JP6909650B2 - Hydraulic control device - Google Patents

Description

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

A hydraulic control device including a solenoid valve controls, for example, the hydraulic pressure of the 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 and an output port for discharging the hydraulic oil from the inside. The valve body constituting the solenoid valve normally closes the input port, and on the other hand, when energized, the valve body is displaced to a position where the input port is opened. As a result, the input port and the output port communicate with each other, and the hydraulic oil input from the input port is output from the output port.

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

Japanese Unexamined Patent Publication No. 2006-22816

The filter member described in Patent Document 1 is composed of an annular body formed by bending a mesh forming a band-shaped body in an annular shape. Then, both ends of the overlap are welded to prevent the band from returning to the strip-shaped body. In such a torus, there is a concern that the filter member orbits (rotates) along the circumferential direction of the sleeve under the pressure of the hydraulic oil flowing through the input port and the output port.

When such a situation occurs, the welded portion overlaps with the input port and the output port, and as a result, the flow of hydraulic oil is hindered. In addition, the joint strength may decrease due to the pressure of the hydraulic oil at the welded portion, and both ends may separate from each other.

In the prior art described in Patent Document 1, an attempt is made to prevent the filter member from rotating by welding both ends to a sleeve when welding the overlapped both ends or by forming a filter member including a resin frame. ing. However, when welding, the sleeve must be made of a weldable material. In addition, since both ends of the strip-shaped body are overlapped with each other, the thickness becomes large. Therefore, the size of the hydraulic control device becomes large.

On the other hand, when the filter member includes the frame, the number of parts increases. Therefore, the assembling work of the filter member becomes complicated and the cost rises.

The present invention has been made to solve the above-mentioned problems, and although it has a simple structure, the annular filter member is prevented from rotating (rotation prevention), and for this purpose, the coupling portion of the annular filter member is an input port or an output. The purpose is to provide a hydraulic control device that can dispel concerns that overlap with the port.

In order to achieve the above object , according to one embodiment of the present invention, 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 to control 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 configured as an annular body having a joint portion in which both abutted ends of a strip-shaped body made of a metal material are joined, and have a phase different from that of the joint portion. The first annular filter member and the second annular filter member are provided with an anti-rotation portion for preventing the second annular filter member from rotating relative to the sleeve, and the coupling portion is the input port or the said. as the output port of phase, the hydraulic control unit through the rotation stopper is positioned and fixed to the sleeve Ru are provided.

By providing the rotation prevention portion in this way, it is possible to prevent the first annular filter member and the second annular filter member from rotating. Therefore, the coupling portion maintains the initial position when the first annular filter member and the second annular filter member are mounted on the sleeve. That is, it is possible to prevent the coupling portion from being displaced so as to overlap the input port or the output port, in other words, the input port and the output port from being blocked by the coupling portion. Therefore, it is possible to prevent the inflow of the hydraulic oil into the input port and the outflow from the output port to be hindered, so that the flow rate of the hydraulic oil can be maintained.

Further, since the coupling portion is located at a position separated from the input port and the output port, the pressure of the hydraulic oil flowing into the input port and the pressure of the hydraulic oil flowing out from the output port do not act on the coupling portion. That is, the joint does not receive the pressure of the hydraulic oil. Therefore, it is possible to prevent the joint portion from being decomposed by the pressure of the hydraulic oil.

Further, the first annular filter member and the second annular filter member are each composed of a single member provided with a rotation prevention portion. Therefore, since the number of parts is small, the configurations of the first annular filter member and the second annular filter member are simplified, and the production becomes easy. Therefore, it is possible to prevent the cost from rising.

Furthermore, in the present invention, both ends of the strip-shaped body to be the first annular filter member and the second annular filter member are butted against each other and joined to each other. That is, the other end is not superimposed on one end. Therefore, it is possible to prevent the first annular filter member, the second annular filter member, and the hydraulic control device from becoming large in size.

In addition, since the first annular filter member and the second annular filter member are not welded to the sleeve, the material of the sleeve is not limited to the one that can be welded. That is, the choice of sleeve material increases.

The connecting portion may include, for example, a protrusion protruding from one end of the band-shaped body along the longitudinal direction and a notch formed at the other end of the band-shaped body. In this case, an annular body can be obtained by fitting the protrusion into the notch.

