JP2017036774A - Solenoid valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a degree of freedom in layout of a solenoid valve.SOLUTION: Solenoid valves 100 and 110 include a main valve 22 which varies a communication opening between a first port 220 and a second port 230, a control pressure chamber 42 which energizes the main valve 22 to a valve close direction, pressure compensation sleeves 26 and 126 slidably inserted into the main valve 22, rubber elastic bodies 28 and 128 interposed between the main valve 22 and the pressure compensation sleeves 26 and 126, an auxiliary valve 27 which varies openings of sleeve through holes 26c and 126b, and a solenoid part 60 which displaces the auxiliary valve 27 in accordance with a current to be supplied.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a solenoid valve.

  In general, a construction machine or an industrial machine that operates by hydraulic pressure uses a solenoid valve that controls the flow rate of hydraulic oil according to electromagnetic force.

  Patent Document 1 includes a main valve that changes the opening degree of communication between the first port and the second port, a control pressure chamber that is guided by hydraulic oil from the first port and biases the main valve in the valve closing direction, A solenoid valve is described that includes a solenoid section that controls the pressure in the control pressure chamber by communicating the control pressure chamber and the second port. The solenoid valve further includes a pressure compensation mechanism for making the drive current of the solenoid unit constant regardless of the pressure difference between the first port and the second port.

JP 2007-239996 A

  In the solenoid valve disclosed in Patent Document 1, a disc spring is used to displace the position of the sleeve constituting the pressure compensation mechanism with respect to the main valve. Since the shape and spring characteristics of the disc spring are standardized, the shape of the main valve and the sleeve must be designed in accordance with the shape of the disc spring that satisfies the required characteristics. For this reason, there exists a possibility that the freedom degree of design of a solenoid valve may fall.

  The present invention has been made in view of such a technical problem, and an object thereof is to improve the degree of freedom in designing a solenoid valve.

  According to a first aspect of the present invention, a rubber elastic body is interposed between the main valve and the pressure compensation sleeve to generate a restoring force by being compressed when the pressure compensation sleeve enters the main valve.

  The second invention is characterized in that a rubber elastic body formed in a cylindrical shape is interposed between the flange portion of the pressure compensation sleeve and the main valve.

  A third aspect of the invention is characterized in that a rubber elastic body formed in a columnar shape is interposed between the bottom surface of the accommodation hole of the main valve and the tip surface of the pressure compensation sleeve.

  In the first to third inventions, a rubber elastic body is used to displace the position of the pressure compensation sleeve relative to the main valve. Since the shape of the rubber elastic body is freely set, the main valve and the pressure compensation sleeve can be freely designed.

  According to a fourth aspect of the present invention, the rubber elastic body is formed by laminating a plurality of rubber materials having different elastic characteristics.

  In the fourth invention, the rubber elastic body is formed by combining a plurality of rubber materials having different elastic characteristics. For this reason, the elastic characteristic of a rubber elastic body can be set arbitrarily.

  ADVANTAGE OF THE INVENTION According to this invention, the freedom degree of design of a solenoid valve can be improved.

It is sectional drawing of the solenoid valve which concerns on 1st Embodiment of this invention. It is sectional drawing of the modification of the solenoid valve which concerns on 1st Embodiment of this invention. It is sectional drawing of the solenoid valve which concerns on 2nd Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

<First Embodiment>
A solenoid valve 100 according to a first embodiment of the present invention will be described with reference to FIG.

  A solenoid valve 100 shown in FIG. 1 is provided in a construction machine, an industrial machine, or the like. The solenoid valve 100 shown in FIG. Control the flow rate.

  The solenoid valve 100 is inserted and fixed in a non-through insertion hole 210 provided in the valve block 200. The valve block 200 has one end opened at the bottom of the insertion hole 210 and the other end opened at the outer surface of the valve block 200 and connected to a fluid pressure source through a pipe (not shown) and the other end. The second port 230 is open to the side surface of the hole 210, and the other end is open to the outer surface of the valve block 200 and is connected to the actuator through a pipe (not shown).

  In the solenoid valve 100, hydraulic oil is used as the working fluid. The hydraulic fluid flows from the first port 220 to the second port 230. The working fluid is not limited to working oil, and may be other incompressible fluid or compressible fluid.

  The solenoid valve 100 includes a main valve 22 that changes the opening degree of communication between the first port 220 and the second port 230, and a hollow cylindrical sleeve that is fixed in the insertion hole 210 and into which the main valve 22 is slidably inserted. 12, the hydraulic oil is guided from the first port 220, and the control pressure chamber 42 that urges the main valve 22 in the valve closing direction, and is slidably inserted into the main valve 22, and the control pressure chamber 42 and the second port 230 is separated from and seated on a pressure compensation sleeve 26 in which a sleeve through hole 26c is formed as a communication passage for communicating with 230 and a sub-sheet portion 26d formed in the pressure compensation sleeve 26, and the opening degree of the sleeve through hole 26c is changed. The auxiliary valve 27 and the solenoid part 60 which displaces the auxiliary valve 27 according to the supplied electric current are provided.

