Valve

Abstract

Provided is a valve in which a valve body operates smoothly. A valve (1) is provided with: a housing (2); a valve body (3) that is disposed so as to be movable in the axial direction within the housing (2) and that has a throttle port (34a), the valve body (3) dividing a primary chamber (S1) and a secondary chamber (S2) of the housing (2); and a biasing means (4) that biases the valve body (3) in the axial direction toward the primary chamber (S1) side, the valve body (3) being operated in the axial direction in accordance with the pressure difference between the primary chamber (S1) and the secondary chamber (S2), the biasing means (4) being disposed closer to the primary chamber (S1) side or the secondary chamber (S2) side than the throttle port (34a).

Description

Technical Field

[0001] The present invention relates to a valve, for example, to a valve for controlling the flow rate of a fluid flowing between a primary chamber and a secondary chamber. Background Art

[0002] A valve used to control a working fluid in various industrial fields has a valve seat and a valve body that can contact and separate from the valve seat, and can control the pressure and flow rate of the working fluid by adjusting the valve opening. As such a valve, a slide valve is known in which a valve core moves parallel to an opening serving as a valve seat.

[0003] The slide valve of Patent Document 1 has a valve body, a cylindrical valve core, a check spring, and a pressure compensation spring. The cylindrical valve core is configured to be movable in the axial direction in the valve body. In addition, the cylindrical valve core has a partition wall, which divides the check spring chamber and the pressure compensation spring chamber on both sides of the axial direction. The check spring is arranged in the check spring chamber, and the pressure compensation spring is arranged in the pressure compensation spring chamber, and the cylindrical valve core is balanced in the neutral position.

[0004] The valve body is provided with: a first flow path extending from the first port and connecting the inspection spring chamber with the flow setting throttle valve; a second flow path connecting the pressure compensation spring chamber with the second port; and a third flow path connecting the throttle valve with the pressure compensation spring chamber. The cylindrical valve core is provided with an inlet and outlet hole corresponding to the third flow path and a throttle hole corresponding to the second flow path.

[0005] When the fluid flows into the first flow path from the first port, the fluid flows out to the second port via the throttle valve, the third flow path, the inlet and outlet holes, the pressure compensation spring chamber, the throttle hole, and the second flow path. At this time, the cylindrical valve core moves in the axial direction according to the pressure difference between the inspection spring chamber and the pressure compensation spring chamber to adjust the opening of the throttle hole. Thus, even if the pressure difference between the inspection spring chamber and the pressure compensation spring chamber changes, the flow rate to the second port can be kept constant.

[0006] On the other hand, when the fluid flows into the second flow path from the second port, the cylindrical valve core moves toward the inspection spring chamber side, and the inlet and outlet holes are directly connected to the inspection spring chamber. As a result, the fluid flows out to the first port via the second flow path, the throttle hole, the pressure compensation spring chamber, the inlet and outlet holes, and the inspection spring chamber. At this time, the inlet and outlet holes are connected to the inspection spring chamber in a fully open state, so the flow rate toward the first port is not restricted.

[0007] Prior art literature

[0008] Patent Literature

[0009] Patent Document 1: Microfilm of Japanese Utility Model Application No. 62-25137 (Japanese Utility Model Application No. 4-7415) (page 2, figure 1) Summary of the invention

[0010] Problems to be solved by the invention

[0011] However, with respect to a sliding valve such as Patent Document 1, the pressure compensating spring is configured to cross the inlet and outlet holes and the throttle hole provided radially through the cylindrical valve core. Therefore, there is a concern that the flow of the fluid entering and exiting the inlet and outlet holes and the throttle hole may be obstructed by the pressure compensating spring, and there is a concern that the pressure compensating spring may be deformed in the bending direction due to the flow of the fluid.

[0012] The present invention has been made in view of such a problem, and an object of the present invention is to provide a valve in which a valve element operates smoothly.