When this configuration is adopted, it is preferable that the width of the protrusion is set larger toward the tip of the protrusion and the width of the notch is set larger toward the depth direction. In this case, the wide portion of the protrusion is hooked on the narrow opening of the notch, whereby the protrusion is prevented from coming off from the notch. That is, with a simple structure, it is possible to prevent the annular body from returning to the band-shaped body.

A preferred example of the anti-rotation portion is an engaging portion that protrudes along the axial direction of the annular body. In this case, the sleeve may be provided with an engaging recess for engaging the engaging portion. As a result, the first annular filter member and the second annular filter member can be prevented from rotating with a simple structure.

The phase difference between the coupling portion and the rotation prevention portion may be set to, for example, 180 °. In this case, it is easy to position the coupling portion and the rotation prevention portion so that they do not overlap the input port (or output port) at the same time.

According to the present invention, since the first annular filter member and the second annular filter member are configured from a single member provided with the rotation prevention portion, the first annular filter member has a simple structure. It is possible to prevent the second annular filter member from rotating. Therefore, there is a concern that the first annular filter member and the second annular filter member may be displaced from each other, and that the joints may overlap the input port or the output port and block the port. ..

As a result, the flow rate of the hydraulic oil can be maintained. Further, since the coupling portion stays at a position separated from the input port and the output port, the coupling portion is not subjected to the pressure of the hydraulic oil flowing into the input port or the pressure of the hydraulic oil flowing out from the output port. Therefore, it is possible to prevent the joint portion from being decomposed by the pressure of the hydraulic oil. That is, the first annular filter member and the second annular filter member maintain the annular body.

Further, since the first annular filter member and the second annular filter member are each composed of a single member provided with a rotation prevention portion, the number of parts is small, so that the first annular filter member and the second annular filter member are configured. Is simpler and easier to manufacture. Therefore, it is possible to prevent the cost from rising.

It is schematic cross-sectional view of the main part of the hydraulic control device which concerns on embodiment of this invention. FIG. 5 is a schematic overall perspective view of an annular filter member constituting the hydraulic control device of FIG. 1. In FIGS. 3A and 3B, the phase difference between 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 is about 180 °. It is an enlarged view of the front main part of a hydraulic control device, and FIG. 3C is an enlarged view of the front main part when the two engaging recesses are provided in the same phase. It is schematic cross-sectional view of the main part when the input port and the output port in the hydraulic control device of FIG. 1 communicate with each other and are in an open state.

Hereinafter, preferred embodiments of the hydraulic control device according to the present invention will be given and will be described in detail with reference to the accompanying drawings.

FIG. 1 is a schematic cross-sectional view of a main part of the hydraulic control device 10 according to the present embodiment. The hydraulic control device 10 is a cartridge type mounted on an automobile and attached to a clutch casing 12 constituting a clutch, and is a sleeve 20 housed in a mounting hole 14 formed in the clutch casing 12 and the sleeve 20. It has a solenoid 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 inside the sleeve 20. A stopper portion 28 on which the spool 26 is seated is provided in the valve hole 24. Further, on the side peripheral wall of the sleeve 20, the first annular groove 30a to the fourth annular groove 30d are formed along the circumferential direction. A plurality of input ports 32 are provided at the bottom of the first annular groove 30a so as to form a predetermined phase difference between them. On the other hand, 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 as to form a predetermined phase difference 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, respectively.

In the present embodiment, the number of input ports 32, output ports 34, and drain ports 36 is four each, and the phase difference between the same adjacent ports is approximately 90 °. In FIG. 1, two pieces having a phase difference of about 180 ° from each other are shown. The input port 32 and the output port 34 are substantially in phase with each other, and the output port 34 and the drain port 36 are substantially in phase with each other. Although not particularly shown, the input port 32, the output port 34, and the drain port 36 communicate with the oil supply passage, the oil discharge passage, and the drain passage 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 arranged 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 formed by bending a band-shaped body, which is mostly a mesh portion 44a, in an annular shape and joining both abutted ends. That is, the first annular filter member 40 has two protrusions 46a formed on the other end of the first annular filter member 40, which protrude from one end along the longitudinal direction of the strip-shaped body (direction of arrow X in FIG. 2). The ring shape is maintained by being fitted into the notches 48a of the above. Hereinafter, both ends of the bond will be referred to as a “joint portion”, and the reference code thereof will be referred to as 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 toward the depth direction (that is, the direction away from the other end). Therefore, even when a force in the direction of separating both ends acts on the first annular filter member 40, it is difficult for the protrusion 46a to separate from the notch 48a.