  The sleeve 12 includes a sliding support portion 12a that slidably supports the outer peripheral surface of the main valve 22, and a seat portion 13 on which the main valve 22 is seated.

  On the inner periphery of the sheet portion 13, two sheet portions, a circular hole-shaped first sheet portion 13 a and a truncated cone-shaped second sheet portion 13 b, are formed in this order from the first port 220 side. The central axis of the first sheet portion 13 a and the central axis of the second sheet portion 13 b coincide with the central axis of the sleeve 12.

  The sleeve 12 is formed with a plurality of communication holes 12b communicating with the space in the sleeve 12 and the second port 230 between the second sheet portion 13b and the sliding support portion 12a at intervals in the circumferential direction. .

  O-rings 51 and 52 are respectively arranged on the outer periphery of the seat portion 13 and the outer periphery of the sliding support portion 12a so as to sandwich the communication hole 12b. The connecting portion between the communication hole 12 b and the second port 230 is sealed by these two O-rings 51 and 52 that are compressed between the sleeve 12 and the insertion hole 210. In particular, the O-ring 51 provided on the outer periphery of the seat portion 13 prevents the first port 220 and the second port 230 from communicating with each other through the gap between the sleeve 12 and the insertion hole 210.

  The main valve 22 is a cylindrical member, and is disposed in the sleeve 12 such that one end surface 22e is located on the seat portion 13 side and the sliding portion 22c is slidably supported by the sliding support portion 12a.

  A cylindrical spool valve 22a that is slidably inserted into the first seat portion 13a is formed on the one end surface 22e side of the main valve 22, and a second spool valve 22a and a sliding portion 22c are provided between the second valve 22a and the sliding portion 22c. A truncated cone-shaped poppet valve 22b seated on the seat portion 13b is formed.

  A recess 22g communicating with the first port 220 is formed on one end surface 22e of the main valve 22 coaxially with the spool valve 22a. In the spool valve 22a, a plurality of through holes 22d having one end opened on a surface sliding with the first seat portion 13a and the other end opened on the inner peripheral surface of the recess 22g are formed at intervals in the circumferential direction.

  Each through hole 22d closed by the first seat portion 13a gradually opens as the spool valve 22a moves in a direction in which the poppet valve 22b and the second seat portion 13b are separated from each other. That is, the area of each through hole 22d exposed from the first seat portion 13a changes according to the amount of movement of the spool valve 22a. Thus, the flow rate of the hydraulic fluid flowing from the first port 220 to the second port 230 can be controlled by changing the opening area of each through hole 22d.

  Each through-hole 22d is disposed so as not to be completely blocked by the first sheet portion 13a even when the poppet valve 22b is in contact with the second sheet portion 13b. That is, the opening area of each through-hole 22d becomes the minimum value at the valve closing position where the poppet valve 22b contacts the second seat portion 13b, and gradually increases as the poppet valve 22b is displaced in the valve opening direction.

  In addition, each through-hole 22d may be arrange | positioned so that the poppet valve 22b may be obstruct | occluded by the 1st sheet | seat part 13a until it leaves | separates from the 2nd sheet | seat part 13b to some extent. In this case, the flow rate of the hydraulic oil can be set to almost zero until the main valve 22 is displaced to some extent.

  The other end surface 22 f of the main valve 22 faces a control pressure chamber 42 defined by the main valve 22, the sleeve 12, and the solenoid unit 60.

  The valve block 200 is formed with a pressure introduction passage 240 that connects the first port 220 and the control pressure chamber 42. The pressure introduction passage 240 communicates with the control pressure chamber 42 through an introduction hole 41 that is formed in the sleeve 12 and functions as an orifice. For this reason, the flow of hydraulic oil into the control pressure chamber 42 is restricted by the introduction hole 41. The pressure introduction passage 240 may be provided with a check valve that prevents the hydraulic oil in the control pressure chamber 42 from flowing back to the first port 220.

  In the control pressure chamber 42, the main return spring 24 is compressed between the main valve 22 and the solenoid unit 60.

  The urging force of the main return spring 24 acts in the direction in which the main valve 22 is closed. Further, the pressure of the first port 220 acts on the valve-opening pressure receiving surface A1 corresponding to the cross section of the second seat portion 13b of the main valve 22, and acts in the direction of opening the main valve 22. Further, the pressure in the control pressure chamber 42 acts on the valve closing pressure receiving surface A2 corresponding to the cross section of the sliding portion 22c, and acts in the direction in which the main valve 22 is closed. Therefore, in the main valve 22, the thrust due to the pressure of the first port 220 acting on the valve opening pressure receiving surface A1 is the thrust due to the pressure of the control pressure chamber 42 acting on the valve closing pressure receiving surface A2 and the biasing force of the main return spring 24. If it exceeds the resultant force, it will be displaced in the valve opening direction, and if it is less, it will be displaced in the valve closing direction.