[0013] Means for solving problems

[0014] In order to solve the above-mentioned problems, the valve of the present invention comprises: a housing; a valve core, which is configured to be able to move axially in the housing and has a throttling port, the valve core divides the housing into a primary chamber and a secondary chamber; and a force-applying unit, which applies force to the valve core axially toward the primary chamber side, the valve core moves axially according to the pressure difference between the primary chamber and the secondary chamber, wherein the force-applying unit is configured at a position closer to the primary chamber side or the secondary chamber side than the throttling port.

[0015] Thus, the flow of the fluid flowing out of the throttle port of the valve core can be prevented from being blocked by the force applying unit. Furthermore, the force applying unit can be prevented from being deformed in the radial direction due to the fluid flowing out of the throttle port of the valve core. Therefore, the force applying unit does not need to be selected according to the requirements of the fluid, and can be freely designed.

[0016] The valve body may be formed with a step portion against which an end portion of the urging means abuts.

[0017] Thus, a part of the urging means can be arranged to overlap the valve body in the axial direction, so that the flow of the fluid flowing out of the throttle port can be reliably prevented from being blocked by the urging means, and the axial dimension of the valve can be shortened.

[0018] The step portion may be provided on an inner peripheral surface of the valve body.

[0019] Thus, since the biasing means can be arranged inside the valve body, the outer peripheral surface of the valve body guided by the inner peripheral surface of the housing can be ensured to be large.

[0020] The valve body may be further provided with an opening / closing port for switching a communication state between the primary chamber and the secondary chamber, and the urging unit may be arranged closer to the secondary chamber than the opening / closing port.

[0021] This can prevent the fluid flowing through the opening and closing port from interfering with the urging means. The flow rate adjustment mechanism and the opening and closing mechanism can be integrally and compactly constructed using one valve element.

[0022] The valve body may be provided with a primary chamber side biasing unit for biasing the valve body toward the secondary chamber side in the axial direction, and the throttle port and the primary chamber may be communicated with each other via a flow path bypassing the primary chamber side biasing member.

[0023] This can avoid interference between the fluid flowing between the throttle port and the primary chamber and the primary chamber-side biasing means. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a longitudinal sectional view showing a valve according to Embodiment 1 of the present invention.

[0025] Figure 2 This is a diagram showing a valve using hydraulic notation.

[0026] Figure 3 It is a longitudinal sectional view showing the state of the valve in the process of controlling the flow rate.

[0027] Figure 4 2 is an enlarged schematic diagram showing the displacement X.

[0028] Figure 5 It is a graph showing the relationship between the front and rear pressure difference and the flow rate.

[0029] Figure 6 It is a longitudinal sectional view showing the state of the valve in free flow flow.

[0030] Figure 7 It is a longitudinal sectional view showing a valve according to a second embodiment of the present invention. DETAILED DESCRIPTION

[0031] Hereinafter, the mode for implementing the valve of the present invention will be described based on the embodiment. In addition, the embodiment will be described by taking the flow control valve as an example.

[0032] Example 1

[0033] Reference Figures 1 to 6 , the flow control valve of Example 1 is described. Figure 1 The left side of the paper is used as the left side of the flow control valve. Figure 1The right side of the paper is described as the right side of the flow control valve. In addition, the left side of the flow control valve is described as the primary chamber side, and the right side of the flow control valve is described as the secondary chamber side.

[0034] like Figure 1 As shown, the flow control valve 1 is a spool type flow control valve, and is assembled in a hydraulic circuit. In addition, the flow control valve 1 is mounted in a mounting hole of a valve housing on the device side and used.

[0035] The flow control valve 1 mainly includes a housing 2 , a flow control valve element 3 (hereinafter simply referred to as valve element 3 ), a flow control spring 4 as a biasing member, a check spring 5 as a primary chamber side biasing member, and a plunger 6 .

[0036] The housing 2 is composed of a first tubular member 21 and a second tubular member 22 .

[0037] The first tubular member 21 has a through hole 21a extending in the axial direction, and an annular convex portion 21b protruding in an annular shape toward the inner diameter side is formed in the substantially central portion in the axial direction. That is, a concave portion 21c opening on the left side is provided at a position closer to the left side than the annular convex portion 21b of the first tubular member 21, and a concave portion 21d opening on the right side is provided at a position closer to the right side than the annular convex portion 21b.

