JPH08192761A - Fluid passage control valve - Google Patents

Abstract

PURPOSE: To shorten a spool, and attain high rigidity by providing a cylindrical spool having a communicating part which has the same circumferential surface with a sealing part and in which a guiding object part to be slidably guided by a support guide part is formed in the shaft direction. CONSTITUTION: Voltage is impressed on an electromagnetic actuator 40, and when a plunger 42 elongates, a spool 30 moves leftward in the shaft direction agaist energizing force of a coil spring 44, and an A port 21 is opened to a P port 23. At this time, since the spool 30 moves in the shaft direction in a sleeve 20 when a guiding object part 36 formed in passages 31a and 31b slidingly moves on a support guide part 28 of the sleeve 30, there is no need to make the land 32 function as a guide part. Therefore, the total length of the spool 30 is shortened, and a fluid passage control valve OCI itself is downsized.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to communication, blocking,
Regarding the fluid path control valve for controlling the direction switching etc.,
More specifically, the present invention relates to a spool type fluid passage control valve that controls a fluid passage by moving a spool in a sleeve in an axial direction.

[0002]

2. Description of the Related Art Conventionally, a fluid path control valve has been used to switch the operating direction of a fluid actuating device (actuator) driven by a fluid. For example, it is applied to an actuator using oil as a fluid. Is widely known. In recent years, spool type fluid path control valves have been widely used for actuators that require high pressure and large discharge amounts. Here, an example of a spool type fluid passage control valve OC3 that has been conventionally used will be described with reference to FIG.

The fluid passage control valve OC3 has a cylindrical sleeve 70 having a plurality of ports, a spool 75 disposed in the sleeve 70 and switching the direction of oil flow by sliding in the axial direction, and a spool 75. And an electromagnetic actuator 78 for axially driving.

The sleeve 70 has a pressure port (P port 7) to which an oil pump 80 for pumping oil is connected.
1), a pressure operating device connection port (A port 72, B port 73) to which a hydraulic cylinder 81 as a pressure operating device is connected, and a reservoir port (R port 74) to which a reservoir tank 83 is connected. ing.

Further, the spool 75 has a P port 71 and A and B ports 72 and 73, or A and B ports 7.
Lands 76 that seal the flow of oil between the ports 2, 73 and the R port 74 are formed. In addition, spool 7
5 has a diameter smaller than that of the land 76, so that the P port 71 and the A and B ports 72 and 73, or the A and B ports.
A passage 77 is formed which connects the ports 72 and 73 and the R port 74.

The lands 76a formed on both ends of the spool 75 function as a guided portion guided by the sleeve 70 when the spool 75 moves in the axial direction. When the spool 75 is in the neutral position, the A and B ports 72 and 73 are closed by the land 76 from the P port 71.

Further, the electromagnetic actuator 78 includes a coil 78a and a plunger 78b which is driven to expand and contract by applying a voltage to the coil 78a.
In the fluid path control valve OC3 having such a configuration, when the spool 75 is in the neutral position, a voltage is applied to the electromagnetic actuator 78 and the extended plunger 78b.
Pushes the spool 75 to the left in the drawing, the P port 71
And A port 72 are connected, and B port 73 and R are also connected.
The port 74 is communicated.

Therefore, the hydraulic pressure is applied to the first pressure chamber 82a of the hydraulic cylinder 81 connected to the A port 72, and the piston 81a moves toward the second hydraulic chamber 82b connected to the B port 73, The oil in the second pressure chamber 82b flows toward the B port 73 and is returned to the reservoir tank 83 via the R port 74.

On the other hand, when the plunger 78b is contracted, the P port 71 and the B port 73 are communicated with each other, and the A port 72 and the R port 74 are communicated with each other. Therefore, the hydraulic cylinder 8 connected to the B port 73
The hydraulic pressure is applied to the second pressure chamber 82b of the first
a moves toward the first hydraulic chamber 82a connected to the A port 72, the oil in the first pressure chamber 82a flows toward the A port 72, and returns to the reservoir tank 83 via the R port 74. Be done.

Further, Japanese Patent Publication No. 5-18752 discloses that
A spool type fluid path control valve used as a control valve for power steering is disclosed. Such a control valve is also the above-mentioned fluid path control valve OC.
The direction of the oil flow is controlled by basically the same operation as in 3.