  The main valve 22 further includes a first communication path 23 a and a second communication path 23 b that allow the control pressure chamber 42 and the second port 230 to communicate with each other.

  The first communication passage 23a as a sliding hole is a non-through hole formed in the main valve 22 such that its central axis coincides with the central axis of the main valve 22, and one end opens to the other end surface 22f. The second communication passage 23 b is formed in the radial direction of the main valve 22, one end communicates with the first communication passage 23 a, and the other end opens on the outer peripheral surface of the main valve 22. The other end of the second communication passage 23b is disposed so as to always communicate with the communication hole 12b within a range in which the main valve 22 is displaced in the axial direction.

  The pressure compensation sleeve 26 is slidably inserted into the first communication passage 23a, and is disposed so as to face the control pressure chamber 42. The flange portion 26b has a larger outer diameter than the sliding portion 26a. And a sleeve through hole 26c formed so as to penetrate in the axial direction from the flange portion 26b to the sliding portion 26a. A frustoconical sub-seat portion 26d, on which the sub-valve 27 is seated, is formed at the open end of the sleeve through hole 26c that opens to the flange portion 26b. Therefore, the first communication passage 23a and the control pressure chamber 42 communicate with each other through the sub seat portion 26d and the sleeve through hole 26c.

  A rubber elastic body 28 is interposed between the flange portion 26b and the other end surface 22f of the main valve 22. The rubber elastic body 28 is formed in a cylindrical shape or an annular shape having a through hole 28a through which the sliding portion 26a is inserted. When the pressure compensation sleeve 26 enters the main valve 22, the rubber elastic body 28 is compressed and deformed to generate a restoring force. When the pressure compensation sleeve 26 retreats from the main valve 22, the rubber elastic body 28 returns to the original shape by the restoring force. The rubber elastic body 28 is formed of an elastomer having elasticity such as nitrile rubber or fluorine rubber excellent in oil resistance, or silicone rubber excellent in compression restoring force.

  The sub valve 27 is a columnar member, and a sub poppet valve 27a having a shape in contact with the sub seat portion 26d is formed at one end. The other end of the auxiliary valve 27 is coupled to a plunger 33 described later.

  When the sub poppet valve 27a and the sub seat portion 26d come into contact with each other, the communication between the control pressure chamber 42 and the first communication passage 23a is cut off. On the other hand, when the sub poppet valve 27a is separated from the sub seat portion 26d and a gap is formed between the sub poppet valve 27a and the sub seat portion 26d, the control pressure chamber 42 and the first communication passage 23a are communicated, and the control pressure chamber The hydraulic oil in 42 flows out to the second port 230 through the first communication path 23a and the second communication path 23b. The hydraulic oil is guided to the control pressure chamber 42 through the pressure introduction passage 240. However, since the introduction of the hydraulic oil into the control pressure chamber 42 is restricted by the introduction hole 41, the pressure in the control pressure chamber 42 is consequently reduced. descend.

  The size of the gap between the sub poppet valve 27a and the sub seat portion 26d is adjusted by changing the position of the sub valve 27 in the axial direction. Since the position of the auxiliary valve 27 in the axial direction is controlled by the solenoid unit 60, the size of the gap is controlled by the solenoid unit 60.

  The solenoid unit 60 includes a coil 62 that generates a magnetic attractive force when supplied with an electric current, and a bottomed cylindrical solenoid tube 14 that is provided on the outer periphery.

  The solenoid tube 14 has an insertion portion 14a that is inserted into the insertion hole 210 of the valve block 200, and a small-diameter portion 14b that is smaller in outer diameter than the insertion portion 14a and disposed outside the insertion hole 210. The solenoid tube 14 is screwed with the sleeve 12 at the insertion portion 14a. The connection between the solenoid tube 14 and the sleeve 12 is not limited to the screw connection, and may be a fitting connection.

  An O-ring 53 as a seal member is disposed on the outer periphery of the insertion portion 14a. The communication between the inside of the insertion hole 210 and the outside is blocked by the O-ring 53 compressed between the solenoid tube 14 and the insertion hole 210. For this reason, the hydraulic oil in the insertion hole 210 is prevented from leaking to the outside, and water, dust and the like are prevented from entering the insertion hole 210 from the outside.

  The fastening member 16 is fitted with play on the outer periphery of the small diameter portion 14b. The fastening member 16 is fastened to the valve block 200 via a bolt (not shown) in a state where the inner peripheral side portion is locked to the insertion portion 14a. When the fastening member 16 is fastened to the valve block 200, the solenoid valve 100 is fixed to the valve block 200.