[0038] The second tubular member 22 is connected to the left side of the first tubular member 21 in a sealed manner by screwing, and the plunger 6 is connected to the right side of the first tubular member 21 in a sealed manner by screwing.

[0039] The second tubular member 22 includes a small diameter portion 22a, a large diameter portion 22b, and a threaded portion 22c.

[0040] The small diameter portion 22a has a diameter smaller than the diameter of the through hole 21a of the first tubular member 21, and is inserted into the through hole 21a from the left side.

[0041] The large diameter portion 22 b has a diameter larger than the diameter of the through hole 21 a and is in contact with the left end surface 21 e of the first tubular member 21 , thereby positioning the second tubular member 22 in the insertion direction.

[0042] The threaded portion 22 c is threadedly engaged with an internal thread portion provided on the inner peripheral surface of the first tubular member 21 .

[0043] Specifically, the second cylindrical member 22 is provided with an O-ring 7 at a corner formed by the large diameter portion 22b and the screw-fitting portion 22c, and the O-ring 7 seals the gap between the first cylindrical member 21 and the second cylindrical member 22. Furthermore, the plunger 6 is provided with an O-ring 10 at a corner formed by the large diameter portion 6b and the screw-fitting portion 6c, and the O-ring 10 seals the gap between the first cylindrical member 21 and the plunger 6. Furthermore, the second cylindrical member 22 is provided with an O-ring 8 in an annular groove portion formed at the right end portion of the small diameter portion 22a and open in the outer diameter direction, and the O-ring 8 seals between the outer peripheral surface of the right end portion of the small diameter portion 22a and the inner peripheral surface of the annular convex portion 21b.

[0044] An annular space 23 is formed between the outer peripheral surface of the small diameter portion 22 a and the inner peripheral surface of the first tubular member 21 , which are sandwiched between the O-rings 7 and 8 .

[0045] A partition wall 22d is formed between the small diameter portion 22a and the threaded portion 22c, and the partition wall 22d divides the internal space of the second tubular member 22 into two axial sides. A through hole 22j is formed in the center of the partition wall 22d so as to penetrate in the axial direction.

[0046] A primary chamber S1 is formed inside a portion of the second tubular member 22 on the left side of the partition wall 22d. The primary chamber S1 communicates with a primary side inlet 22h opened on the left side of the second tubular member 22.

[0047] A plurality of communication holes 22e for connecting the space 23 and the primary chamber S1 are formed along the circumferential direction near the outer diameter side of the partition wall 22d of the second tubular member 22. The space 23 and the communication holes 22e constitute a flow path for connecting a throttle port 34a described later and the primary chamber S1.

[0048] Furthermore, the small diameter portion 22 a is provided with a first annular groove 22 f and an orifice 221 , and a second annular groove 22 g and a hole 222 .

[0049] The first annular groove 22f and the second annular groove 22g are grooves opened toward the inner diameter side of the small diameter portion 22a, and are provided to be spaced apart in the axial direction.

[0050] The orifice 221 is provided so as to connect the first annular groove 22 f on the right side with the space 23 .

[0051] The hole 222 is provided so as to connect the left second annular groove 22 g and the space 23 .

[0052] The valve element 3 is arranged inside the small diameter portion 22 a so as to be slidable in the axial direction.

[0053] The valve body 3 is a cylindrical body, and a partition wall 31 is formed on the left side of the valve body 3 to divide the inner space thereof into two sides in the axial direction.

[0054] The valve element 3 has a concave portion 32 opened on the left side formed by the cylindrical portion 3A on the left side of the partition wall 31 and the partition wall 31 , and a concave portion 33 opened on the right side formed by the cylindrical portion 3B on the right side of the partition wall 31 and the partition wall 31 .

[0055] The recess 32 of the valve body 3 and the recess formed by the small diameter portion 22a and the partition wall 22d of the second tubular member 22 form a check spring chamber 9 in which a check spring 5 described later is arranged. The check spring chamber 9 communicates with the primary chamber S1 via the through hole 22j.