Two engaging protrusions 52a (rotation prevention portions) as engaging portions are provided on the outer peripheral edge portion of the first annular filter member 40 along the axial direction (arrow Y direction in FIG. 2) orthogonal to the longitudinal direction. Is formed as a protrusion. The engaging protrusions 52a extend in directions opposite to each other. The engaging projection 52a and the coupling portion 50a are provided at positions 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 component is designated by a reference numeral using "b" instead of the subscript "a", and detailed description thereof will be omitted.

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

As shown in FIG. 3B, engaging recesses 54b for engaging the engaging protrusions 52b are also formed at two locations in the vicinity of the second annular groove 30b. By engaging the engaging projection 52b with the engaging recess 54b, the second annular filter member 42 is positioned and fixed to the sleeve 20. Here, the phase difference between the engaging recess 54b and the engaging recess 54a is approximately 180 °. Therefore, 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 °. Therefore, the engaging projection 52a in the first annular groove 30a and the coupling portion 50b in the second annular groove 30b are substantially in phase with each other. 3A and 3B show the phases in which this state is visually recognized. Since the engaging recess 54b is formed at a position having a predetermined phase difference (for example, about 45 °) with respect to the output port 34, the engaging projection 52b and the coupling portion 50b overlap with the output port 34. It will not be placed.

An O-ring 56 that seals between the inner wall of the mounting hole 14 and the sleeve 20 is mounted on the remaining fourth annular groove 30d. The outer peripheral wall (outer wall) of the sleeve 20 where the first annular groove 30a to the fourth annular groove 30d are not formed is a sealing surface that abuts on the inner wall of the mounting hole 14. Further, the surface of the sleeve 20 facing the solenoid valve 22 is a mounting surface on which the solenoid valve 22 is mounted, and a fifth annular groove 30e is formed on the mounting surface. An O-ring 58 that seals between the sleeve 20 and the solenoid valve 22 is mounted on 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 having an inner hole 61 extending along the longitudinal direction. .. An annular recess 62, which serves as an oil passage for hydraulic 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. There is. The large diameter portion 64 and the flange portion 66 are in sliding contact with the inner wall of the valve hole 24.

The inner diameter of the inner hole 61 is large in the large diameter portion 64, while the inner diameter is small in other portions. That is, there is a difference in inner diameter between the inner holes 61, and therefore, a step 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 via the lateral hole 70.

The pilot chamber 72 is a part of the valve hole 24, and is a space defined by a flange portion 66, a sleeve 20, and a fixed core 74 described later. Pilot oil that supplies 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 step portion 68. The return spring 80 directs the spool 26 toward the solenoid valve 22 and urges the spool 26 to repel.

The solenoid valve 22 has a fixed core 74, a bobbin 84 around which an electromagnetic coil 82 is wound, a movable core 86, and a housing 88 that accommodates them. The large-diameter end of the fixed core 74 is in contact with 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 inside of the cylindrical portion.

An annular wall 92 that enters the through hole 90 of the bobbin 84 is projected from the ceiling of the housing 88. The bobbin 84 is supported by the annular wall 92. Further, for example, a bush 93 made of resin is fitted in the hollow inside of the annular wall 92. The movable core 86 is displaceably inserted into the hollow interior of the bush 93, and when displaced, it is in sliding contact with the inner wall of the bush 93.

The electromagnetic coil 82 wound around the bobbin 84 is energized from a power source (not shown). A magnetic field is formed around the electromagnetic coil 82 with this energization, 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 radial direction. As a result, the housing 88 is prevented from coming off from the sleeve 20.

The hydraulic control device 10 configured in this way is attached to the clutch casing 12 via the attachment stay 94.

The hydraulic control device 10 according to the present embodiment is basically configured as described above, and the effects thereof will be described next.

As described above, the first annular filter member 40 has a band-shaped body, which is mostly a mesh portion 44a, curved in an annular shape, and further has two protrusions 46a protruding from one end of the band-shaped body. It is obtained by fitting each of the two notches 48a formed at the ends (see FIG. 2). Here, in order to fit the protrusion 46a into the notch 48a, for example, one end where the protrusion 46a is formed is positioned downward and the other end where the notch 48a is formed is positioned upward, and both are positioned along the vertical direction. The protrusion 46a may be passed through the notch 48a in close proximity. As a result, the coupling portion 50a is formed, and the first annular filter member 40 as an annular body (annular body) is obtained.