[0011]

However, in the power steering control valve disclosed in the fluid passage control valve OC3 and Japanese Patent Publication No. 518752/1993, the sleeve 70 causes the spool 75 to move in the axial direction. In order to be guided, the lands 76a as guided parts had to be separately provided at both ends of the spool 75. That is, the sleeve 70 has the annular groove portion 70a having an opening area larger than the opening area of the port in order to ensure the flow passage even when the land 76 does not completely open each port. ing. Also,
Since the passage 77 of the spool 75 is formed to have a diameter smaller than that of the land 76 over the entire circumference thereof, it cannot function as a guide portion. Then, a chamfer 79a at the boundary between the passage 77 and the land 76
Although the chamfer 79b of the groove 70a partially overlaps with each other, the degree of the overlap is extremely small, and it is difficult to say that the spool 75 is guided by the sleeve 70.

Therefore, there is no choice but to form a land 76a as a guided portion guided by the sleeve 70 when the spool 75 moves at both ends of the spool 75 that does not affect the valve function, and the fluid path is formed. The total length of the control valve OC3 is inevitably long, and there is a problem that it is difficult to save space and increase the rigidity of the spool. Also,
Improvements in processing efficiency and processing accuracy of the spool 75 have been hindered by the lengthening of the spool 75, the multiple formation of the passage 77, and the like.

Particularly, in the open center type fluid path control valve, the width of the land of the spool is formed narrower than the width of the annular groove portion of the sleeve, and the edge portion of the land and the edge portion of the groove portion are different from each other. It will not overlap at all. Therefore, it is indispensable to form the guide portions on both ends of the spool.

The present invention has been made in order to solve the above-mentioned conventional problems, and an object of the present invention is to shorten the spool and increase the rigidity thereof. Therefore, the fluid path control valve can be made compact and durable. The purpose is to improve.

[0015]

In order to achieve the above object, a fluid path control valve according to the invention of claim 1 has a plurality of connection ports and a support guide portion formed along the inner peripheral surface. A bottom-cylindrical sleeve, a sealing portion that seals a fluid flow between predetermined ports among the ports, and a predetermined port among the ports that communicates with each other and has the same circumference as the sealing portion. A cylindrical spool having a communicating portion that has a surface and that is guided in a slidable manner by the support guide portion and that is formed in the axial direction.

A fluid passage control valve according to a second aspect of the present invention is the fluid passage control valve according to the first aspect, wherein the communicating portion is formed at a substantially central position of the spool, and the support guide portion is formed. As a configuration, the sleeve is formed at a substantially central position corresponding to the communication portion.

Further, a fluid passage control valve according to a third aspect of the present invention is the fluid passage control valve according to the first or second aspect, wherein the support guide portion has an annular shape along an inner peripheral surface thereof. It is provided with a structure that a groove is formed.

[0018]

In the fluid path control valve according to the invention of claim 1 having the above-mentioned structure, the desired ports are communicated with each other by the communication portion formed in the spool, and the fluid is circulated between the desired ports. Moreover, the desired ports are sealed by the sealing portion formed on the spool, and the fluid flow between the desired ports is sealed.

Here, on the inner peripheral surface of the sleeve, a support guide portion for supporting the spool and guiding the movement of the spool is formed. Further, in the communicating portion of the spool, a guided portion that has the same peripheral surface as the sealing portion and is guided by the support guide portion is formed in the axial direction.

Therefore, the spool moves axially in the sleeve when the guided portion formed in the communicating portion is guided by the support guide portion of the sleeve. In this way, the communicating portion communicates between the predetermined ports and also has a function of being guided by the support guide portion when the spool moves, so that it is not necessary to form an independent guided portion separately from the communicating portion. Therefore, the fluid path control valve can be shortened.

Further, in the fluid path control valve according to the second aspect of the present invention, the communication portion is formed at a substantially central position of the spool, and the support guide portion is formed at a substantially central position of the sleeve corresponding to the communication portion. There is. Therefore, the center of gravity of the spool and the support position are close to each other, and the spool is supported in a balanced manner with respect to the sleeve, and the movement of the spool within the sleeve is facilitated.

Further, in the fluid path control valve according to the invention of claim 3, an annular groove portion is formed along the inner peripheral surface of the support guide portion. Therefore, even when the sleeve does not have the number of fluid supply means connection ports different from the number of guided parts, the fluid supply means connection ports are not directly blocked by the guided parts and the fluid is It is supplied into the sleeve through the annular groove.