[0056] The portion 3B has a thick wall portion 34 formed on the left side and a thin wall portion 35 formed on the right side. The outer peripheral surface of the thick wall portion 34 and the outer peripheral surface of the thin wall portion 35 are flatly connected. The inner peripheral surface of the thick wall portion 34 is located closer to the inner diameter side than the inner peripheral surface of the thin wall portion 35. The right end of the thick wall portion 34 is a step portion 36 that protrudes toward the inner diameter side than the thin wall portion 35.

[0057] The thick portion 34 is provided with a plurality of throttle ports 34 a and a plurality of opening and closing ports 34 b along the circumferential direction.

[0058] The recessed portion 33 of the valve body 3 and the recessed portion 21 d of the first tubular member 21 form a secondary chamber S2 . The secondary chamber S2 communicates with a secondary-side inflow outlet 6 a provided to penetrate the plunger 6 .

[0059] Reference Figure 2 The throttle port 34a of the valve core 3, the first annular groove 22f of the second tubular member 22, and the throttle hole 221 constitute the flow adjustment mechanism V1. In addition, the opening and closing port 34b of the valve core 3, the second annular groove 22g of the second tubular member 22, and the hole 222 constitute the opening and closing mechanism V2.

[0060] return Figure 1 The flow control spring 4 is a coil spring, and is disposed between the step portion 36 of the valve body 3 and the plunger 6. That is, the flow control spring 4 urges the valve body 3 toward the left side.

[0061] The check spring 5 is a coil spring, and is disposed in the check spring chamber 9, in other words, between the partition wall 31 of the valve body 3 and the partition wall 22d of the second tubular member 22. That is, the check spring 5 urges the valve body 3 toward the right.

[0062] In a state where oil as a fluid does not flow through the flow control valve 1, the valve element 3 is arranged in a neutral position (see Figure 1 ). In the neutral position of the valve core 3, the throttle port 34a is in a state of being fully open and communicating with the first annular groove 22f, and the opening and closing port 34b is in a state of not communicating with the second annular groove 22g. In addition, the flow control spring 4 and the check spring 5 are balanced with each other by the force F1.

[0063] Next, the operation of the flow control valve 1 will be described.

[0064] First, use Figure 3 The operation of the flow control valve 1 in the controlled flow in which oil flows in from the primary-side inlet 22h and flows out to the secondary-side inlet port 6a will be described.

[0065] The oil flowing in from the primary side inlet 22h flows out to the secondary side inlet outlet 6a via the primary chamber S1, the communication hole 22e, the space 23, the throttle hole 221, the first annular groove 22f, the throttle port 34a, and the secondary chamber S2.

[0066] At this time, the pressure in the primary chamber S1 is slightly higher than that in the secondary chamber S2, and the valve core 3 moves to the right by a displacement of X without oil flowing. Figure 4 In addition, at this time, the opening and closing port 34b is closed by the small diameter portion 22a of the second tubular member 22. Figure 4 , the throttle port 34a in a state where oil does not flow is shown by a dotted line. The left-hand one of the two single-dot dash lines for indicating the displacement amount X is a meridian passing through the center of the throttle port 34a in a state where oil does not flow, and the right-hand one is a meridian passing through the center of the throttle port 34a after the valve core 3 is displaced to the right.

[0067] Here, the cross-sectional area of ​​the valve core 3 is set to S, the spring constant of the flow control spring 4 is set to K1, and the spring constant of the check spring 5 is set to K2. Furthermore, the flow rate flowing through the throttle hole 221 is set to Q, the cross-sectional area of ​​the throttle hole 221 is set to M, the pressure before flowing into the throttle hole 221 is set to P1, and the pressure after flowing into the throttle hole 221 is set to P2. Then, according to the formula of the throttle hole, the following formula (1) is established.

[0068]

[0069] Furthermore, when the opening area of ​​the throttle port 34a is represented by N and the pressure in the secondary chamber S2 is represented by P3, similarly to the formula (1), the following formula (2) holds.