  In the solenoid tube 14, the sub-valve 27 is fixed to the shaft center, and the cylindrical plunger 33 that is attracted by the magnetic attractive force generated by the coil 62, the columnar retainer 34 that is movable in the axial direction, and the plunger 33. And a sub return spring 35 interposed between the retainer 34 and the retainer 34 by compression. The plunger 33 is urged by the sub return spring 35 in the direction in which the sub poppet valve 27a formed at the tip of the sub valve 27 is seated on the sub seat portion 26d.

  A plurality of through holes 33a penetrating in the axial direction are formed in the plunger 33, and the spring chamber 44 in which the sub return spring 35 is disposed communicates with the control pressure chamber 42 through the through hole 33a. Therefore, the pressure in the spring chamber 44 is equivalent to the pressure in the control pressure chamber 42, and the urging force of the sub return spring 35 and the pressure in the spring chamber 44 press the sub poppet valve 27a against the sub seat portion 26d. Acts in the direction.

  An adjustment screw 36 is threaded through the end portion 14d of the solenoid tube 14 in the axial direction. One end of the adjusting screw 36 is in contact with the retainer 34 in the spring chamber 44. When the adjusting screw 36 is rotated, the position of the retainer 34 in the axial direction is changed, and the biasing force of the sub return spring 35 is changed. Thus, by rotating the adjustment screw 36, the initial load of the sub return spring 35 acting on the plunger 33 can be changed. The other end of the adjustment screw 36 protruding from the solenoid tube 14 is covered with a cover 63 attached to the solenoid tube 14.

  Next, the operation of the solenoid valve 100 will be described.

  When no current is supplied to the coil 62, the plunger 33 is pressed by the biasing force of the sub return spring 35, the sub poppet valve 27a of the sub valve 27 is seated on the sub seat portion 26d, and the control pressure chamber 42 is closed. It becomes a state. For this reason, the hydraulic oil in the first port 220 is guided into the control pressure chamber 42 through the pressure introduction passage 240 and the introduction hole 41, and the pressure in the control pressure chamber 42 becomes equal to the pressure in the first port 220. That is, a pressure equivalent to the pressure of the first port 220 acts on the valve closing pressure receiving surface A2.

  Here, the area of the valve closing pressure receiving surface A2 on which the pressure in the control pressure chamber 42 acts is larger than the area of the valve opening pressure receiving surface A1 on which the pressure of the first port 220 acts. Therefore, the resultant force of the pressure in the control pressure chamber 42 acting on the valve closing pressure receiving surface A2 and the biasing force of the main return spring 24 exceeds the thrust due to the pressure of the first port 220 acting on the valve opening pressure receiving surface A1. The main valve 22 is urged in a direction to close the seat portion 13. Thus, when the coil 62 is in a non-energized state, the flow of hydraulic oil from the first port 220 to the second port 230 is interrupted.

  On the other hand, when a current is supplied to the coil 62, the plunger 33 overcomes the urging force of the sub return spring 35 by the thrust generated by the solenoid unit 60 and is attracted to the coil 62 side. When the sub valve 27 is displaced together with the plunger 33, the sub poppet valve 27a is separated from the sub seat portion 26d, and a gap is formed between the sub poppet valve 27a and the sub seat portion 26d. The hydraulic oil in the control pressure chamber 42 passes through the gap, passes through the sleeve through hole 26c, the first communication path 23a, the second communication path 23b, and the communication hole 12b, and is discharged to the second port 230.

  Since the flow of hydraulic oil from the first port 220 into the control pressure chamber 42 is restricted by the introduction hole 41 that functions as an orifice, the pressure in the control pressure chamber 42 is controlled between the control pressure chamber 42 and the second port 230. Reduced by communication. And the resultant force of the thrust in the control pressure chamber 42 acting on the valve closing pressure receiving surface A2 and the urging force of the main return spring 24, the thrust due to the pressure of the first port 220 acting on the valve opening pressure receiving surface A1, The main valve 22 is displaced in a direction to open the seat portion 13 until the two are balanced. As a result, the hydraulic fluid flows from the first port 220 to the second port 230 between the through hole 22d and the first seat portion 13a, between the poppet valve 22b and the second seat portion 13b, and through the communication hole 12b. .

  When the current supplied to the coil 62 is increased, the sub poppet valve 27a further moves away from the sub seat portion 26d. As a result, the amount of hydraulic oil discharged from the control pressure chamber 42 to the second port 230 increases, and the pressure in the control pressure chamber 42 further decreases. As the pressure in the control pressure chamber 42 decreases, the main valve 22 further moves in a direction to open the seat portion 13, and the area where the through hole 22d of the spool valve 22a is exposed from the first seat portion 13a is increased. growing. As a result, the flow rate of the hydraulic oil flowing from the first port 220 to the second port 230 increases.