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

That is, since the widths of the protrusion 46a and the notch 48a are set as described above, the protrusion 46a is hooked on the opening of the notch 48a. Therefore, the protrusion 46a is prevented from coming off from the notch 48a, and the first annular filter member 40 can maintain the 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 engaging protrusion 52a is engaged with the engaging 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 50a and the engaging protrusion 52a 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 engaging projection 52a. Of course, the mesh portion 44a faces the input port 32.

In the same manner as described above, the second annular filter member 42 is installed in the second annular groove 30b by engaging the engaging protrusion 52b with the engaging recess 54b (see FIG. 3B). A predetermined phase difference (for example, about 45 °) is formed between the coupling portion 50b and the engaging projection 52b and the output port 34, and the coupling portion 50b has a phase difference of approximately 180 ° with respect to the coupling portion 50a. Become. It goes without saying that the mesh portion 44b faces the output port 34.

The hydraulic control device 10 to which the first annular filter member 40 and the second annular filter member 42 are assembled in this way is subsequently 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 inner wall of the mounting hole 14 and the sleeve 20 are sealed with an O-ring 56.

The hydraulic control device 10 operates as follows.

When the electromagnetic coil 82 is not energized and the pilot pressure is not applied to the pilot chamber 72, the spool 26 is elastically urged toward the solenoid valve 22 by the return spring 80 as shown in FIG. Further, the movable core 86 is most retracted by receiving the elastic 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. Therefore, the hydraulic oil is not introduced into the valve hole 24 from the input port 32. That is, the communication between the input port 32 and the output port 34 is cut off in a non-communication (communication cutoff) state, and the hydraulic control device 10 is in a closed state.

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

In this state, the input port 32 and the output port 34 communicate with each other via the annular recess 62. That is, the flood control device 10 is opened. Therefore, 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 to supply a predetermined clutch pressure. After that, 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 be mixed in the hydraulic oil. The foreign matter that has reached the input port 32 is captured by the mesh portion 44a of the first annular filter member 40, and the foreign matter that has reached 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, in which the mesh portions 44a and 44b are not formed 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. Therefore, the inflow of the hydraulic oil into the input port 32 or the outflow from the output port 34 is not hindered by the coupling portions 50a and 50b.

Moreover, the engaging protrusions 52a and 52b are engaged with the engaging recesses 54a and 54b, respectively, to prevent the first annular filter member 40 and the second annular filter member 42 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 from each other and overlap with the input port 32 and the output port 34.

That is, the coupling portions 50a and 50b are positioned to block the input port 32 and the output port 34 during the operation of the hydraulic control device 10, and due to this, the hydraulic oil flows into or outputs to the input port 32. It is avoided that the outflow from the port 34 is hindered. Therefore, the flow rate of the hydraulic oil is prevented from changing.

In addition, since the coupling portions 50a and 50b are not subjected to the pressure of the hydraulic oil, there is no concern that the protrusions 46a and 46b will be separated from the notches 48a and 48b. Therefore, the concern that the first annular filter member 40 and the second annular filter member 42 return to the strip-shaped body is eliminated.

Moreover, in this case, it is not necessary to superimpose both ends of the first annular filter member 40 and the second annular filter member 42. Therefore, it is possible to prevent the thickness of the first annular filter member 40 and the second annular filter member 42 from increasing, and to prevent the hydraulic control device 10 from increasing in size accordingly.

Further, the first annular filter member 40 and the second annular filter member 42 are each a single member, and it is not necessary 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. Therefore, the structure is simplified, the production is easy, and the cost rise is avoided.

Here, when the engaging recesses 54a and 54b are in the same phase as shown in FIG. 3C, the engaging recesses 54a and 54b are close to each other so as to face each other, so that the minimum length L2 of the sealing surface (see FIG. 3C) is set. It gets shorter. On the other hand, in the present embodiment, the engaging recesses 54a and 54b are positioned so that a predetermined phase difference (for example, about 180 °) is formed with each other as shown in FIGS. 3A and 3B. Therefore, the engaging recesses 54a and 54b do not face each other even in part. Therefore, the minimum length L1 of the sealing surface becomes sufficient, and as a result, a sufficient sealing ability can be obtained.

