JP2019011779A - Hydraulic control device - Google Patents

Abstract

To provide a hydraulic control device for securing the length of a seal surface to seal a space between a sleeve and an opposite material when providing engaged parts in the outside wall of the sleeve for rotation prevention parts of annular filter members to be engaged therewith.SOLUTION: A first annular filter member 40 and a second annular filter member 42 are formed with engagement protrusions 52a, 52b as rotation prevention parts, respectively, while a sleeve 20 is formed with engagement recesses 54a, 54b as engaged parts with which the engagement protrusions 52a, 52b are engaged. The engagement of the engagement protrusions 52a, 52b with the engagement recesses 54a, 54b causes the rotation stop of the first annular filter member 40 and the second annular filter member 42. The engagement recesses 54a, 54b are provided, for example, at positions where a mutual phase difference is about 180°.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a hydraulic control device that controls the pressure of hydraulic oil.

  A hydraulic control device including a solenoid valve controls, for example, the hydraulic pressure of hydraulic oil of a clutch mounted on an automobile. That is, the sleeve constituting the hydraulic control device is formed with an input port for supplying hydraulic oil therein and an output port for discharging the hydraulic oil from the inside. The valve body constituting the electromagnetic valve normally closes the input port. On the other hand, when energized, it is displaced to a position where the input port is opened. As a result, the input port communicates with the output port, and the hydraulic oil input from the input port is output from the output port.

  Foreign matter may be mixed in the hydraulic oil. In order to avoid this foreign matter from entering the hydraulic control device or the clutch, filter members are installed at the input port and the output port, as described in Patent Document 1. Foreign substances are captured by these filter members.

JP-A-5-68819

  The filter member described in Patent Document 1 is made of an injection-molded woven fabric, and is formed into an annular shape by snap-bonding both ends of two segments having a resin portion, and each annular member is provided with a port. It is arranged in the groove. Here, the filter member receives hydraulic pressure from the hydraulic oil flowing through each port. For this reason, the filter member may circulate (rotate) along the outer peripheral wall of the sleeve in the annular groove. When such a situation occurs and the resin portion overlaps the port, the inflow of hydraulic oil into the port or the outflow from the port is hindered.

  In order to prevent this, it is recalled that the filter member is provided with an anti-rotation portion and an engaged portion with which the anti-rotation portion is engaged is provided on the outer peripheral wall (outer wall) of the sleeve. In this case, it is possible to prevent the filter member from rotating with a simple configuration in which the rotation preventing portion is engaged with the engaged portion.

  Here, the outer peripheral wall of the sleeve serves as a seal surface that abuts against the inner peripheral wall of the mounting hole of the mating member to which the hydraulic control device is mounted to seal between the mating material and the sleeve. Therefore, providing the engaged portion on the outer peripheral wall of the sleeve means that the length of the seal surface is reduced. In particular, when the filter member is provided in each of the input port and the output port as described above, since a plurality of engaged portions are formed, there is a concern that the length of the seal surface is reduced and the sealing ability is reduced. .

  The present invention has been made in order to solve the above-described problems, and provides a hydraulic control device that can prevent the rotation of the annular filter member (prevents rotation) and can ensure the length of the seal surface while having a simple configuration. The purpose is to provide.

In order to achieve the above object, a hydraulic control device according to the present invention includes a sleeve in which a plurality of input ports to which hydraulic oil is supplied and a plurality of output ports to which the hydraulic oil is discharged are formed,
A solenoid valve provided on the sleeve for controlling the flow rate of the hydraulic oil;
A first annular filter member mounted on the sleeve and simultaneously covering the plurality of input ports;
A second annular filter member mounted on the sleeve and simultaneously covering the plurality of output ports;
With
The first annular filter member and the second annular filter member are each provided with a first anti-rotation part and a second anti-rotation part for preventing relative rotation with respect to the sleeve,
The outer wall of the sleeve is provided with a first engaged portion with which the first anti-rotation portion is engaged, and a second engaged portion with which the second anti-rotation portion is engaged,
The first engaged portion and the second engaged portion have different phases.

  Thus, in the present invention, a predetermined interval is provided between the first engaged portion for engaging the first rotation preventing portion and the second engaged portion for engaging the second rotation preventing portion. A phase difference is provided. In other words, the first engaged portion and the second engaged portion are not provided in the same phase. For this reason, a 1st to-be-engaged part and a 2nd to-be-engaged part do not adjoin.

