JP2017082933A - Hydraulic control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic control valve which can shorten processing time of a sleeve, while preventing a filter from rotating.SOLUTION: A hydraulic control valve includes a sleeve 50 and filters 70, 71. The sleeve 50 has a cylindrical shape, has a port where a fluid can flow in/out, and it has at least one circular arc or elliptic arc-shaped recess 60 on an outer wall 56. The filters 70, 71 are wound along groove parts 91, 92 so as to cover a port for preventing intrusion of foreign substances, and it has a protrusion 80 which can be fitted in the recess 60 on a side wall 73 opposing to an inner wall 93 of the groove parts 91, 92. The recess 60 of the sleeve 50 and the protrusion 80 of the filters 70, 71 prevent the filters 70, 71 from rotating. Also, as the recess 60 has an arc shape, in the case of processing the sleeve 50 by end mill processing and the like, the diameter of the end mill can be enlarged. Therefore, processing time of the sleeve can be shortened.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a hydraulic control valve used for an automatic transmission or the like.

  2. Description of the Related Art Conventionally, it is known that a hydraulic control valve including a spool that switches between communication and blocking of a port and a cylindrical sleeve that supports the spool so as to be slidable in a reciprocating manner is used in an automatic transmission. Oil flowing into the sleeve may contain foreign substances such as metal powder due to wear of the transmission mechanism of the automatic transmission. For this reason, as disclosed in Patent Document 1, a filter is installed so that foreign matter contained in the oil does not flow into the sleeve.

JP 2013-092228 A

  In the hydraulic control valve disclosed in Patent Document 1, the port of the sleeve is covered with a filter having a mesh portion and a non-rotating shape. Further, the filter is fitted in an arc shape, and rotation is prevented at a portion corresponding to the port by a non-rotating shape. In such a structure, there are few fitting parts and it is thought that the adhesive force of a sleeve and a filter is small.

  When the rotational force is generated in the filter by the circumferential pressure by the hydraulic pressure or the vibration at the time of operation, the filter may rotate because the contact force is small. As the filter rotates, the filter may fall off the sleeve. In addition, when the filter is assembled to the sleeve or when the hydraulic control valve is transported, the filter may fall off the sleeve.

  By the way, in order to prevent the filter from rotating, a configuration of a hydraulic control valve in which a rectangular concave portion is provided outside the sleeve and a convex portion corresponding to the concave portion is provided in the filter is conceivable. Actually, when processing the recess in the sleeve, it is performed by cutting such as end milling. However, when the recess is processed into a rectangle such as a rectangle in end milling or the like, the diameter of the end mill must be reduced. When the diameter of the end mill is small, the moving distance of the end mill becomes large, so that the processing time becomes long.

  The present invention was created in view of the above points, and an object of the present invention is to provide a hydraulic control valve that can reduce the processing time of the sleeve while preventing the filter from rotating. .

The present invention is a hydraulic control valve used in an automatic transmission or the like.
The hydraulic control valve includes a sleeve (50), a spool (40), and filters (70, 71).
The sleeve includes a circumferential groove (91, 92) including a port (51, 52, 53, 54) through which fluid can flow in and out, and at least one arc shape recessed axially from the inner wall (93) of the groove. It has an elliptical arc-shaped recess (60, 120).

The spool is accommodated in the sleeve so as to be slidable back and forth, and can be switched between communication and blocking of the port.
The filter is wound along the groove so as to cover the port to prevent foreign matter from entering, and the convex part (80, 160, 180) that can be fitted into the concave part on the side wall (73) facing the inner wall of the groove part. Have

  In the hydraulic control valve of the present invention, the sleeve has at least one arc-shaped or elliptical arc-shaped recess that is recessed in the axial direction from the inner wall (93) of the groove, and the filter has a protrusion that can be fitted into the recess. With such a configuration, when a rotational force is generated in the filter, the concave portion and the convex portion are fitted with each other, so that the filter can be prevented from rotating.