After an appropriate amount of hydraulic oil has been circulated, the energization of the electromagnetic coil 82 from the power source is stopped. Along with this, the electromagnetic force acting on the movable core 86 disappears. Therefore, the return spring 80 expands and elastically urges the spool 26 and the movable core 86 integrally. As a result, the spool 26 and the movable core 86 are displaced upward in FIG. 4 and 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 flood 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 and the output port 34 and the coupling portions 50a and 50b may be 30 °, 60 °, or the like. Further, 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 for controlling the hydraulic pressure of the hydraulic oil of the clutch is illustrated, but the present invention includes, for example, a hydraulic control device for controlling the hydraulic pressure of an oil pump or the like. It can also be used as a hydraulic control device.

10 ... Hydraulic control device 14 ... Mounting hole 20 ... Sleeve 22 ... Solenoid valve 24 ... Valve hole 26 ... Spool 32 ... Input port 34 ... Output port 36 ... Drain port 40 ... First annular filter member 42 ... Second annular filter member 44a , 44b ... Mesh portions 46a, 46b ... Protrusions 48a, 48b ... Notches 50a, 50b ... Couplings 52a, 52b ... Engagement protrusions 54a, 54b ... Engagement recesses 61 ... Inner holes 62 ... Annular recesses 64 ... Large diameter portion 66 ... Flange 72 ... Pilot chamber 74 ... Fixed core 80 ... Return spring 82 ... Solenoid coil 84 ... Bobbin 86 ... Movable core

Claims (3)

A plurality of input ports which hydraulic oil is supplied, a plurality of output ports which the operating oil is discharged to a hydraulic control device comprising a sleeve of cylindrical shape made form,
A plurality of annular grooves extending along the circumferential direction are formed in parallel on the side peripheral wall of the sleeve along the axial direction of the sleeve.
The plurality of input ports are opened at the bottom of the first annular groove among the plurality of annular grooves at positions separated from each other along the circumferential direction, and the plurality of output ports are the plurality of. At the bottom of the second annular groove among the annular grooves, openings are made at positions separated from each other along the circumferential direction.
A solenoid valve provided at one end of the sleeve in the axial direction to control the flow rate of the hydraulic oil,
A first band-shaped body made of a metal material having a first mesh portion is curved in an annular shape, and is configured as an annular body having a first joint portion in which both abutted ends of the first band-shaped body are joined. , A first annular filter member mounted in the first annular groove and simultaneously covering the plurality of input ports with the first mesh portion.
A second band-shaped body made of a metal material having a second mesh portion is curved in an annular shape, and is configured as an annular body having a second joint portion in which both abutted ends of the second band-shaped body are joined. , A second annular filter member mounted in the second annular groove and simultaneously covering the plurality of output ports with the second mesh portion.
With
The first band shape and the second band shape each project from one end in the circumferential direction along the circumferential direction, and a plurality of protrusions whose widths are set larger toward the protruding tip and the circumferential direction. It has a plurality of notches formed at the other end of the above and whose width is set larger toward the depth direction, and the plurality of protrusions are individually fitted into the plurality of notches. The first joint portion and the second joint portion are configured.
The first annular filter member and the second annular filter member are provided in a phase different from the first coupling portion and the second coupling portion by 180 ° in the circumferential direction, and the first annular filter member and the second annular filter member and the second annular filter member. Each has an anti-rotation portion that prevents the filter member from rotating relative to the sleeve.
The rotation prevention portion is a pair of engaging protrusions protruding in opposite directions along the axial direction of the sleeve.
The first annular filter member and the second annular filter member are located between the input ports adjacent to each other in the circumferential direction or between the output ports at the bottoms of the first annular groove and the second annular groove, respectively. as the first coupling portion and the second coupling portion is a phase you positioned between the hydraulic control apparatus characterized by being positioned and fixed to the sleeve via the pair of engaging projections .. In the hydraulic control device according to claim 1, the first mesh portion of the first annular filter member and the second mesh portion of the second annular filter member are formed between the pair of engaging protrusions. A hydraulic control device characterized by the fact that. The hydraulic control apparatus according to claim 1 or 2, wherein the side wall of the front Symbol sleeve, the hydraulic control apparatus characterized by a pair of engaging recesses for engaging the pair of engaging projections are formed ..

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