  That is, the first engaged portion and the second engaged portion that are in phase do not face each other. For this reason, since the loss of the length of the seal surface is only for the first engaged portion or only for the second engaged portion, the length of the seal surface is sufficiently secured. For this reason, the space between the sleeve and the mating member is sufficiently sealed

  The phase difference between the first engaged portion and the second engaged portion is set to 180 °, for example. In this case, since the first engaged portion and the second engaged portion are spaced apart to the maximum, it is avoided that the first engaged portion and the second engaged portion are partially opposed. That is, it becomes easier to ensure the length of the sealing surface.

  According to the present invention, a predetermined phase difference is formed between the first engaged portion and the second engaged portion that are formed on the outer wall of the sleeve to engage the rotation preventing portion of the filter. It is intended to be provided at a position where Therefore, the first engaged portion and the second engaged portion are provided in the same phase, in other words, the first engaged portion and the second engaged portion do not face each other. Therefore, the loss of the length of the seal surface is only for the first engaged portion or only for the second engaged portion, and for this reason, the length of the seal surface is sufficiently secured. As a result, it is possible to sufficiently seal between the sleeve and the counterpart material.

It is a principal part schematic sectional drawing of the hydraulic control apparatus which concerns on embodiment of this invention. It is a schematic whole perspective view of the annular filter member which comprises the hydraulic control apparatus of FIG. 3A and 3B, the engaging recess for positioning and fixing the annular filter member of the input port and the engaging recess for positioning and fixing the annular filter member of the output port have a phase difference of about 180 °. FIG. 3C is an enlarged view of the main part of the hydraulic control device, and FIG. 3C is an enlarged view of the main part of the front when the two engaging recesses are provided in the same phase. FIG. 2 is a schematic cross-sectional view of a main part when an input port and an output port in the hydraulic control device of FIG.

  Preferred embodiments of the hydraulic control apparatus according to the present invention will be described below in detail with reference to the accompanying drawings.

  FIG. 1 is a schematic cross-sectional view of a main part of a hydraulic control apparatus 10 according to the present embodiment. The hydraulic control device 10 is a cartridge type that is mounted on an automobile and is attached to a clutch casing 12 that constitutes a clutch. A sleeve 20 that is accommodated in an attachment hole 14 formed in the clutch casing 12, and a sleeve 20 And an electromagnetic valve 22 provided.

  The sleeve 20 has a substantially cylindrical shape, and a valve hole 24 extending along the axial direction of the sleeve 20 is formed therein. A stopper portion 28 on which the spool 26 is seated is provided in the valve hole 24. Further, a first annular groove 30a to a fourth annular groove 30d are formed on the side peripheral wall of the sleeve 20 along the circumferential direction. A plurality of input ports 32 are provided at the bottom of the first annular groove 30a so that a predetermined phase difference is formed between them. Meanwhile, a plurality of output ports 34 and a plurality of drain ports 36 are provided at the bottoms of the second annular groove 30b and the third annular groove 30c so that a predetermined phase difference is formed between them. . The input port 32, the output port 34, and the drain port 36 extend along the diameter direction of the sleeve 20, and communicate with the valve hole 24.

  In the present embodiment, the number of input ports 32, output ports 34, and drain ports 36 is four, and the phase difference between adjacent identical ports is approximately 90 °. FIG. 1 shows two pieces having a phase difference of about 180 °. The input port 32 and the output port 34, and the output port 34 and the drain port 36 are substantially in phase. Although not particularly illustrated, the input port 32, the output port 34, and the drain port 36 communicate with an oil supply path, an oil discharge path, and a drain path formed in the clutch casing 12, respectively.

  Here, a first annular filter member 40 and a second annular filter member 42 made of a metal material are disposed at the bottoms of the first annular groove 30a and the second annular groove 30b, respectively. In other words, the input port 32 and the output port 34 are covered with the first annular filter member 40 and the second annular filter member 42, respectively.

  FIG. 2 is an overall schematic perspective view of the first annular filter member 40. The first annular filter member 40 is configured by a belt-shaped body, which is mostly a mesh portion 44a, being curved in an annular shape and joining both ends that are butted together. That is, the first annular filter member 40 has two protrusions 46a that are formed at one end of the first annular filter member 40 along the longitudinal direction of the band-shaped body (in the direction of arrow X in FIG. 2). The annular shape is maintained by being respectively fitted to the notches 48a. Hereinafter, the joined ends are referred to as “joining portions”, and the reference numeral 50a.