[0070]

[0071] Therefore, based on equations (1) and (2), the following equation (3) is derived.

[0072]

[0073] Furthermore, in the axial direction of the valve body 3, the force balance equation of the following equation (4) holds true.

[0074] P1·S+(F1-K2·X)=P3·S+(F1+K1·X)

[0075] ∴P1-P3=(K1+K2)·X / S (4)

[0076] When a flow rate Qe exceeding the flow rate Q flows to the throttle hole 221 from this state, the value of the pressure difference (P1-P3) in equation (3) also increases, but when the value of the pressure difference (P1-P3) in equation (4) increases, the value of the displacement X also increases.

[0077] like Figure 4 As shown in FIG. 1 , when the displacement X increases, the opening area N of the throttle port 34a decreases. As a result, according to equation (3), As the value of becomes smaller, the oil is throttled, so the flow rate Qe decreases. As a result, the flow rate Q and the pressure difference (P1-P3) before and after the throttle hole 221 and the throttle port 34a are always constant and balanced.

[0078] That is, when a flow rate exceeding the flow rate Q attempts to flow through the orifice 221 , the valve element 3 operates so that a flow rate exceeding the constant flow rate Q does not flow.

[0079] Therefore, when expressing it as a curve graph, a certain constant flow rate is set as Q1, and a constant pressure difference of P1-P3 is set as P X , then Figure 5 Like that.

[0080] Next, use Figure 6 The operation of the flow control valve 1 in a free flow flow in which oil flows in from the secondary-side inflow port 6a and flows out to the primary-side inlet 22h will be described.

[0081] The oil flowing in from the secondary side inflow outlet 6a branches from the secondary chamber S2 to the opening and closing port 34b or the throttle port 34a. The oil flowing into the opening and closing port 34b flows into the space 23 via the flow path of the second annular groove 22g and the hole 222. The oil flowing into the throttle port 34a flows into the space 23 via the flow path of the first annular groove 22f and the throttle hole 221. The oil flowing into the space 23 flows out to the primary side inlet 22h via the communicating hole 22e and the primary chamber S1.

[0082] The flow rate of oil flowing into the secondary side inflow outlet 6a is set to Q', the pressure in the secondary chamber S2 is set to P1', and the pressure in the primary chamber S1 is set to P3'. The valve core 3 is balanced in a state where the displacement amount Y is shifted to the left from the state where oil does not flow. At this time, in the axial direction of the valve core 3, the force balance equation of the following equation (5) holds.

[0083] P1'·S+(F1-K1·Y)=P3'·S+(F1+K2·Y)

[0084] ∴P1'-P3'=(K1+K2)·Y / S (5)

[0085] Furthermore, let the flow rate through the throttling port 34a be Q1', the flow rate through the opening and closing port 34b be Q2', let the cross-sectional area of ​​the throttling hole 221 be M, let the opening area of ​​the throttling port 34a be N, and let the opening area of ​​the opening and closing port 34b be R. Then, according to the formula of the throttling hole, the following formulas (6) to (8) hold.

[0086]

[0087] Q'=Q1'+Q2' (8)

[0088] Therefore, based on equations (6) to (8), the following equation (9) is derived.

[0089]

[0090] Consider the case where a flow rate Qe' exceeding the flow rate Q' flows in from the secondary side inflow outlet 6a from this state. When the flow rate Qe' flows in, the pressure difference (P1'-P3') in the above formula (9) becomes larger, and when the value of the pressure difference (P1'-P3') in the formula (5) becomes larger, the value of the displacement Y also becomes larger. However, unlike the above-mentioned control flow, the opening area of ​​the throttle port 34a and the opening and closing port 34b of the valve core 3 is not restricted.

[0091] As described above, the flow control spring 4 is arranged at a position closer to the secondary chamber S2 than the throttle port 34a. Thus, the flow control spring 4 is arranged at a position offset to the right side of the throttle port 34a in the axial direction, so that the flow of oil entering and exiting the throttle port 34a can be prevented from being blocked by the flow control spring 4. In addition, the flow control spring 4 can be prevented from being deformed in the radial direction due to the flow of oil entering and exiting the throttle port 34a.