  Further, since the concave portion has an arc shape or an elliptical arc shape, the diameter of the end mill can be increased when the sleeve is processed by end mill processing or the like. Since the diameter of the end mill can be increased, the moving distance of the end mill can be reduced. Therefore, the processing time of the sleeve can be shortened.

1 is a cross-sectional view of a hydraulic control valve according to a first embodiment of the present invention. 1 is an external view of a hydraulic control valve according to a first embodiment of the present invention. The expanded view of the filter of the hydraulic control valve by 1st Embodiment of this invention. The IV section enlarged view of FIG. The V section enlarged view of the sleeve and filter of the hydraulic control valve by 2nd Embodiment of this invention. The VI section enlarged view of the sleeve and filter of the hydraulic control valve by 3rd Embodiment of this invention. The VII part enlarged view of the sleeve and filter of the hydraulic control valve by 4th Embodiment of this invention.

  Hereinafter, a hydraulic control valve 1 according to an embodiment of the present invention will be described with reference to the drawings. In the description of the plurality of embodiments, the same reference numerals are given to the substantially same configurations as those in the first embodiment. Further, when referring to “this embodiment”, the first to fourth embodiments are included. The hydraulic control valve of these embodiments is used in, for example, a hydraulic control device for an automatic transmission.

(First embodiment)
As shown in FIGS. 1 and 2, the hydraulic control valve 1 includes a linear solenoid 10, a spool 40, a sleeve 50, and filters 70 and 71.

  The linear solenoid 10 includes a coil assembly 11, a plunger 12, a yoke 13, and a core stator 14.

The coil assembly 11 includes a bobbin 15, a coil 16, a terminal 17, and a mold resin 18.
The bobbin 15 is a cylindrical resin member.
The coil 16 is a wire in which an insulation coating is wound around a bobbin 15, generates a magnetic field when energized, and forms a magnetic circuit that passes through the plunger 12, the yoke 13, and the core stator 14.
The terminal 17 is connected to an external device and supplies power to the coil 16.
The mold resin 18 is a secondary molding resin that molds the outside of the coil 16, and forms a connector 19 that holds the terminal 17.

  The plunger 12 is formed of a cylindrical magnetic body and is provided so as to be movable in the axial direction inside the bobbin 15. The plunger 12 includes a breathing hole 20 penetrating in the axial direction. The plunger 12 is urged toward the bottom 23 of the yoke 13 by the spring 22 via the shaft 21 and the spool 40.

  The yoke 13 is a cup-shaped magnetic body and covers the outside of the coil 16. The cylindrical portion 24 of the yoke 13 includes a notch 25 for taking out the terminal 17 to the outside. Moreover, the cylinder part 24 is being fixed to the sleeve 50 by crimping.

The core stator 14 is a cylindrical magnetic body and includes a guide part 26, a suction part 27, and a magnetic shield part 28.
The guide portion 26 has a cylindrical shape and is provided inside the coil 16 and on the bottom 23 side of the yoke 13. The guide portion 26 is fitted to the outside of the plunger 12 and guides the plunger 12 so as to be slidable in the axial direction. The end of the guide portion 26 faces the bottom portion 23 of the yoke 13.

  The attracting unit 27 attracts the plunger 12 by generating a magnetic attracting force when the coil 16 is energized. The suction portion 27 has a fitting hole 29 into which the sucked plunger 12 is fitted, and a flange 30 that is magnetically coupled is formed.

  The magnetic blocker 28 is provided between the guide unit 26 and the suction unit 27, and blocks the magnetism between the guide unit 26 and the suction unit 27.

  The spool 40 is in contact with the plunger 12 and has an outer diameter that is equal to the inner diameter of the sleeve 50. The spool 40 can switch communication and blocking of the ports 51, 52, 53, and 54 of the sleeve 50, and controls the communication state of the ports 51, 52, 53, and 54.