  In this way, the flow rate of the hydraulic oil flowing from the first port 220 to the second port 230 is controlled by increasing or decreasing the current supplied to the coil 62 and controlling the displacement amount of the main valve 22.

  When the energization of the coil 62 is stopped, the thrust force that attracts the plunger 33 disappears, and the plunger 33 is pressed in the direction in which the sub poppet valve 27a is seated on the sub seat portion 26d by the urging force of the sub return spring 35. The When the sub poppet valve 27a of the sub valve 27 is seated on the sub seat portion 26d, the hydraulic oil in the first port 220 is introduced into the control pressure chamber 42 through the introduction hole 41, and the pressure in the control pressure chamber 42 is It rises until it becomes equal to the pressure of 1 port 220.

  When the pressure in the control pressure chamber 42 becomes equal to the pressure of the first port 220, as described above, the thrust by the pressure of the first port 220 acting on the valve opening pressure receiving surface A1 acts on the valve closing pressure receiving surface A2. This is less than the resultant force of the thrust generated by the pressure in the control pressure chamber 42 and the urging force of the main return spring 24. For this reason, the main valve 22 is urged in a direction to close the seat portion 13, and as a result, the main valve 22 is displaced in a direction to close the seat portion 13, and the first port 220 moves to the second port 230. The flow of hydraulic oil is cut off.

  Next, the pressure compensation action by the pressure compensation sleeve 26 will be described.

  The pressure of the first port 220 acts on the auxiliary valve 27 through the spring chamber 44, and the pressure of the second port 230 acts through the sleeve through hole 26c. Therefore, in order to separate the sub valve 27 from the sub seat portion 26d, the pressure difference between the pressure of the first port 220 and the pressure of the second port 230 is a force that urges the sub valve 27 in the valve closing direction. The coil 62 must generate a magnetic attractive force that overcomes the resultant force of the sub return spring 35 and the force that biases the sub valve 27 in the valve closing direction. That is, the greater the pressure difference between the pressure at the first port 220 and the pressure at the second port 230, the greater the current supplied to the coil 62 in order to drive the subvalve 27. As described above, since the current for driving the auxiliary valve 27 is changed by the pressure difference between the pressure of the first port 220 and the pressure of the second port 230, the current supplied to the coil 62 from the first port 220 is changed. The flow rate of the hydraulic oil flowing to the second port 230 becomes unstable.

  Therefore, by changing the position of the pressure compensation sleeve 26 having the sub seat portion 26d on which the sub valve 27 is seated according to the pressure difference between the pressure of the first port 220 and the pressure of the second port 230, the sub valve 27 Pressure compensation is performed to keep the current required for opening the valve constant.

  Specifically, the pressure of the first port 220 acts on the side of the flange portion 26b of the pressure compensation sleeve 26 through the control pressure chamber 42, and the second port 230 on the side of the sliding portion 26a passes through the first communication path 23a. The pressure of acts. Here, since the rubber elastic body 28 is interposed between the flange portion 26b and the other end surface 22f of the main valve 22, the pressure difference between the pressure of the first port 220 and the pressure of the second port 230 is reduced. When it becomes larger, the rubber elastic body 28 is compressed in the axial direction of the pressure compensation sleeve 26, and the position of the sub seat portion 26 d is displaced closer to the main valve 22.

  At this time, the sub valve 27 urged in the valve closing direction by the sub return spring 35 is displaced following the displacement of the sub seat portion 26d. Since the sub return spring 35 expands by the amount the seating position of the sub valve 27 is displaced closer to the main valve 22, as a result, the urging force of the sub return spring 35 acting in the direction to close the sub valve 27 decreases.

  Thus, even if the pressure difference between the pressure of the first port 220 and the pressure of the second port 230 is increased by providing the pressure compensation sleeve 26, the urging force of the sub return spring 35 is reduced by that amount. As a result, an increase in the magnetic attractive force required to displace the sub valve 27 is suppressed. As a result, the amount of displacement of the sub valve 27 with respect to the current supplied to the coil 62 is stabilized, so that the flow rate of the hydraulic oil flowing from the first port 220 to the second port 230 can be accurately controlled.

  The displacement amount of the pressure compensation sleeve 26 can be changed by a disc spring. However, since the disc spring has a standardized shape and spring characteristics, the disc spring has a disc spring shape that satisfies the required characteristics. The shapes of the main valve 22 and the pressure compensation sleeve 26 must be designed. Further, when the outer diameter of the disc spring satisfying the required characteristics is increased, the outer diameter of the solenoid valve 100 must be increased.