[0023]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Several embodiments in which the fluid path control valve according to the present invention is embodied as an oil control valve will be described below with reference to the drawings.

The fluid passage control valve OC1 according to the first embodiment will be described with reference to FIGS. First, the configuration of the fluid path control valve OC1 according to the first embodiment will be described with reference to FIG. FIG. 1 is an overall configuration diagram of a hydraulic control system using the fluid path control valve OC1 according to the first embodiment.

The fluid path control valve OC1 comprises a cylindrical sleeve 20, a cylindrical spool 30 arranged in the sleeve 20, and an electromagnetic actuator 40 for moving the spool 30 in the axial direction. Also, the fluid path control valve O
C1 is connected to a hydraulic cylinder 11 as a pressure operating device, an oil pump 13 as a fluid supply means, and a reservoir tank 15 as a fluid tank.

The sleeve 20 has an actuator connection port (A port 21, B port 22) to which the hydraulic cylinder 11 is connected via the oil pipe 14 and the oil pipe 1.
It has a pressure port (P port 23) to which the oil pump 13 is connected via 4 and a reservoir port (R port 24) to which the reservoir tank 15 is connected via the oil pipe 14.

Four P-ports 23 are arranged on the circumferential surface of the sleeve 20 at intervals of 90 degrees.
Is an annular groove portion 25 provided on the outer circumference of the sleeve 20.
Are connected to each other via. Therefore, even if the number of the oil pipes 14 connected to the oil pump 13 is one, the oil is uniformly supplied from the four P ports 23 into the sleeve 20.

The A port 21 and the B port 22 are arranged on both sides of the P port 23 below the sleeve 20 in FIG. 1, and the A port 2 is provided via the oil pipe 14.
Reference numeral 1 is connected to the first pressure chamber 12a of the hydraulic cylinder 11, and B port 22 is connected to the second pressure chamber 12b of the hydraulic cylinder 11.

An annular groove 2 is formed on the inner peripheral surface of the sleeve 20 in which the A port 21 and the B port 22 are arranged.
6 and 27 are provided to improve the responsiveness of oil flow when communicating with the ports. The convex portion sandwiched by the two annular groove portions 26 and 27 guides the movement of the spool 30 in the axial direction, and
A support guide portion 28 that supports 0 is formed.

The R port 24 is the sleeve 2 in FIG.
It is arranged in the vicinity of the base end on the upper side of 0 and is connected to the reservoir tank 15 via the oil pipe 14. A cap 43 is fitted on the tip of the sleeve 20,
Further, a coil spring 44 that urges the spool 30 in a contracting direction of a plunger 42 (described later) is interposed between the tip of the spool 30 and the cap.

The electromagnetic actuator 40 includes a coil 41.
And a plunger 42 that expands when a voltage is applied to the coil 41 and expands and contracts when the applied voltage is removed.

Next, the structure of the spool 30 is shown in FIG.
~ It demonstrates in detail with reference to FIG. As shown in FIG.
The spool 30 is formed with passages 31a, 31b, 31c near the center thereof for communicating the ports, and at both ends of the spool 30 where the passages 31a, 31b, 31c are not formed, Lands 32 are formed to seal the flow of oil in. Further, a contact portion 33 with which the coil spring 44 is brought into contact is provided at the tip of the spool 30, and the contact portion 33 is recessed.
An oil communication hole 34a is provided as shown in FIG. Further, the rear end of the spool 30 is formed in a substantially conical shape with a flat top portion, and its slope has four oil communication holes 34c as shown in FIG.

As shown in the side sectional view of FIG. 3, the spool 30 has an oil communication passage 34b therein, which communicates the front end of the spool 30 with the rear end of the spool 30. 34b is connected to the oil communication hole 34a at the front end, is branched near the rear end, and is then connected to the oil communication hole 34c. And spool 3
Front end side chamber 35a and rear end side chamber 3 defined by 0
5b allows the oil to flow mutually through the oil communication passage 34b and the oil communication holes 34a, 34b.

The passages 31a, 31b, 31c are formed by cutting out a part of the circumference in a direction perpendicular to the axial direction of the spool 30, and as shown in FIG. If formed, it is formed in a rectangular shape. In addition, the land 32 is attached to the passages 31a, 31b, 31c.
A guided portion 36 having the same circumferential surface as that is formed in the axial direction so as to connect both lands 32.