  The sleeve 50 is formed of a nonmagnetic material. For example, stainless steel or aluminum is used as the nonmagnetic material. The sleeve 50 accommodates the spool 40 so as to be reciprocally slidable on the inner side surface 55, and has grooves 91 and 92 around which the filters 70 and 71 are wound, and a recess 60 described later.

  The sleeve 50 has a cylindrical inner side surface 55 that extends in the axial direction from the linear solenoid 10 side toward the spring 22 side. The spool 40 is supported inside the inner surface 55 of the sleeve 50 so as to be slidable in the axial direction of the sleeve. The outer peripheral surface 41 of the spool 40 is a sliding surface that slides with the inner surface 55 of the sleeve 50.

  The grooves 91, 92, 93, 94 are formed in the circumferential direction of the outer wall 56 of the sleeve 50, have a stepped shape, and include ports 51, 52, 53, 54 through which oil can flow in and out.

  The ports 51 to 54 are installed on the outer side in the radial direction of the sleeve 50 and open in an arc shape in the circumferential direction. The ports 51 to 54 include an input port 51, an output port 52, a discharge port 53, and a feedback port 54. The inside and outside of the inner side surface 55 communicate with each other in the radial direction of the sleeve 50, and fluid can flow in and out. is there. In this embodiment, oil is used as the fluid.

  The input port 51 is a channel hole that is formed in the groove 91 and is supplied with oil from a supply source such as an oil pump. The input port 51 is connected to the inside of the inner surface 55 of the sleeve 50 so that oil can flow when the linear solenoid 10 is operated.

  The output port 52 is formed in the groove 92 and is spaced apart so as to be parallel to the input port 51. The output port 52 outputs oil from the inner side surface 55 of the sleeve 50 to, for example, an automatic transmission (not shown). It is a hole. The output port 52 is connected to the input port 51 so as to be able to flow when the linear solenoid 10 is operated.

The discharge port 53 is formed in the groove portion 93 and is spaced apart so as to be parallel to the output port 52, communicates with the output port 52, and discharges oil that has flowed back to the output port 52 from the inner surface 55 of the sleeve 50. .
The feedback port 54 is a flow path hole that is formed in the groove portion 94, is installed on the spring 22 side, and is supplied with oil from the output port 52. The pressure output from the output port 52 is adjusted.

  As shown in FIG. 3, the filters 70 and 71 have a plurality of filter holes 72 and convex portions 80 described later. The filters 70 and 71 are made of, for example, copper or stainless steel, and are attached to the sleeve 50.

  The filter 70 covers the input port 51 and winds along the groove 91. The filter 70 is fitted so as to surround the groove 91. The filter 71 covers the output port 52 similarly to the filter 70 that covers the input port 51. Oil pressure from the radially outer side to the inner side acts on the filters 70 and 71, and the inner peripheral surfaces of the filters 70 and 71 are in close contact with the sleeve 50.

The plurality of filter holes 72 are small holes that are smaller than the particle size of the foreign matter contained in the oil and through which the oil can flow. The plurality of filter holes 72 are formed by etching or pressing. The formation range of the filter hole 72 is formed so as to be equal to or greater than the circumferential width of the input port 51 and the output port 52 in the longitudinal direction (circumferential direction) of the filters 70 and 71.
(Function)

The operation of the hydraulic control valve 1 of the present embodiment will be described.
When power is not supplied to the coil 16, the spool 40 is stopped at the position on the linear solenoid 10 side by the biasing force of the spring 22. When the spool 40 stops at the position on the linear solenoid 10 side, the spool 40 closes the input port 51 and connects the output port 52 and the discharge port 53.

  Oil discharged from a supply source such as an oil pump and having passed through the filter hole 72 of the filter 70 reaches the input port 51. Since the spool 40 blocks the input port 51, the oil that reaches the input port 51 remains without flowing into the sleeve 50.