  The width of the protrusion 46a is set so as to increase toward the protruding tip (that is, the other end). On the other hand, the notch 48a has a shape corresponding to the shape of the protrusion 46a, and becomes wider in the depth direction (that is, the direction away from the other end). For this reason, even if the force of the direction which separates both ends acts with respect to the 1st annular filter member 40, it is difficult for the protrusion part 46a to detach | leave from the notch 48a.

  On the outer peripheral edge of the first annular filter member 40, two engagement protrusions 52a (first rotation prevention) as an engagement portion along an axial direction (arrow Y direction in FIG. 2) orthogonal to the longitudinal direction. Part) is formed to protrude. The engagement protrusions 52a extend in directions opposite to each other. The engaging protrusion 52a and the coupling portion 50a are provided at a position where the phase difference between them is approximately 180 °.

  The remaining second annular filter member 42 is configured according to the first annular filter member 40. Therefore, the same components are denoted by reference numerals using “b” instead of the subscript “a”, and detailed description thereof is omitted.

  As shown in FIG. 3A, in the vicinity of the first annular groove 30a of the sleeve 20, engagement recesses 54a (first engaged portions) for engaging the engagement protrusions 52a are formed at two locations. The first annular filter member 40 is positioned and fixed to the sleeve 20 by the engagement protrusions 52a being engaged with the engagement recesses 54a. The engaging recess 54a is formed at a position where a predetermined phase difference (for example, about 45 °) is formed with respect to the input port 32. That is, the engagement protrusion 52a and the coupling portion 50a having a phase difference of about 180 ° with respect to the engagement protrusion 52a are not arranged so as to overlap the input port 32.

  As shown in FIG. 3B, also in the vicinity of the second annular groove 30b, there are two engaging recesses 54b (second engaged portions) for engaging the engaging protrusions 52b (second rotation preventing portions). Is formed. The second annular filter member 42 is positioned and fixed to the sleeve 20 by the engagement protrusion 52b being engaged with the engagement recess 54b. Here, the phase difference between the engaging recess 54b and the engaging recess 54a is approximately 180 °. Accordingly, the phase difference between the coupling portion 50a in the first annular groove 30a and the coupling portion 50b in the second annular groove 30b is also approximately 180 °. For this reason, the engagement protrusion 52a in the 1st annular groove 30a and the connection part 50b in the 2nd annular groove 30b become substantially the same phase. 3A and 3B show a phase in which this state is visually recognized. Since the engaging recess 54b is formed at a position where a predetermined phase difference (for example, about 45 °) is formed with respect to the output port 34, the engaging protrusion 52b and the coupling portion 50b overlap the output port 34. It is never placed.

  An O-ring 56 that seals between the inner wall of the mounting hole 14 and the sleeve 20 is attached to the remaining fourth annular groove 30d. Note that the outer peripheral wall (outer wall) of the portion of the sleeve 20 where the first annular groove 30 a to the fourth annular groove 30 d are not formed serves as a seal surface that comes into contact with the inner wall of the mounting hole 14. Further, the surface of the sleeve 20 facing the electromagnetic valve 22 is a mounting surface for mounting the electromagnetic valve 22, and a fifth annular groove 30 e is formed on the mounting surface. An O-ring 58 that seals between the sleeve 20 and the electromagnetic valve 22 is attached to the fifth annular groove 30e.

  The valve hole 24 accommodates a bottomed cylindrical cap member 60 that closes one end of the valve hole 24 and a long spool 26 in which an inner hole 61 extending along the longitudinal direction is formed. . An annular recess 62 serving as an oil passage for the working oil is formed on the outer peripheral wall of the spool 26. Therefore, the spool 26 has a shape in which a large-diameter portion 64 and a flange portion 66 are formed with the annular recess 62 interposed therebetween. Yes. The large diameter portion 64 and the flange portion 66 are in sliding contact with the inner wall of the valve hole 24.

  In the large diameter portion 64, the inner diameter of the inner hole 61 is large, while in other parts, the inner diameter is small. That is, the inner hole 61 has an inner diameter difference, and therefore, a stepped portion 68 is formed inside the spool 26. Further, the spool 26 is formed with a plurality of lateral holes 70 extending in a direction orthogonal to the longitudinal direction. The inner hole 61 communicates with the pilot chamber 72 through the lateral hole 70.