In this embodiment, three passages 31
a, 31b, 31c, and three guided portions 36 are formed, and when the spool 30 is cut along the line AA in FIG. 3, the cross section has a substantially triangular shape as shown in the sectional view of FIG. Presents.

The guided portion 36 is a portion that slides and is guided by the supporting guide portion of the sleeve 20 when the spool 30 moves in the sleeve 20 in the axial direction, and is the same portion as the passages 31a, 31b, 31c. Is formed in. When the spool 30 is arranged in the sleeve 20, the passages 31a, 31b, 31c are divided into three parts by the guided portion 36.

The edges 37a, 37b at the boundary between the passages 31a, 31b, 31c and the land 32,
37c are formed at positions displaced from each other as shown in FIGS. 2, 5, and 8. Here, FIG. 8 shows the passage 31
3 is an enlarged sectional view showing edges 37a, 37b, 37c at boundaries between a, 31b, 31c and a land 32 and edges 29 of annular groove portions 26, 27 in the sleeve 20. FIG.

The edges 37a, 37b and 37c are
Originally, they are formed in the same plane, but here they are shown overlaid for comparison. Also, the passages 31a, 31
edge 37 at the boundary between b, 31c and land 32
The edges a of the annular groove portions 26, 27 of the sleeves 20, a, 37b, 37c are exaggerated for ease of explanation.

Next, the operation of the fluid path control valve OC1 according to the first embodiment having the above construction will be described with reference to the drawings. Here, the fluid path control valve OC1 is initially set as shown in FIG.
Each land 32 blocks the A port 21 (annular groove portion 26) and P port 23, and the B port 22 (annular groove portion 27) and P port 23, the oil pump 13 is driven, and the passages 31a and 31b from the P port 23 are driven. , 31c, the oil is being pumped. Further, each oil circuit including each pressure chamber 12a, 12b of the hydraulic cylinder 11 is assumed to be filled with oil.

When a voltage is applied to the electromagnetic actuator 40 and the plunger 42 extends, the spool 30 moves to the left along the axial direction against the urging force of the coil spring 44 and moves to the A port 21 (circle). The annular groove 26) is opened to the P port 23. At this time, the spool 30
The guided portions 36 formed on the passages 31a, 31b, 31c slide in the support guide portions 28 of the sleeve 20 to move in the sleeve 20 in the axial direction, so that the lands 32 function as guide portions. You don't have to.

Therefore, unlike the conventional fluid passage control valve OC3 having the land 32 that functions as a guide portion, the total length of the spool 30 is shortened and the fluid passage control valve O is reduced.
C1 itself is miniaturized.

When the A port 21 is opened to the P port 23, the passages 31a, 31b, 31c located farther from the inner peripheral surface of the sleeve 20 than the land 32 are.
And the P port 2 through the gap on the inner peripheral surface of the sleeve 20.
3 is communicated with the A port 21. Then, the oil supplied from the oil pump 13 to the P port 23 reaches the A port 21 through the gap between the passages 31 a, 31 b, 31 c and the inner peripheral surface of the sleeve 20, and the oil is supplied from the A port 21 via the oil pipe 14. Is supplied to the first pressure chamber 12a of the hydraulic cylinder 11.

Here, four P ports 23 are provided on the peripheral surface of the sleeve 20, and the number of the guided portions 36 formed is three.
Different from one. Therefore, even if any one of the P ports 23 is blocked by the guided portion 36, the remaining P ports 23 are never blocked, and smooth oil supply is realized.

Thus, when oil is supplied to the first pressure chamber 12a of the hydraulic cylinder 11, the hydraulic pressure of the first pressure chamber 12a becomes higher than the hydraulic pressure of the second pressure chamber 12b, and the piston 11a moves to the right (second By moving to the pressure chamber 12b side), the hydraulic cylinder 11 acts as a pressure actuating device. On the other hand, oil is discharged from the second pressure chamber 12b pressed by the piston 12a, and the discharged oil is supplied from the B port 22 to the rear end side chamber 35b in the sleeve 20 via the oil pipe 14. The oil supplied to the rear end side chamber 35b in the sleeve 20 is R
It is returned from the port 24 to the reservoir tank 15 via the oil pipe 14.