  The oil that has flowed out of the output port 52 into the automatic transmission passes through the filter 71. The oil that has passed through the filter 71 flows backward from the automatic transmission to the output port 52. When the oil returns to the output port 52, the filter 71 prevents foreign substances such as metal powder contained in the oil from entering the sleeve 50. The oil returned to the output port 52 flows out from the discharge port 53 to the outside of the inner side surface 55 of the sleeve 50 through the inside of the inner side surface 55 of the sleeve 50.

  As described above, when power is not supplied to the coil 16, the communication between the input port 51 and the output port 52 is cut off, so that it functions as a normally closed type hydraulic control valve 1.

  On the other hand, when electric power is supplied to the coil 16, the plunger 12 is attracted to the core stator 14 in accordance with the magnitude of the current flowing through the coil 16. As the plunger 12 is sucked, the shaft 21 pushes the spool 40 connected to the shaft 21 toward the sleeve 50. When the shaft 21 pushes out the spool 40, the spool 40 moves to the sleeve 50 side.

  When the spool 40 moves toward the sleeve 50, the magnetic attraction force of the plunger 12, the urging force of the spring 22, and the feedback force acting on the spool 40 due to the pressure of oil flowing from the output port 52 to the feedback port 54 are generated. Balance. The spool 40 stops at a position where these forces are balanced.

  When the spool 40 moves to the sleeve 50 side, the opening area of the input port 51 is enlarged, and the opening area of the discharge port 53 is reduced. The oil that has passed through the filter 70 flows into the input port 51. The filter 70 prevents foreign matters contained in the oil pressure-fed and supplied to the input port 51 from entering the inside of the sleeve 50.

(Feature configuration)
The recessed part 60 and the convex part 80 which are the characteristic structures of this embodiment are demonstrated with reference to FIG. 2 and FIG. In FIG. 4, the concave portion 60 and the convex portion 80 are exaggerated for easy understanding of the characteristic configuration.

  As shown in FIG. 2, the sleeve 50 has a recess 60 in the groove portions 91 and 92. The filter 70 has a convex portion 80 on the side wall 73 facing the inner wall 93 of the groove portions 91 and 92. The concave portion 60 and the convex portion 80 are formed correspondingly so that the side surface 64 of the concave portion 60 faces the outer surface 84 of the convex portion 80.

As shown in FIG. 4, the recess 60 is formed so as to be recessed in the axial direction in the inner wall 93 adjacent to the filter 70 of the grooves 91 and 92 formed in the outer wall 56 of the sleeve 50. A straight line If extending over the convex portion 80 on the side wall 73 of the filters 70 and 71 and connecting the base end 81 and the base end 83 is defined as a virtual line If. The concave portion 60 and the convex portion 80 include the same central axis O, and the intersection of the central axis O and the virtual line If is the center Os.
The recess 60 is formed in an arcuate quadratic curve shape including the radius Rs from the center Os.

  The convex portion 80 is formed on the side wall 73 of the filters 70 and 71 and is formed so as to be able to fit the concave portion 60 at a position facing the concave portion 60 of the sleeve 50. The convex portion 80 has an arc shape with a radius Rf that is the center Of on the central axis O. The distance from the central axis O to the end portions 61 and 63 is Ws, and the distance from the central axis O to the intersection 85 defined by the outer surface 84 of the convex portion 80 and the virtual line Is is Wf.

The concave portion 60 and the convex portion 80 are formed so that the radius Rs of the concave portion 60 is larger than the radius Rf of the convex portion 80, that is, Rs> Rf.
For this reason, the concave portion 60 and the convex portion 80 are formed such that the distance Ws is larger than the distance Wf, that is, Ws> Wf.