  On the other hand, in the first embodiment, the displacement amount of the pressure compensation sleeve 26 is determined by the elastic characteristics of the rubber elastic body 28. The rubber elastic body 28 formed of a rubber material can be freely set in shape as compared with a disc spring, and the elastic characteristics can be arbitrarily changed by changing the material. For this reason, since the main valve 22 and the pressure compensation sleeve 26 can be designed freely, the degree of freedom in designing the solenoid valve 100 can be improved. Furthermore, it can suppress that the outer diameter of the solenoid valve 100 becomes large.

  According to the above 1st Embodiment, there exists an effect shown below.

  In the solenoid valve 100, a rubber elastic body 28 is used to displace the position of the pressure compensation sleeve 26 with respect to the main valve 22. Since the shape of the rubber elastic body 28 is freely set, the main valve 22 and the pressure compensation sleeve 26 can be freely designed, and the degree of freedom in designing the solenoid valve 100 can be improved.

  Hereinafter, a modification of the solenoid valve 100 according to the first embodiment will be described with reference to FIG. FIG. 2 is a cross-sectional view corresponding to FIG. 1 of the first embodiment.

  In the first embodiment, one rubber elastic body 28 for displacing the position of the pressure compensation sleeve 26 with respect to the main valve 22 is interposed between the flange portion 26 b and the other end surface 22 f of the main valve 22. The Instead, a plurality of rubber elastic bodies 29a and 29b may be provided between the flange portion 26b and the other end surface 22f of the main valve 22.

  In the modification, as shown in FIG. 2, the first rubber elastic body 29 a and the second rubber elastic body 29 b are stacked and arranged side by side in the axial direction of the pressure compensation sleeve 26. The first rubber elastic body 29a and the second rubber elastic body 29b have different elastic characteristics.

  Therefore, for example, by preparing a plurality of rubber elastic bodies having different elastic characteristics and combining two rubber elastic bodies from among them, the elastic characteristics of the entire rubber elastic body can be changed. As a result, the displacement amount of the pressure compensation sleeve 26 with respect to the pressure difference between the pressure of the first port 220 and the pressure of the second port 230 can be arbitrarily set.

  Thus, in the modified example, as in the first embodiment, the rubber elastic bodies 29a and 29b are used to displace the position of the pressure compensation sleeve 26 with respect to the main valve 22. Similar effects can be obtained. Furthermore, the elastic characteristics of the rubber elastic bodies 29a and 29b can be arbitrarily set.

  The first rubber elastic body 29a and the second rubber elastic body 29b may be integrally formed. Moreover, it is good also as a structure which laminated | stacked the 3 or more rubber elastic body which has a different elastic characteristic. Further, the elastic characteristics may be changed by changing the material inside the rubber elastic body or providing a space inside.

Second Embodiment
Next, a solenoid valve 110 according to a second embodiment of the present invention will be described with reference to FIG. Below, it demonstrates centering on a different point from 1st Embodiment, the same code | symbol is attached | subjected to the structure similar to 1st Embodiment, and description is abbreviate | omitted.

  The basic configuration of the solenoid valve 110 is the same as that of the solenoid valve 100 according to the first embodiment. The solenoid valve 110 is different from the solenoid valve 100 in that a rubber elastic body 128 for displacing the position of the pressure compensation sleeve 126 with respect to the main valve 22 is provided inside the main valve 22.

  The main valve 22 of the solenoid valve 110 has a non-penetrating accommodation hole 22h whose one end opens on the other end surface 22f, a support member 122 having an insertion hole 122a that is fixed to the accommodation hole 22h and through which the pressure compensation sleeve 126 is inserted, and one end. Has a communication passage 123b that opens to the inner peripheral surface of the housing hole 22h and the other end opens to the outer peripheral surface of the main valve 22. The other end of the communication path 123b is arranged so as to always communicate with the communication hole 12b within a range in which the main valve 22 is displaced in the axial direction. A rubber elastic body 128 is accommodated in the accommodating space 22i defined inside the main valve 22 by the accommodating hole 22h and the support member 122.

  The pressure compensation sleeve 126 has a sliding portion 126a that is slidably inserted into the insertion hole 122a, a sleeve through hole 126b that is formed to penetrate in the axial direction, and one end connected to the sleeve through hole 126b. It has a sleeve communication hole 126c formed so as to penetrate in the radial direction, and a sub-sheet portion 126d formed at the open end of the sleeve through-hole 126b facing the control pressure chamber 42. The sleeve communication hole 126c is disposed so as to always open to the accommodation space 22i within a range in which the pressure compensation sleeve 126 is displaced in the axial direction.

  Therefore, when the sub poppet valve 27a is separated from the sub seat portion 126d and a gap is formed between the sub poppet valve 27a and the sub seat portion 126d, the hydraulic oil in the control pressure chamber 42 penetrates the sleeve through the gap. It passes through the hole 126b, the sleeve communication hole 126c, the accommodating space 22i, the communication path 123b, and the communication hole 12b and is discharged to the second port 230.