Subsequently, when the voltage applied to the electromagnetic actuator 40 is removed, the plunger 42 and the
The spool 30 moves to the right with the urging force of the coil spring 44, the A port 21 is closed with respect to the P port 23, and the supply of oil to the first pressure chamber 12a of the hydraulic cylinder 11 is stopped. Even in such a case, the spool 30 moves in the sleeve 20 in the axial direction by the guided portion 36 being supported and guided by the support guide portion 36 of the sleeve 20.

At the same time, the B port 22 becomes the P port 2
3, the P port 23 and the B port 22 are communicated with each other via the passages 31a, 31b, 31c.
Therefore, from the oil pump 13 to the oil pipe 14,
The oil that has passed through the P port 23 and is supplied into the sleeve 20 reaches the B port 22 through the passages 31a, 31b, 31c. Then, the oil reaching the B port 22 passes through the oil pipe 14 and the hydraulic cylinder 11
Is supplied to the second pressure chamber 12b, and the hydraulic pressure in the second pressure chamber 12b gradually rises. As a result, the second pressure chamber 12
When the hydraulic force of b is higher than that of the first pressure chamber 12a, the piston 12a moves to the left (the first pressure chamber 12a
Side) to start moving.

On the other hand, surplus oil is discharged from the first pressure chamber 12a pressed by the piston 12a, and the discharged oil passes through the oil pipe 14 and the A port 21.
Is returned to the tip side chamber 35a in the sleeve 20. Then, the oil returned to the front end side chamber 35a in the sleeve 20 is sealed with the B port 22 via the communication hole 34a at the tip of the spool 30, the communication passage 34b inside the spool 30, and the communication hole 34c at the rear end of the spool 30. Rear end side chamber 35b
To reach. Thus, the oil that has reached the rear end side chamber 35b is returned from the R port 24 to the reservoir tank 15 via the oil pipe 14.

Next, the fluid path control valve OC according to the first embodiment.
1, the passages 31a, 31b of the spool 30,
An edge 37a at the boundary between 31c and the land 32,
The hydraulic pressure characteristics of 37b and 37c will be described with reference to FIGS. 8, 9, 13, and 14. FIG. 9 is a graph showing the hydraulic characteristics of the fluid path control valve OC1 in the case where the edges 37a, 37b, 37c shown in FIG. 8 are provided, where the vertical axis left shows the hydraulic pressure and the vertical axis right shows the opening area. Shows,
The horizontal axis indicates the spool stroke.

FIG. 13 shows a chamfer 79a at the boundary between the passage 77 and the land 76 of the spool 75 which constitutes the conventional fluid passage control valve OC3.
Further, FIG. 14 is a graph showing the hydraulic pressure characteristic of the fluid path control valve OC3 in the case where the chamfer 79a shown in FIG. 13 is provided. The vertical axis left shows the hydraulic pressure, the vertical axis right shows the opening area, and the horizontal axis is the horizontal axis. The spool stroke is shown.

In the conventional spool 75, a chamfer 79a as shown in FIG. 13 is formed at the boundary between the land 76 and the passage 77 in order to obtain desired hydraulic characteristics. Without the chamfer 79a, as shown by the solid line in FIG. 14, the amount of change in the opening area with respect to the spool stroke becomes large, and accordingly, the amount of change in hydraulic pressure with respect to the spool stroke also becomes large. As a result, from the A port 72, the B port 73 to the hydraulic cylinder 81
However, the accuracy of control of the oil flow rate (hydraulic pressure) supplied to the actuator has decreased, and it has been difficult to obtain a desired operation. In order to solve this, conventionally, a chamfer 79a was formed, but a chamfering process is required in the production process,
The spool was expensive.

On the other hand, in the spool 30 according to the first embodiment, the passages 31a, 31b, 31c are notched so as to be displaced in the axial direction, and the edges 37a, 37b,
37c is also formed to be displaced. Such an edge 37a,
In the case of including 37b, 37c, the edges 37a, 3
The opening area changes every 7b and 37c (FIG. 9).
A, b, and c on the horizontal axis are the edges 37a, 37b, and 3
7c shows the opening start position of 7c. ).