  The pilot chamber 72 is a part of the valve hole 24 and is a space defined by the flange portion 66, the sleeve 20, and a fixed core 74 described later. Pilot oil for supplying pilot pressure enters and exits the pilot chamber 72 through a breathing hole 76 formed in the cap member 60.

  A return spring 80 is interposed between the cap member 60 and the spool 26. One end of the return spring 80 is seated on the bottom surface of the cap member 60, and the other end is seated on the stepped portion 68. The return spring 80 elastically biases the spool 26 toward the electromagnetic valve 22 side.

  The electromagnetic valve 22 includes a fixed core 74, a bobbin 84 around which the electromagnetic coil 82 is wound, a movable core 86, and a housing 88 that accommodates these. The large-diameter end portion of the fixed core 74 abuts on the mounting surface of the sleeve 20, and the small-diameter cylindrical portion is inserted into the through-hole 90 of the bobbin 84 together with the movable core 86. The tip of the spool 26 is inserted into the hollow interior of the cylindrical portion.

  An annular wall 92 that protrudes into the through hole 90 of the bobbin 84 is formed on the ceiling portion of the housing 88 so as to protrude. The bobbin 84 is supported by the annular wall 92. In addition, a bush 93 made of, for example, resin is fitted into the hollow inside of the annular wall 92. The movable core 86 is inserted in the hollow inside of the bush 93 so as to be displaceable, and comes into sliding contact with the inner wall of the bush 93 when displaced.

  The electromagnetic coil 82 wound around the bobbin 84 is energized from a power source (not shown). With this energization, a magnetic field is formed around the electromagnetic coil 82, and as a result, the movable core 86 is displaced downward in FIG.

  The open end of the housing 88 surrounds the large-diameter end of the fixed core 74 and the vicinity of the mounting surface of the sleeve 20 and is crimped inward in the diameter direction. Thereby, the housing 88 is prevented from coming off from the sleeve 20.

  The hydraulic control device 10 configured as described above is attached to the clutch casing 12 via the attachment stay 94.

  The hydraulic control apparatus 10 according to the present embodiment is basically configured as described above. Next, the function and effect will be described.

  As described above, the first annular filter member 40 bends the belt-shaped body, which is mostly the mesh portion 44a, in an annular shape, and further includes two protrusions 46a protruding from one end of the belt-shaped body. It is obtained by fitting into two notches 48a formed at the ends (see FIG. 2). Here, in order to fit the protruding portion 46a into the notch 48a, for example, one end where the protruding portion 46a is formed is positioned downward, and the other end where the notched portion 48a is formed is positioned upward. The protrusion 46a may be passed through the notch 48a by approaching. Thereby, the coupling | bond part 50a is formed and the 1st annular filter member 40 as an annular body (annular body) is obtained.

  After that, if both ends are released, a force acts to return the toric body to the original band-shaped body. However, in the present embodiment, the width of the protrusion 46a is set so as to increase toward the projecting tip, and the width of the notch 48a is set so as to increase in the depth direction. That is, the cutout 48a has the narrowest opening. It is difficult for the projecting tip of the protruding portion 46a to be separated from the narrowed opening.

  That is, since the width of the protrusion 46a and the notch 48a is set as described above, the protrusion 46a is hooked on the opening of the notch 48a. For this reason, the protrusion 46a is prevented from coming off from the notch 48a, and the first annular filter member 40 can maintain an annular shape. For the same reason, the second annular filter member 42 also maintains an annular shape.

  The first annular filter member 40 thus obtained is installed in the first annular groove 30a. That is, the engagement protrusion 52a is engaged with the engagement recess 54a (see FIG. 3A). As a result, the first annular filter member 40 is positioned and fixed to the sleeve 20. As described above, the coupling portion 50 a and the engagement protrusion 52 a have a phase different from that of the input port 32. In other words, a predetermined phase difference (for example, about 45 °) is formed between the input port 32 and the coupling portion 50a and the engagement protrusion 52a. Of course, the mesh portion 44a faces the input port 32.

