the sleeve 127 is formed with a convex portion 62 as a fixing portion. The convex portion 62 is formed at the bottom of the first valve mounting groove 21. In the seventh embodiment, the convex portion 62 is provided so as to protrude radially inward from the deepest portion of the deep bottom portion 55, and is press-fitted into the first check valve 31. Thereby, there exists an effect similar to 6th Embodiment.

[Eighth Embodiment]
In the eighth embodiment, as shown in FIG. 16, the sleeve 128 has six retard supply openings. The three retard supply openings 35 are open only in the shallow bottom portion 56. Three retard angle supply openings 355 are open only in the deep bottom 55. The total opening area of the retardation supply opening 35 in the shallow bottom portion 56 is the same as the total opening area of the retardation supply opening 355 in the deep bottom portion 55.

  The retard supply opening 355 is formed with a diaphragm 63. In the eighth embodiment, the inner diameter of the retard supply opening 355 decreases from the inner side toward the outer side in the radial direction. The restricting portion 63 is a small diameter portion on the radially outer side of the retard supply opening 355. By providing the throttle portion 63 in this way, a difference can be made between the amount of hydraulic oil flowing through the retard supply opening 35 and the amount of hydraulic oil flowing through the retard supply opening 355. Thereby, the fluid force acting on the first check valve 31 at a shallow portion of the first valve mounting groove 21 is larger than the fluid force acting on the first check valve 31 at a deep portion of the first valve mounting groove 21. Therefore, the first check valve 31 is opened so as to be pressed from a deep portion of the first valve mounting groove 21 toward a shallow portion. Therefore, the same effects as those of the first embodiment are obtained.

[Ninth Embodiment]
In the ninth embodiment, as shown in FIG. 17, the sleeve 129 includes a first retardation supply opening 356 that opens to the deep bottom portion 55 and a second retardation supply opening that opens to the shallow bottom portion 56. A portion 357 is formed. The total opening area of the second retardation supply opening 357 in the shallow bottom portion 56 is the same as the total opening area of the first retardation supply opening 356 in the deep bottom portion 55.

  In the axial flow channel 41, the flow passage space A2 outside the second retardation supply opening 357 has a smaller flow cross-sectional area than the flow passage space A1 outside the first retardation supply opening 356. . By changing the size of the flow path space in this way, a difference can be made between the amount of hydraulic oil flowing through the second retardation supply opening 357 and the amount of hydraulic oil flowing through the first retardation supply opening 356. Thereby, there exists an effect similar to 8th Embodiment.

[Other Embodiments]
In other embodiments, the securing portion may be screwed, glued or welded. Further, the fixing portion may be a recess formed in the bottom portion of the valve mounting groove.

  In another embodiment, the restricting portion of the supply opening is not limited to the radially outer side of the supply opening, and may be formed on the radially inner side or the intermediate portion. Further, a member other than the sleeve may be fitted into the supply opening to constitute the throttle portion.

  The present invention is not limited to the embodiments described above, and can be implemented in various forms without departing from the spirit of the invention.

10: Fluid control valve 12, 122, 123, 124, 125, 126, 127, 128, 129: Sleeve 13: Spool 21, 22, 212: Valve mounting groove 25, 26: Groove bottom surface 31, 32: Check valve 35, 36, 352, 354, 355, 356, 357: supply opening 38, 39: connection opening 53: sliding surface 88: retarding chamber (target for fluid supply)
89: Advance chamber (target for fluid supply) 95: Fluid supply source AX1: Center axis AX2: Eccentric axis De: Eccentric direction Dd: Displacement direction

Claims (7)

A fluid control valve for controlling a flow of fluid supplied from a fluid supply source (95) to a fluid supply target (88, 89),
A cylindrical sleeve (12, 122, 123, 124, 125, 126, 127, 128, 129);
An annular valve mounting groove (21, 22, 212) formed in the inner wall of the sleeve;
A supply opening (35, 36, 352, 354, 355, 356, 357) formed so as to penetrate from the groove bottom surface (25, 26) of the valve mounting groove to the outer wall of the sleeve;
Connection openings (38, 39) formed so as to penetrate the sleeve in and out at an axial position different from the valve mounting groove;
A spool (13) which is movable in the axial direction within the sleeve and which switches communication and blocking between the valve mounting groove and the connection opening according to an axial position;
It consists of a ring-shaped elastic body provided in the valve mounting groove, opens by reducing the diameter, allows the flow of fluid from the supply opening to the connection opening, and closes by expanding the diameter. Check valves (31, 32) for blocking fluid flow from the connection opening to the supply opening;
With
When the surface on which the spool slides is the sliding surface (53) of the inner wall surface of the sleeve,
The groove bottom surface of the valve mounting groove is eccentric with respect to the sliding surface;
A cross section perpendicular to the axis (AX1) of the sliding surface is a transverse cross section, a direction in which the check valve is displaced by the flow of fluid from the supply opening is a displacement direction (Dd), and the groove extends from the axis. When the direction toward the eccentric axis (AX2) on the bottom is the eccentric direction (De),
A fluid control valve in which an angle formed by the displacement direction and the eccentric direction is within ± 90 ° in a cross section. An imaginary straight line connecting the axis and the eccentric axis in the transverse section is defined as an eccentric direction line (L1), and an imaginary straight line passing through the axis and orthogonal to the eccentric direction line in the transverse section is an orthogonal line. (L2), a portion of the groove bottom surface located on the side of the eccentric axis with respect to the orthogonal line is defined as a deep bottom portion (55, 552), and the eccentric axis center with respect to the orthogonal line of the groove bottom surface. If the part located on the opposite side is the shallow bottom (56, 562),
The fluid control valve according to claim 1, wherein a total opening area of the supply opening in the shallow bottom is larger than a total opening area of the supply opening in the deep bottom.   The fluid control valve according to claim 1 or 2, further comprising a fixing portion (61, 62) for fixing a part of the check valve in a circumferential direction to the groove bottom surface.   The fluid control valve according to claim 3, wherein the fixing portion (61) is press-fitted, screwed, bonded, or welded to the check valve.   The fluid control valve according to claim 3, wherein the fixed portion (62) is a convex portion or a concave portion formed in a bottom portion of the valve mounting groove. An imaginary straight line connecting the axis and the eccentric axis in the transverse section is an eccentric direction line, and an imaginary straight line passing through the axis and orthogonal to the eccentric direction line in the transverse section is an orthogonal line, A portion of the groove bottom surface that is located on the side of the eccentric axis with respect to the orthogonal line is a deep bottom portion, and a portion of the groove bottom surface that is on the side opposite to the eccentric axis is a shallow bottom portion. Then,
The fluid control valve according to claim 1, wherein a throttle part (63) is formed in the supply opening part that is open to the deep bottom part. An imaginary straight line connecting the axis and the eccentric axis in the transverse section is an eccentric direction line, and an imaginary straight line passing through the axis and orthogonal to the eccentric direction line in the transverse section is an orthogonal line, A portion of the groove bottom surface located on the side of the eccentric axis with respect to the orthogonal line is defined as a deep bottom portion, the supply opening portion opened to the deep bottom portion is defined as a first supply opening portion, When a portion located on the opposite side of the eccentric axis with respect to the orthogonal line is a shallow bottom portion, and the supply opening portion opened to the shallow bottom portion is a second supply opening portion,
The fluid control valve according to claim 1, wherein the flow passage space (A2) outside the second supply opening has a smaller flow cross-sectional area than the flow passage space (A1) outside the first supply opening.

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