Therefore, as compared with the spool 75 of the conventional example, the amount of change in the opening area with respect to the spool stroke can be switched stepwise. As a result, the amount of change in hydraulic pressure with respect to the spool stroke also becomes gradual, and A
The control of the oil flow rate (hydraulic pressure) supplied to the actuator such as the hydraulic cylinder 11 from the port 21 and the B port 22 is accurately performed.

Further, it is generally known that the hydraulic characteristics largely depend on the width of the passage. Here, in the present embodiment, the edges 37a, 37b, 37c are formed at positions displaced from each other, so that the edges 37a, 37b, 37c can behave as if they have a plurality of passage widths. Various hydraulic characteristics are realized by the valve OC1).

Next, the fluid path control valve OC according to the second embodiment.
2 will be described with reference to FIG. Since the basic configuration of the fluid path control valve OC2 according to the second embodiment is the same as the configuration of the fluid path control valve OC1 according to the first embodiment, the same components are designated by the same reference numerals and their description is omitted. Will be omitted and only different components will be described.

The structure of the fluid path control valve OC2 according to the second embodiment differs from the structure of the fluid path control valve OC1 according to the first embodiment in the shape of the sleeve 50. That is, in the sleeve 20 of the first embodiment, four P ports 23 are arranged at 90 degree intervals, and each P port 23 is connected by the annular groove portion 25 provided on the outer circumference of the sleeve 20.

On the other hand, in the sleeve 50 of the second embodiment, P
Only one port 51 is arranged on the peripheral surface of the sleeve 50,
An annular groove portion 52 is provided on the inner peripheral surface of the sleeve 50. That is, the guided portion 36 comes into contact with the annular groove portion 52, does not close the P port 51, and the annular groove portion 52 is annularly provided on the inner peripheral surface of the sleeve 50. Therefore, it is not blocked by the guided portion 36. As a result, P port 51
The smooth supply of oil into the sleeve 50 is realized by only providing one.

Here, the provision of the annular groove portion 52 may reduce the contact area between the guided portion 36 and the support guide portion 53, but the support guide portion 53 causes the guided portion 3 to move.
There is no change in the overall width that guides and supports 6, and the spool 30
Does not cause any hindrance in moving. Rather, since the contact area is reduced, the frictional resistance generated between the guided portion 36 and the support guide portion 53 is reduced, and the responsiveness of the spool 30 is improved.

The fluid path control valve OC according to the second embodiment.
The function of 2 is basically the same as that of the fluid path control valve OC1 according to the first embodiment, so only the difference will be described. The oil reaching the P port 51 from the oil pump 13 via the oil pipe 14 is the P port 23 of 1
From the inside into the sleeve 50. And sleeve 5
0 to the annular groove 52 provided on the inner peripheral surface of the passage 3
The A port 21 and the B port 22 are reached via 1a, 31b, and 31c.

After that, the oil flow after reaching the B port 22 is the same as that described in the first embodiment, so the description thereof will be omitted. As described above in detail based on the respective embodiments, the fluid path control valves OC1 and OC according to the respective embodiments described above.
2 is the passages 31a, 31b, 31c of the spool 30.
In the embodiment, the guided portion 36 formed in the axial direction so as to have the same peripheral surface as the land 32 is provided, and the support guide portions 28, 53 corresponding to the guided portion 36 are provided in the sleeves 20, 50.

Therefore, unlike the conventional fluid path control valve OC3 in which the guided portions 76a independent of the passage 77 are provided at both ends of the land 76, the total length of the spool 30 can be shortened and the rigidity of the spool 30 can be reduced. Can be higher. As a result, the durability of the spool 30 can be improved, and the passages 31a, 31b, 3
It is possible to improve processing accuracy when forming the notch 1c.

Further, for example, in the conventional 4-port fluid path control valve, it was necessary to provide three passages partitioned by lands in the longitudinal direction thereof, whereas in the 4-port fluid path control valve according to the above embodiment. In the valves OC1 and OC2, the passage 31 including the passages 31a, 31b and 31c may be provided at one place, and the production efficiency thereof is improved.

Further, the total length of the sleeves 20 and 50 including the spool 30 can be shortened, and the rigidity and the cylindrical accuracy of the sleeves 20 and 50 can be improved. Therefore, when the spool 30 moves, it is difficult for the sleeves 20 and 50 to come into contact with the spool 30, and the movement of the spool 30 can be made smoother.