  The pressure compensation sleeve 126 further includes a flange portion 125 that is press-fitted into the sliding portion 126a in the accommodation space 22i and closes the opening end of the sleeve through hole 126b that opens to the distal end surface 126e of the pressure compensation sleeve 126.

  The flange portion 125 is formed to have an outer diameter larger than that of the sliding portion 126a, and a rubber elastic body 128 is interposed between the flange portion 125 and the bottom surface of the accommodation hole 22h. The flange portion 125 is formed with a convex portion 125a that protrudes toward the rubber elastic body 128, and the rubber elastic body 128 is formed with a concave portion 128a into which the convex portion 125a is inserted. By inserting the convex portion 125a of the flange portion 125 into the concave portion 128a of the rubber elastic body 128, the rubber elastic body 128 is restricted from moving in the radial direction.

  The flange 125 is formed as a member separate from the pressure compensation sleeve 126. Instead, the flange portion 125 and the pressure compensation sleeve 126 may be integrally formed. Moreover, the coupling | bonding of the collar part 125 and the pressure compensation sleeve 126 is not limited to press fitting, A screw coupling and a bolt coupling | bonding may be sufficient.

  The rubber elastic body 128 is formed in a columnar shape or a disk shape so as to be easily sandwiched between the flange portion 125 and the bottom surface of the accommodation hole 22h.

  Regarding the operation of the solenoid valve 110, when the main valve 22 is opened, the hydraulic oil in the control pressure chamber 42 passes through the sleeve through hole 126b, the sleeve communication hole 126c, the accommodation space 22i, the communication path 123b, and the communication hole 12b. The operation is the same as that of the solenoid valve 100 of the first embodiment except that it is discharged to the port 230. Therefore, the description thereof is omitted.

  Next, the pressure compensation action by the pressure compensation sleeve 126 will be described.

  The pressure of the first port 220 acts on the end face of the pressure compensation sleeve 126 facing the control pressure chamber 42, and the end face of the pressure compensation sleeve 126 facing the accommodation space 22 i and the sleeve through hole 126 b The pressure of the second port 230 acts through the communication path 123b.

  Here, since the rubber elastic body 128 is interposed between the front end surface 126e of the pressure compensation sleeve 126 facing the accommodation space 22i and the bottom surface of the accommodation hole 22h, the pressure of the first port 220 and the second port 220 When the pressure difference from the pressure 230 increases, the rubber elastic body 128 is compressed in the axial direction of the pressure compensation sleeve 26, and the position of the sub seat 126d is displaced toward the main valve 22.

  At this time, the sub valve 27 urged in the valve closing direction by the sub return spring 35 is displaced following the displacement of the sub seat portion 126d. Since the sub return spring 35 expands by the amount the seating position of the sub valve 27 is displaced closer to the main valve 22, as a result, the urging force of the sub return spring 35 acting in the direction to close the sub valve 27 decreases.

  Thus, even if the pressure difference between the pressure of the first port 220 and the pressure of the second port 230 is increased by providing the pressure compensation sleeve 126, the urging force of the sub return spring 35 is reduced by that amount. As a result, an increase in the magnetic attractive force required to displace the sub valve 27 is suppressed. As a result, the amount of displacement of the sub valve 27 with respect to the current supplied to the coil 62 is stabilized, so that the flow rate of the hydraulic oil flowing from the first port 220 to the second port 230 can be accurately controlled.

  According to the above 2nd Embodiment, there exists an effect shown below.

  In the solenoid valve 110, a rubber elastic body 128 is used to displace the position of the pressure compensation sleeve 126 with respect to the main valve 22. Since the shape of the rubber elastic body 128 is freely set, the main valve 22 and the pressure compensation sleeve 126 can be freely designed, and the degree of freedom in designing the solenoid valve 110 can be improved.

  As in the modification of the first embodiment, the rubber elastic body 128 may be formed by stacking a plurality of rubber elastic bodies having different elastic characteristics.

  Hereinafter, the configuration, operation, and effect of the embodiment of the present invention will be described together.

  Solenoid valves 100 and 110 that control the flow rate of hydraulic fluid flowing from the first port 220 to the second port 230 include a main valve 22 that changes the communication opening degree between the first port 220 and the second port 230, and the first port. A hydraulic pressure is guided from 220 and a control pressure chamber 42 that urges the main valve 22 in the valve closing direction, and a sleeve that is slidably inserted into the main valve 22 and communicates the control pressure chamber 42 and the second port 230. The pressure compensation sleeves 26 and 126 in which the through holes 26 c and 126 b are formed are interposed between the main valve 22 and the pressure compensation sleeves 26 and 126, and the pressure compensation sleeves 26 and 126 enter the main valve 22. Sub-valves that are separated from and seated on the pressure compensating sleeves 26 and 126 in order to change the degree of opening of the rubber elastic bodies 28 and 128 that generate a restoring force and are compressed by the sleeve through holes 26c and 126b. 7, a solenoid 60 for displacing the auxiliary valve 27 in response to the current supplied, characterized in that it comprises a.