  A clearance 90 is formed between the inner wall 93 and the side wall 73 of the groove portions 91 and 92 adjacent to the filters 70 and 71. The size of the clearance 90 is a distance C from the inner wall 93 to the side wall 73. Further, the distance from the inner wall 93 to the highest vertex 62 of the concave portion 60 is Ls, and the distance from the side wall 73 to the tip point 82 of the convex portion 80 is Lf.

  The concave portion 60 and the convex portion 80 are formed such that the distance (C + Ls) from the side wall 73 to the highest vertex 62 is larger than the distance Lf, that is, C + Ls> Lf. The concave portion 60 and the convex portion 80 are formed such that the distance Ls is greater than the distance Lf, and the distance Lf is greater than the distance C, that is, Ls> Lf> C.

  A tangent line Ts is provided from the end 61 of the recess 60 toward the recess 60. Further, on the inner wall 93, a virtual line Is connecting the end 61 and the end 63 is provided. A tangent angle defined by the tangent line Ts and the virtual line Is is defined as θc. Further, a recess angle defined by the straight line Hs connecting the end portion 61 and the highest vertex 62 and the virtual line Is is defined as θs.

  A tangent line Tf is provided from the base end 81 of the convex part 80 toward the convex part 80, and a tangential angle defined by the tangent line Tf and the virtual line If is θi. A convex angle defined by the straight line Hf connecting the base end 81 and the front end point 82 and the virtual line If is θf.

The concave portion 60 and the convex portion 80 are formed so that the tangent angle θc is larger than the tangential angle θi, that is, θc> θi. The concave portion 60 and the convex portion 80 are formed so that the concave portion angle θs is equal to or larger than the convex portion angle θf, that is, θs ≧ θf.
(effect)

  (1) In the present embodiment, when the rotational force acts on the filters 70 and 71 and the filters 70 and 71 rotate, the concave portions 60 and the convex portions 80 are fitted, so that the filters 70 and 71 rotate. Can be prevented.

  (2) Since the recess 60 has an arc shape, when the sleeve 50 is processed using end milling or the like, the diameter of the end mill is increased in normal processing in which the end mill shaft is orthogonal to the sleeve 50 axis. And the travel distance of the end mill can be reduced. Therefore, the processing time of the sleeve 50 can be shortened.

  (3) Since the concave portion 60 and the convex portion 80 are formed such that the concave portion angle θs is equal to or larger than the convex portion angle θf, the tip point 82 does not contact the side surface 64 of the concave portion 60, and the convex portion 80 is not in the concave portion 60. Does not interfere with. Since the tip point 82 does not interfere with the recess 60, the stress generated at the tip point 82 can be reduced. By reducing the stress at the tip point 82, it is possible to suppress the deformation of the convex portion 80 and to secure the function of preventing the filters 70 and 71 from rotating.

  (4) Since the concave portion 60 and the convex portion 80 are formed such that the distance (C + Ls) from the side wall 73 to the highest vertex 62 is larger than the distance Lf, the clearance 90 can be secured. Since the clearance 90 is secured, when the filters 70 and 71 are assembled to the sleeve 50, a position where the robot hand or the like grasps the filters 70 and 71 can be secured. Further, since the assembly position error in the axial direction or the component tolerance of the filter width can be absorbed, the assembly is facilitated.

  (5) Since the concave portion 60 and the convex portion 80 are formed so that the distance Ws is larger than the distance Wf, the end portions 61 and 63 are the outer surfaces 84 of the convex portion 80 when the filters 70 and 71 do not rotate. Does not interfere with. Since the end portions 61 and 63 do not interfere with the convex portion 80 when the filters 70 and 71 are not rotating, the deformation of the concave portion 60 or the convex portion 80 is suppressed, and the rotation prevention function of the filters 70 and 71 is further secured. be able to.