Furthermore, by shortening the overall lengths of the spool 30 and the sleeves 20 and 50, the fluid path control valves OC1 and OC2 can be miniaturized.
Therefore, there is no dimensional restriction when selecting the location where the fluid path control valves OC1 and OC2 are mounted, and the machining length of the mating housing can be shortened, and machining of the mating housing can be achieved. The process can be simplified.

Further, the fluid path control valve O according to each of the above embodiments
C1 and OC2 are provided with edges 37a, 37b and 37c that are formed in multiple stages at the boundary between the passages 31a, 31b and 31c and the land 32. Therefore, as compared with the fluid path control valve OC3 according to the conventional example, the opening area of each port (annular groove portion) can be changed with good responsiveness to the displacement of the spool stroke.

Further, by forming the edges 37a, 37b, 37c in multiple stages, it is possible to arbitrarily select the passage width influencing the hydraulic characteristics in one spool 30. As a result, it is possible to realize several types of hydraulic characteristics with one fluid path control valve OC1, and it is possible to control the hydraulic characteristics with respect to the spool stroke more accurately.

Next, the fluid path control valve OC according to the first embodiment.
The first sleeve 20 has four P ports 23 different from the number of guided portions 36 formed on the spool 30. Therefore, even if the spool 30 rotates, the guided portion 36 does not block all the four P ports 23, and the oil can be constantly supplied into the sleeve 20.

Further, the fluid passage control valve OC2 according to the second embodiment is provided with the annular groove portion 52 on the inner peripheral surface (support guide portion) of the sleeve 50 corresponding to the arrangement position of the P port 51. Therefore, the guided portion 36 of the spool 30
And the P port 51 do not come into direct contact with each other, and the oil can be stably supplied into the sleeve 50 by providing only one P port 51.

Further, since the annular groove portion 52 is formed, the contact area between the guided portion 36 and the support guide portion 53 becomes small, so that the frictional resistance generated between the two can be reduced. Therefore, the fluid path control valve OC2
The responsiveness of can be improved.

The present invention can be variously modified and improved without departing from the spirit thereof. For example, in each of the above-described embodiments, a part of the spool 30 is cut out perpendicularly to the axial direction, so that the passages 31a, 31b,
31c is obtained, but the passage has a cylindrical notch shape perpendicular to the axial direction of the spool 30 as shown in FIG.
You may form so that the guided part 36 may be provided.

In such a case, similar passages of oil can be realized in each of the passages 31a, 31b, 31c divided by the guided portion 36, and the hydraulic characteristics can be set to an arbitrary value by devising the cylindrical shape. It can be a property. In addition to this, in the spool according to the conventional example in which the passage is formed in a cylindrical shape having a smaller diameter than the land, the land and the land may be connected by the guided portion.

In each of the above embodiments, the fluid path control valve O
P port 23, 51, A port 2 as C1 and OC2
The four-port fluid path control valves OC1 and OC2 provided with four ports, namely, the B port 22, the B port 22, and the R port 24 have been described.
The present invention may be applied to a 5-port fluid path control valve or the like that includes five ports, that is, one B port 22, and two R ports 24. In such a case, the communication passage 34b formed in the spool 30 becomes unnecessary. It should be noted that the number of ports may appropriately correspond to the conditions to which the fluid path control valve is applied.

Further, in each of the above embodiments, the fluid path control valve OC, which is driven and controlled by the electromagnetic actuator 40, is used.
1, OC2 was used, but manual type, mechanical operation type, hydraulic type,
A drive control means such as a hydraulic electromagnetic type may be used. Which drive control means is to be used may be appropriately adapted depending on the condition to which the fluid path control valve is applied.

Furthermore, in each of the above embodiments, the edges 37a, 37b, 37c at the boundary between the passages 31a, 31b, 31c and the land 32 are formed in a three-step shape, but it is sufficient if they are multi-stepped. , But not limited to this. That is, the number of stages may be determined according to the number of hydraulic characteristics desired to be realized by the fluid path control valve.

Next, the fluid path control valve OC according to the first embodiment.
In the first embodiment, the sleeve 20 having four P ports 23 and the spool 30 having three guided portions 36 are used, but the number of P ports 23 and the number of guided portions 36 may be different, It is not limited to this. That is, all the P ports 23 need not be closed by the guided portion 36 when the spool 30 rotates in the sleeve 20.