  Similarly to the above, the second annular filter member 42 is installed in the second annular groove 30b by engaging the engagement protrusion 52b with the engagement recess 54b (see FIG. 3B). A predetermined phase difference (for example, about 45 °) is formed between the coupling portion 50b and the engagement protrusion 52b and the output port 34, and the coupling portion 50b has a phase difference of about 180 ° with respect to the coupling portion 50a. Become. Of course, the mesh portion 44 b faces the output port 34.

  The hydraulic control device 10 assembled with the first annular filter member 40 and the second annular filter member 42 in this manner is then attached to the clutch casing 12 via the attachment stay 94. At this time, the sleeve 20 is inserted into the mounting hole 14 and the space between the inner wall of the mounting hole 14 and the sleeve 20 is sealed with the O-ring 56.

  The hydraulic control device 10 operates as follows.

  When the electromagnetic coil 82 is not energized and no pilot pressure is applied to the pilot chamber 72, the spool 26 is elastically biased toward the electromagnetic valve 22 by the return spring 80 as shown in FIG. Further, the movable core 86 is most retracted by receiving a bullet urging force of the return spring 80 via the spool 26.

  At this time, the large diameter portion 64 of the spool 26 closes the input port 32 and the annular recess 62 extends from the output port 34 to the drain port 36. For this reason, hydraulic oil is not introduced from the input port 32 into the valve hole 24. That is, the communication between the input port 32 and the output port 34 is cut off, and the hydraulic control device 10 is closed.

  When the electromagnetic coil 82 is energized from this state via the power source, the fixed core 74 is magnetized, and as a result, an electromagnetic force that attracts the movable core 86 is generated. Since this electromagnetic force exceeds the elastic urging force of the return spring 80, the movable core 86 is displaced downward in FIG. 1, that is, toward the fixed core 74 side. At this time, pilot oil that has passed through the breathing hole 76, the inner hole 61, and the lateral hole 70 is introduced into the pilot chamber 72.

  The spool 26 that is pressed by the displaced movable core 86 and receives the pilot pressure at the flange portion 66 is displaced integrally with the movable core 86. Along with this, the return spring 80 contracts. As shown in FIG. 4, the spool 26 stops when seated on the stopper portion 28.

  In this state, the input port 32 and the output port 34 communicate with each other through the annular recess 62. That is, the hydraulic control device 10 is opened. For this reason, the hydraulic oil that has flowed into the valve hole 24 from the input port 32 reaches the output port 34 via the annular recess 62, and further flows out from the output port 34 to the oil discharge path. The hydraulic oil further flows into the clutch through the oil discharge path, and supplies a predetermined clutch pressure. Thereafter, the oil returns to the oil supply path via a predetermined path, and is further resupplied from the input port 32 to the valve hole 24 (annular recess 62).

  During this time, foreign matter may enter the hydraulic oil. Foreign matter reaching the input port 32 is captured by the mesh portion 44a of the first annular filter member 40, and foreign matter reaching the output port 34 from the annular recess 62 is captured by the mesh portion 44b of the second annular filter member 42. On the other hand, the coupling portions 50a and 50b that are not formed with the mesh portions 44a and 44b and do not exhibit the filter function are located at positions where a predetermined phase difference is formed with respect to the input port 32 and the output port 34. For this reason, the inflow to the input port 32 of hydraulic fluid, or the outflow from the output port 34 is not inhibited by the coupling portions 50a and 50b.

  Moreover, the engagement projections 52a and 52b are engaged with the engagement recesses 54a and 54b, respectively, so that the first annular filter member 40 and the second annular filter member 42 are prevented from rotating. Therefore, the first annular filter member 40 and the second annular filter member 42 are prevented from rotating (rotating) along the outer peripheral wall of the sleeve 20 under the pressure of the flowing hydraulic oil. Therefore, it is avoided that the coupling portions 50a and 50b are displaced and overlap the input port 32 and the output port 34.

  That is, when the hydraulic control device 10 is in operation, the coupling portions 50a and 50b are in a position where the input port 32 and the output port 34 are closed, and as a result, the hydraulic oil flows into the input port 32 or is output. It is avoided that the outflow from the port 34 is hindered. Accordingly, the flow rate of the hydraulic oil is prevented from changing.

  In addition, since the coupling portions 50a and 50b do not receive the pressure of the hydraulic oil, there is no concern that the projections 46a and 46b are detached from the notches 48a and 48b. For this reason, the concern that the first annular filter member 40 and the second annular filter member 42 return to the band-shaped body is eliminated.