The second embodiment is the same as the first embodiment except for the shape of the recess.
(Second Embodiment)
As shown in FIG. 5, the recess 120 includes a short axis common to the imaginary line Is connecting the end 121 and the end 123 and a long axis common to the central axis O. The concave portion 120 has an elliptical arc shape with the center Ob as the intersection of the central axis O and the virtual line Is. The distance from the central axis O to the end 121 is the short diameter La, and the distance from the top vertex 122 to the virtual line Is is the long diameter Lb.

  The concave portion 120 and the convex portion 80 are formed so that the minor axis La is larger than the radius Rf of the convex portion 80, that is, La> Rf. For this reason, the distance (La) from the end portions 121 and 123 to the central axis O is larger than the distance Wf from the intersection 85 defined by the outer surface 84 of the convex portion 80 and the virtual line Is to the central axis O.

  The concave portion 120 and the convex portion 80 are formed so that the distance (C + Lb) from the side wall 73 to the highest vertex 122 is larger than the distance Lf, that is, C + Lb> Lf. The concave portion 120 and the convex portion 80 are formed such that the major axis Lb is larger than the distance Lf and the distance Lf is larger than the distance C, that is, Ls> Lf> C.

  A tangent angle defined by a tangent line Ts at the end 121 and a virtual line Is connecting the end 121 and the end 123 is defined as θq. A recess angle defined by the straight line Hb connecting the end 121 and the top vertex 122 and the virtual line Is is defined as θb.

  The concave portion 120 and the convex portion 80 are formed so that the tangent angle θq is larger than the tangential angle θi, that is, θq> θi. Further, the concave portion 120 and the convex portion 80 are formed so that the concave portion angle θb is equal to or larger than the convex portion angle θf, that is, θb ≧ θf.

  Also in the second embodiment, since the recess 120 has an elliptical arc shape, when the end mill is tilted with respect to the sleeve 50, the processing of the sleeve 50 can be facilitated. For this reason, the processing time of the sleeve 50 can be shortened. In addition, since the sleeve 50 and the filters 70 and 71 do not interfere with each other, the same effects as those of the first embodiment can be obtained.

In 3rd Embodiment and 4th Embodiment, except the form of a convex part, other than that is the same as that of 1st Embodiment.
(Third embodiment)
As shown in FIG. 6, the convex part 160 is formed in a triangular shape of an isosceles triangle having the central axis O as a symmetry axis. The distance from the intersection 165 defined by the outer surface 164 of the convex portion 160 and the virtual line Is to the central axis O is defined as Wt. Further, the distance from the imaginary line If connecting the base end 181 and the base end 183 to the front end point 162 of the convex portion 160 is Lt.

  The convex portion 160 and the concave portion 60 are formed such that the distance Ws is larger than the distance Wt, that is, Ws> Wt.

  Further, the convex portion 160 and the concave portion 60 are formed so that the distance (C + Ls) from the side wall 73 to the highest vertex 62 is larger than the distance Lt, that is, C + Ls> Lt. Further, the convex portion 160 is formed so that the distance Ls is larger than the distance Lt and the distance Lf is larger than the distance C, that is, Ls> Lt> C.

  A convex portion angle defined by the straight line Ht connecting the distal end point 162 and the base ends 161 and 163 corresponding to the vertices of the isosceles triangle and the virtual line If is defined as θt. The convex portion 160 and the concave portion 60 are formed so that the tangent angle θc is larger than the convex portion angle θt, that is, θc> θt.

  Further, the convex portion 160 and the concave portion 60 are formed such that the concave portion angle θs is equal to or larger than the convex portion angle θt, that is, θs ≧ θt. Also in the fourth embodiment, the convex portion 160 does not interfere with the concave portion 60, and has the same effect as the first embodiment.

(Fourth embodiment)
As shown in FIG. 7, the convex portion 180 is formed in an isosceles trapezoidal quadrangular shape with the central axis O as the symmetry axis. The distance from the intersection 185 defined by the outer surface 186 of the convex portion 180 and the virtual line Is to the central axis O is defined as Wd. Further, the distance from the virtual line If to the tip point 182 of the convex portion 180 is Ld.