[0092] Therefore, it is not necessary to consider and select the number of turns and wire diameter of the flow control spring 4 according to the requirements of the oil, and the flow control spring 4 can be designed freely.

[0093] Furthermore, a step portion 36 is formed on the valve core 3 for the end of the flow control spring 4 to abut. Thus, the flow control spring 4 can be arranged at a position overlapping with the inner diameter side end of the throttle port 34a in the axial direction. In other words, the flow control spring 4 can be arranged at a position closer to the outer diameter side than the inner peripheral surface of the thick wall portion 34 opening the throttle port 34a, so that the flow of the fluid flowing out of the throttle port 34a can be reliably prevented from being blocked by the flow control spring 4. Furthermore, a part of the flow control spring 4 can be overlapped with the valve core 3 in the radial direction, so the axial dimension of the flow control valve 1 can be shortened. Furthermore, the misalignment of the axis of the valve core 3 and the flow control spring 4 can be suppressed.

[0094] Furthermore, the step portion 36 is provided on the inner circumferential surface of the valve core 3, and the flow control spring 4 can be arranged inside the valve core 3. Thus, the outer circumferential surface of the valve core 3 guided by the inner circumferential surface of the small diameter portion 22a of the second tubular member 22 can be ensured to be larger in the axial direction, so that the axial movement of the valve core 3 can be stabilized.

[0095] The valve core 3 is provided with an opening and closing port 34b for switching the communication state with the primary chamber S1, and the flow control spring 4 is arranged closer to the secondary chamber S2 than the opening and closing port 34b. Thus, the oil flowing in the opening and closing port 34b can be prevented from interfering with the flow control spring 4.

[0096] Furthermore, according to the flow control valve 1 , the flow rate adjustment mechanism V1 based on the throttle port 34 a and the opening and closing mechanism V2 based on the opening and closing port 34 b can be integrally configured compactly using one valve element 3 .

[0097] Furthermore, the flow control valve 1 includes the check spring 5 axially urging the valve element 3 toward the secondary chamber S2 , so that the axial motion of the valve element 3 is stable, and the flow adjustment mechanism V1 and the opening and closing mechanism V2 can function accurately.

[0098] The throttle port 34a communicates with the primary chamber S1 via the space 23 and the communication hole 22e that bypass the check spring 5. This prevents the oil flowing between the throttle port 34a and the primary chamber S1 from interfering with the check spring 5.

[0099] The housing 2 is composed of a first tubular member 21 and a second tubular member 22, and a space 23 is formed between the first tubular member 21 and the second tubular member 22. Thus, by combining the first tubular member 21 and the second tubular member 22, the space 23 that connects the throttle port 34a and the primary chamber S1 can be easily formed.

[0100] Example 2

[0101] Next, refer to Figure 7 , the valve of Example 2 is described. In addition, the repeated structural description of the same structure as the previous embodiment is omitted.

[0102] like Figure 7 As shown, the flow control valve 10 of the second embodiment is configured by directly assembling the tubular member 12, the valve element 13, the flow control spring 14, and the check spring 15 to a valve body 40 such as a main control valve.

[0103] The tubular member 12 is connected to the mounting hole 40 a of the valve body 40 in a sealing manner by screwing.

[0104] An annular space 123 is formed between the small diameter portion 12 a of the tubular member 12 and the inner peripheral surface of the mounting hole 40 a of the valve body 40 .

[0105] The recessed portion 133 of the valve body 13 and the mounting hole 40 a of the valve body 40 form a secondary chamber S2 ′. The secondary chamber S2 ′ communicates with a secondary-side inflow outlet 40 b provided in the valve body 40 .

[0106] As mentioned above, although the embodiment of the present invention is described with reference to the drawings, the specific structure is not limited to these embodiments, and the change and addition within the range which does not deviate from the summary of the present invention are also included in the present invention.