  The pressure compensation sleeve 26 has a sliding portion 26a slidably inserted into a first communication passage 23a provided in the main valve 22, and an outer diameter arranged outside the main valve 22 than the sliding portion 26a. The rubber elastic body 28 is formed in a cylindrical shape having a through hole 28a through which the sliding portion 26a is inserted, and is interposed between the flange portion 26b and the main valve 22. It is characterized by.

  The main valve 22 has a housing hole 22h in which the rubber elastic body 128 is housed, the pressure compensation sleeve 126 has a tip surface 126e that faces the housing hole 22h, and the rubber elastic body 128 has a cylindrical shape. It is formed and is interposed between the bottom surface of the accommodation hole 22h and the front end surface 126e.

  In these configurations, rubber elastic bodies 28 and 128 are used to displace the pressure compensating sleeves 26 and 126 with respect to the main valve 22. Since the rubber elastic bodies 28 and 128 are freely configured, the main valve 22 and the pressure compensation sleeves 26 and 126 can be freely designed, and the degree of freedom in designing the solenoid valves 100 and 110 is improved. Can be made.

  The displacement amount of the pressure compensation sleeves 26 and 126 can also be changed by a disc spring. However, since the disc spring has a standardized shape and spring characteristics, the disc spring has an outside of the disc spring that satisfies the required characteristics. As the diameter increases, the outer diameter of the solenoid valve 100 must also be increased. On the other hand, when the rubber elastic bodies 28 and 128 are used, the shape can be freely set and the elastic characteristics can be arbitrarily changed by changing the material. For this reason, it can suppress that the outer diameter of the solenoid valve 100 becomes large.

  The rubber elastic bodies 28 and 128 are formed by laminating a plurality of rubber materials having different elastic characteristics.

  In this configuration, the rubber elastic bodies 28 and 128 are formed by combining a plurality of rubber materials having different elastic characteristics. For this reason, the elastic characteristics of the rubber elastic bodies 28 and 128 can be set arbitrarily.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  For example, in the above embodiment, the solenoid valves 100 and 110 control the flow of hydraulic oil from the first port 220 to the second port 230, but the present invention is not limited to this, and the first port 220 to the first port 230 A bidirectional flow control valve that can also control the flow of hydraulic oil to the port 220 may be used.

100, 110 ... solenoid valve, 22 ... main valve, 22h ... receiving hole, 26, 126 ... pressure compensation sleeve, 26a ... sliding part, 26b ... collar part, 26c, 126b ... Sleeve through hole (communication path), 26d, 126d ... Sub-seat part, 27 ... Sub valve, 28, 128 ... Rubber elastic body, 28a ... Through hole, 29a ... 1st rubber elastic body (rubber elastic body), 29b ... 2nd rubber elastic body (rubber elastic body), 35 ... sub return spring, 42 ... control pressure chamber, 60 ... solenoid part, 126e ... Front end surface, 200 ... Valve block, 220 ... First port, 230 ... Second port

Claims (4)

A solenoid valve for controlling a flow rate of the working fluid flowing from the first port to the second port,
A main valve that changes a communication opening degree between the first port and the second port;
A control pressure chamber in which a working fluid is guided from the first port and biases the main valve in a valve closing direction;
A pressure compensation sleeve that is slidably inserted into the main valve and has a communication passage that communicates the control pressure chamber and the second port;
A rubber elastic body interposed between the main valve and the pressure compensation sleeve, and generating a restoring force by being compressed when the pressure compensation sleeve enters the main valve;
A sub-valve that is separated from and seated on the pressure compensation sleeve to change the opening of the communication path;
A solenoid unit that displaces the sub-valve according to the supplied current;
A solenoid valve comprising: The pressure compensation sleeve includes a sliding portion that is slidably inserted into a sliding hole provided in the main valve, a flange portion that is disposed outside the main valve and has an outer diameter larger than the sliding portion, Have
The solenoid according to claim 1, wherein the rubber elastic body is formed in a cylindrical shape having a through-hole through which the sliding portion is inserted, and is interposed between the flange portion and the main valve. valve. The main valve has an accommodation hole in which the rubber elastic body is accommodated,
The pressure compensating sleeve has a tip surface facing the receiving hole;
The solenoid valve according to claim 1, wherein the rubber elastic body is formed in a columnar shape and is interposed between a bottom surface of the accommodation hole and the tip end surface.   4. The solenoid valve according to claim 1, wherein the rubber elastic body is formed by laminating a plurality of rubber materials having different elastic characteristics. 5.

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