  The convex portion 180 and the concave portion 60 are formed such that the distance Ws is greater than the distance Wd, that is, Ws> Wd.

  Further, the convex portion 180 and the concave portion 60 are formed so that the distance (C + Ls) from the side wall 73 to the highest vertex 62 is larger than the distance Ld, that is, C + Ls> Ld. Further, the convex portion 160 is formed so that the distance Ls is larger than the distance Ld and the distance Ld is larger than the distance C, that is, Ls> Ld> C.

  A convex angle defined by a straight line Hd connecting the distal end point 182 and the proximal end 181 provided on the same hypotenuse as the proximal end 181 and a virtual line If connecting the proximal ends 181 and 183 is defined as θd. The straight line Hd is substantially the same as the straight line connecting the distal end point 184 and the proximal end 183.

  The convex portion 180 and the concave portion 60 are formed so that the tangent angle θc is larger than the convex portion angle θd, that is, θs> θd. Further, the convex portion 180 and the concave portion 60 are formed so that the concave portion angle θs is equal to or larger than the convex portion angle θd, that is, θs ≧ θd. The fourth embodiment also has the same effect as the first embodiment.

(Other embodiments)
(A) A plurality of recesses may be provided in the sleeve. Further, a plurality of convex portions corresponding to the concave portions may be provided in the filter. The convex portion may be a polygonal shape. The same effect as the first embodiment is achieved.

(A) The convex portion formed on the side wall of the filter may be provided on the filter hole side. The positions of the concave portion and the convex portion are not limited, and the same effects as those of the first embodiment can be obtained.
As mentioned above, this invention is not limited to such embodiment, In the range which does not deviate from the meaning of invention, it can implement with a various form.

40 ・ ・ ・ Spool,
50 ... Sleeve,
51-54 Port,
91, 92 ... groove, 93 ... inner wall,
60, 120, 140 ... recess,
70, 71 ... Filter, 73 ... Side wall,
80, 160, 180 ... convex portions.

Claims (6)

Circumferential grooves (91, 92) including ports (51, 52, 53, 54) through which fluid can flow in and out, and at least one arc shape or elliptic arc shape recessed in the axial direction from the inner wall (93) of the groove portions A sleeve (50) having a recess (60, 120) of
A spool (40) accommodated in the sleeve so as to be reciprocally slidable and capable of switching between communication and blocking of the port;
A convex portion (80, 160, 180) that is wound along the groove portion so as to cover the port and prevents foreign matter from entering, and is fitted to the concave portion on the side wall (73) facing the inner wall of the groove portion. ) Having a filter (70, 71),
Hydraulic control valve comprising.   A recess defined by a straight line (Hs, Hb) connecting the end (61, 63, 121, 123) of the recess and the top (62, 122) of the recess and a virtual line (Is) connecting the end. The angles (θs, θb) are straight lines (Hf, Ht, Hd) connecting the base ends (81, 83, 161, 163, 181, 183) of the convex portions and the tip points (82, 162, 182) of the convex portions. And a convex angle (θf, θt, θd) defined by a virtual line (If) connecting the base ends.   The hydraulic control valve according to claim 2, wherein a distance from the side wall to the topmost point is greater than a distance (Lf, Lt, Ld) from the side wall to the tip end point.   The distance (Ws) from the central axis (O) of the concave portion to the end portion is an intersection point (85, 85) defined by an outer surface (84, 164, 184) of the convex portion and an imaginary line connecting the end portions. The hydraulic control valve according to claim 2 or 3, wherein the hydraulic control valve is larger than a distance (Wf, Wt, Wd) from 165, 185) to the central axis.   The hydraulic control valve according to claim 1, wherein the concave portion has an arc shape.   The hydraulic control valve according to claim 1, wherein the convex portion has a triangular shape.

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