  In addition, in this case, it is not necessary to overlap both ends of the first annular filter member 40 and the second annular filter member 42. For this reason, it is avoided that the thickness of the 1st annular filter member 40 and the 2nd annular filter member 42 becomes large, and the hydraulic control apparatus 10 enlarges in connection with this.

  Furthermore, each of the first annular filter member 40 and the second annular filter member 42 is a single member, and there is no need to combine other members. That is, the number of parts is small. Further, it is not necessary to weld the first annular filter member 40 and the second annular filter member 42 to the sleeve 20. For this reason, the structure is simplified and the fabrication is easy, and the cost is prevented from rising.

  Here, as shown in FIG. 3C, when the engagement recesses 54a and 54b are in the same phase, the engagement recesses 54a and 54b are close to each other so that the minimum length L2 of the seal surface (see FIG. 3C) is obtained. Shorter. On the other hand, in the present embodiment, the engagement recesses 54a and 54b are positions where a predetermined phase difference (for example, about 180 °) is formed as shown in FIGS. 3A and 3B. For this reason, even if a part of engagement recessed part 54a, 54b does not oppose. Therefore, the minimum length L1 of the sealing surface is sufficient, and as a result, a sufficient sealing capability is obtained.

  After an appropriate amount of hydraulic fluid has circulated, energization from the power source to the electromagnetic coil 82 is stopped. As a result, the electromagnetic force acting on the movable core 86 disappears. Accordingly, the return spring 80 extends to elastically bias the spool 26 and the movable core 86 together. As a result, the spool 26 and the movable core 86 are displaced upward in FIG. 4 to return to the state shown in FIG. That is, the communication between the input port 32 and the output port 34 is cut off, and the hydraulic control device 10 is closed.

  At this time, the pilot oil in the pilot chamber 72 is discharged through the lateral hole 70, the inner hole 61 and the breathing hole 76. Further, the hydraulic oil in the vicinity of the output port 34 is discharged to the drain passage via the drain port 36.

  The present invention is not particularly limited to the above-described embodiment, and various modifications can be made without departing from the gist of the present invention.

  For example, the phase difference between the input port 32, the output port 34, and the coupling portions 50a and 50b may be 30 °, 60 °, or the like. Furthermore, the phase difference between the coupling portion 50a and the coupling portion 50b is not limited to 180 °, and may be 90 °, 125 °, or the like.

  Further, in the above embodiment, the hydraulic control device 10 that controls the hydraulic pressure of the hydraulic fluid of the clutch is illustrated, but the present invention is not limited to the hydraulic control device that controls the hydraulic pressure of an oil pump or the like. It can also be used as a hydraulic control device.

DESCRIPTION OF SYMBOLS 10 ... Hydraulic control apparatus 14 ... Mounting hole 20 ... Sleeve 22 ... Solenoid valve 24 ... Valve hole 26 ... Spool 32 ... Input port 34 ... Output port 36 ... Drain port 40 ... 1st annular filter member 42 ... 2nd annular filter member 44a , 44b ... mesh portions 46a, 46b ... projections 48a, 48b ... notches 50a, 50b ... coupling portions 52a, 52b ... engagement projections 54a, 54b ... engagement recess 61 ... inner hole 62 ... annular recess 64 ... large diameter portion 66 ... Flange 72 ... Pilot chamber 74 ... Fixed core 80 ... Return spring 82 ... Electromagnetic coil 84 ... Bobbin 86 ... Movable core

Claims (2)

A sleeve in which a plurality of input ports to which hydraulic oil is supplied and output ports from which the hydraulic oil is discharged are formed;
A solenoid valve provided on the sleeve for controlling the flow rate of the hydraulic oil;
A first annular filter member mounted on the sleeve and simultaneously covering the plurality of input ports;
A second annular filter member mounted on the sleeve and simultaneously covering the plurality of output ports;
With
The first annular filter member and the second annular filter member are each provided with a first anti-rotation part and a second anti-rotation part for preventing relative rotation with respect to the sleeve,
The outer wall of the sleeve is provided with a first engaged portion with which the first anti-rotation portion is engaged, and a second engaged portion with which the second anti-rotation portion is engaged,
The hydraulic control device according to claim 1, wherein the first engaged portion and the second engaged portion have different phases.   2. The hydraulic control device according to claim 1, wherein a phase difference between the first engaged portion and the second engaged portion is 180 °.

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