[0107] For example, in the above-mentioned embodiments 1 and 2, the flow control spring and the check spring are used to apply force to the valve core from both sides in the axial direction, but the present invention is not limited thereto. As long as there is at least a force applying unit, i.e., a flow control spring, which applies force to the valve core in the axial direction toward the primary chamber side, the structure of the check spring can be omitted.

[0108] Furthermore, in the aforementioned embodiments 1 and 2, a step portion is provided on the inner circumferential surface of the valve core and the end of the flow control spring abuts against the step portion, but it is also possible that a step portion is provided on the outer circumferential surface of the valve core and the flow control spring is embedded outside the valve core.

[0109] Furthermore, in the aforementioned embodiments 1 and 2, an example is given in which an opening and closing port is provided on the primary chamber side of the valve core and a throttling port is provided at a position closer to the secondary chamber side than the opening and closing port. However, it may also be that a throttling port is provided on the primary chamber side of the valve core and an opening and closing port is provided at a position closer to the secondary chamber side than the throttling port.

[0110] Furthermore, in the aforementioned embodiments 1 and 2, the flow path connecting the throttle port and the primary chamber is provided so as to bypass the check spring, but the flow path may be provided so as to cross the check spring.

[0111] Furthermore, the flow control spring and the check spring are illustrated as compression springs, but they may also be tension springs. In this case, the flow control spring may be arranged at a position closer to the primary chamber side than the throttle port, and the check spring may be arranged at a position closer to the secondary chamber side than the throttle port. Furthermore, the force applying unit is not limited to a spring, and may also be an elastic body such as a synthetic resin, a spring mechanism such as an air spring, or the like.

[0112] Furthermore, in the above-mentioned embodiments 1 and 2, an example of using oil as the fluid is shown, but it may be other liquids, gases such as gas, or a gas-liquid mixture.

[0113] Furthermore, in the above-mentioned first and second embodiments, an example is given in which the valve element is provided with an opening and closing port. However, an opening and closing port may not be provided, and the valve may be a valve that controls only the control flow rate.

[0114] Furthermore, in the above-mentioned first embodiment, an example is given in which the throttle hole is provided in the small diameter portion of the second tubular member, but the arrangement position of the throttle hole can be freely set, and the throttle hole may not be provided.

[0115] Description of symbols

[0116] 1: flow control valve (valve); 2: housing; 3: flow control valve core; 4: flow control spring (force unit); 5: check spring (primary chamber side force unit); 10: flow control valve (valve); 13: valve core; 14: flow control spring; 15: check spring; 21: first tubular component; 22: second tubular component; 22e: connecting hole (flow path); 23: space (flow path); 34a: throttling port; 34b: opening and closing port; 36: step portion; 40: valve body; 221: throttling hole; 222: hole; S1: primary chamber; S2, S2': secondary chamber; V1: flow control mechanism; V2: opening and closing mechanism.

Claims

1. A valve, comprising: case; A valve core, which is configured to be movable in the axial direction in the housing and has a throttling port, and the valve core divides a primary chamber and a secondary chamber of the housing; as well as a force applying unit for applying force to the valve core in the axial direction toward the primary chamber side, The valve core moves in the axial direction according to the pressure difference between the primary chamber and the secondary chamber. in, The biasing unit is disposed closer to the primary chamber side or the secondary chamber side than the throttle port.

2. The valve according to claim 1, wherein: The valve body is formed with a step portion against which an end portion of the urging unit abuts.

3. The valve according to claim 2, wherein: The step portion is provided on the inner peripheral surface of the valve core.

4. The valve according to claim 1, wherein: The valve core is also provided with an opening and closing port for switching the communication state between the primary chamber and the secondary chamber. The urging unit is disposed closer to the secondary chamber than the opening and closing port.

5. The valve according to any one of claims 1 to 4, wherein: The valve includes a primary chamber side force applying unit for applying force to the valve element in the axial direction toward the secondary chamber side. The throttle port communicates with the primary chamber via a flow path that bypasses the primary chamber-side biasing member.

Images