The technical ideas other than the claims that can be understood from the above embodiments will be described below along with their effects. (1) In the fluid path control valve according to claim 1 or 2, the sleeve has a fluid supply means connection port for connecting a fluid supply means for supplying a fluid, and the fluid supply means connection port. Is different from the number of the guided parts.

With such a structure, even if the spool rotates when the spool moves in the sleeve, the guided portion formed in the communicating portion closes the fluid supply means connection port. This has the advantage that stable fluid direction control is always performed.

(2) In the fluid path control valve according to the first aspect, the edges formed at the boundary between the sealing portion and the communicating portion are formed stepwise so that the positions are different. A fluid path control valve characterized in that

In such a case, many hydraulic characteristics can be realized by one fluid passage control valve, and the fluid passage control valve can be controlled more accurately.

[0079]

As described above, the fluid path control valve according to the invention of claim 1 is slidably guided and supported by the support guide portion of the sleeve at the communicating portion of the spool that communicates between the predetermined ports. It has a guided part.

Therefore, it is not necessary to provide separate and independent guided portions at both ends of the sealing portion, and the spool can be made short and high in rigidity. Further, by shortening the spool, the fluid path control valve can be downsized, and its durability can be improved.

Further, the fluid path control valve according to the invention of claim 2 has a construction in which the communicating portion is formed at a substantially central position of the spool, and the guided portion is formed at a substantially central position of the spool.

Therefore, the center of gravity of the spool and the supporting position are close to each other, the balance of the spool with respect to the sleeve is easily maintained, and the movement of the spool can be made smoother.

Further, the fluid path control valve according to the invention of claim 3 is provided with an annular groove portion formed along the inner peripheral surface of the support guide portion. Therefore, without providing the fluid supply means connection port in the number different from the number of guided portions,
It is possible to realize a stable supply of fluid in the sleeve at all times.

[Brief description of drawings]

FIG. 1 is an overall configuration diagram of a hydraulic control system using a fluid path control valve to which the present invention is applied.

FIG. 2 is an overall perspective view of a spool used in the first embodiment.

FIG. 3 is a side sectional view of a spool used in the first embodiment.

FIG. 4 is a sectional view of the spool taken along the line AA in FIG.

FIG. 5 is a plan view of a spool used in the first embodiment.

FIG. 6 is a rear view of the spool used in the first embodiment.

FIG. 7 is a front view of a spool used in the first embodiment.

FIG. 8 is an enlarged sectional view showing an edge of a spool used in the first embodiment.

9 is a hydraulic characteristic diagram of the fluid path control valve including the spool having the edge shown in FIG.

FIG. 10 is an enlarged configuration diagram in which a spool and a sleeve used in the second embodiment are combined.

FIG. 11 is an overall perspective view of a spool used in another embodiment.

FIG. 12 is an overall configuration diagram of a fluid path control valve according to a conventional example.

FIG. 13 is an enlarged sectional view showing an edge of a spool used in a conventional example.

14 is a hydraulic characteristic diagram of an oil control valve including a spool having an edge shown in FIG.

[Explanation of symbols]

20 ... Sleeve, 21 ... A port, 22 ... B port, 2
3 ... P port, 24 ... R port, 28 ... support guide part,
30 ... Spool, 31a, 31b, 31c ... Passage (communication part), 32 ... Land (sealing part), 36 ... Guided part, 37a, 37b, 37c ... Edge, 40 ... Electromagnetic actuator, 42 ... Plunger, 50 … Sleeves, 5
1 ... P port

Claims (3)

[Claims] 1. A bottomed cylindrical sleeve having a plurality of ports and a support guide portion formed along an inner peripheral surface, and sealing a fluid flow between predetermined ports of the respective ports. A guided portion is formed in the axial direction that communicates between the sealing portion and a predetermined port among the ports and has the same peripheral surface as the sealing portion and is slidably guided by the support guide portion. And a cylindrical spool having a communicating portion that is connected to the fluid path control valve. 2. The fluid path control valve according to claim 1, wherein the communication portion is formed at a substantially central position of the spool, and the support guide portion is substantially central position of the sleeve corresponding to the communication portion. A fluid path control valve characterized by being formed in. 3. The fluid passage control valve according to claim 1, wherein the support guide portion has an annular groove portion formed along an inner peripheral surface thereof. Control valve.