WO2022264876A1

WO2022264876A1 - Valve

Info

Publication number: WO2022264876A1
Application number: PCT/JP2022/022911
Authority: WO
Inventors: 亮一百枝; 渉高橋; 康平福留; 啓吾白藤
Original assignee: イーグル工業株式会社
Priority date: 2021-06-16
Filing date: 2022-06-07
Publication date: 2022-12-22
Also published as: JPWO2022264876A1

Abstract

Provided is a valve capable of reducing leakage of a working fluid between a back space and one space.　A gap S10 connecting one space S2 and a back space S3 is formed between a rod 20 and a valve housing 10, and the gap S10 has a bent portion E.

Description

valve

The present invention relates to a valve that controls working fluid.

Valves used to control working fluid in various industrial fields have a valve seat and a valve element that can be separated from and attached to the valve seat. Pressure and flow rate can be controlled.

Such valves include a spool valve in which a spool, which is a valve body, moves parallel to an opening, which is a valve seat, a butterfly valve, in which a valve body has a pivot shaft, and a A typical valve form is a lift valve that moves perpendicularly to the valve. Among these valves, lift valves are the most suitable for flow rate and pressure control.

Examples of lift valves include capacity control valves for variable capacity compressors used in air conditioning systems for automobiles. A variable displacement compressor includes a rotating shaft that is driven to rotate by an engine, a swash plate that is connected to the rotating shaft so that the inclination angle can be changed, and a compression piston that is connected to the swash plate. By changing the angle, the stroke amount of the piston is changed to control the discharge amount of the fluid. The inclination angle of the swash plate is determined by using a displacement control valve that is driven to open and close by electromagnetic force. By appropriately controlling the pressure in the control chamber while utilizing the control pressure Pc in the control chamber containing the swash plate, the pressure can be changed continuously.

The displacement control valve of Patent Document 1 includes a valve housing in which a primary pressure space through which a control fluid having a control pressure Pc passes and a secondary pressure space through which a control fluid having a suction pressure Ps passes; a valve seat provided between a secondary pressure space and a valve body having a valve contact portion provided in the primary pressure space and a rod portion provided in a back space on the side of the solenoid and capable of contacting and separating from the valve seat; The control pressure Pc of the control chamber is adjusted by moving the valve element by the electromagnetic force generated at .

In addition, the valve housing is formed with a communication passage that communicates the secondary pressure space and the back space. According to this, the secondary pressure space and the back space can be made to have the same pressure by the communication passage, and no pressure difference occurs on both sides in the axial direction of the valve body. can be controlled.

WO 2020/110925 (page 10, Figure 3)

In the capacity control valve of Patent Document 1, the rod portion of the valve body is inserted into a guide hole provided between the primary pressure space and the back space in the valve housing, and the rod portion is guided in the guide hole. It is designed to slide stably. However, since there is a minute gap between the outer peripheral surface of the rod portion and the inner peripheral surface of the guide hole, the fluid in the primary pressure space of the control pressure Pc will flow between the outer peripheral surface of the rod portion and the inner peripheral surface of the guide hole. There is a possibility that the control pressure Pc in the primary pressure space cannot be controlled with high accuracy due to a slight leakage into the back space through the space between the .

The present invention has been made with attention paid to such problems, and an object of the present invention is to provide a valve that can reduce the leakage of working fluid between the back space and one space.

In order to solve the above problems, the valve of the present invention is
a valve housing having a primary pressure space, a secondary pressure space, and a rear space adjacent to one of the primary pressure space and the secondary pressure space;
a valve seat disposed between the primary pressure space and the secondary pressure space;
a rod inserted through a guide hole of the valve housing provided between the one space and the back space and axially driven by a drive source;
a valve body that is seated or separated from the valve seat by driving the rod;
a communication means for communicating between the back space and the other of the primary pressure space and the secondary pressure space,
A gap connecting the one space and the back space is formed between the rod and the valve housing, and the gap has a bent portion.
According to this, pressure loss of the working fluid occurs when the direction of the working fluid flowing through the gap formed between the rod and the valve housing changes at the bent portion. Leakage of working fluid to the back space can be reduced.

A channel cross-sectional area of the bent portion may be the smallest when the valve is closed.
According to this, the flow passage cross-sectional area of the bent portion changes according to the valve opening, and since the flow passage cross-sectional area is the smallest when the valve is closed, the pressure of the working fluid generated at the bent portion when the valve is closed is loss can be increased.

When the valve is closed, the pair of axially facing surfaces constituting the bent portion may be spaced apart in the axial direction.
According to this, since the pair of axially facing surfaces of the rod and the valve housing do not contact each other when the valve is closed, the valve body can be reliably seated on the valve seat.

The side surface of the rod and the side surface of the valve housing may be the pair of axially opposed surfaces.
According to this, since the curved portion is formed at the entrance or the exit of the gap, it is possible to effectively prevent the working fluid from flowing into or out of the gap.

The pair of axially facing surfaces may be orthogonal to the axial direction.
According to this, it is possible to increase the pressure loss of the working fluid that occurs at the bent portion. Also, the pair of radially facing surfaces that are continuous with the pair of axially facing surfaces can be ensured to be long in the axial direction.

The bent portion may be crank-shaped.
According to this, since the direction of flow of the working fluid changes on both sides in the radial direction between the pair of axially facing surfaces, the pressure loss of the working fluid can be increased.

The effective pressure-receiving area of the rod may be equal to the effective pressure-receiving area of the valve.
According to this, since the force due to the fluid pressure in the back space acting on the rod and the force due to the fluid pressure in the other space acting on the valve body are canceled, the fluid in the back space and the other space The valve body can be moved with high precision regardless of the pressure.

1 is a cross-sectional view showing a displacement control valve in Example 1 according to the present invention; FIG. FIG. 4 is an enlarged cross-sectional view of a main part showing a gap between a guide hole and a rod when the valve is closed; FIG. 4 is a schematic diagram showing working fluid flowing through a gap; FIG. 4 is an enlarged cross-sectional view of a main part showing a state in which the displacement control valve is closed; FIG. 4 is an enlarged cross-sectional view of a main part showing a state in which the capacity control valve is opened; 4 is an enlarged cross-sectional view of a main part showing Modification 1 of the capacity control valve of Embodiment 1. FIG. 4 is a cross-sectional view showing Modification 2 of the capacity control valve of Embodiment 1. FIG. FIG. 5 is an enlarged cross-sectional view of a main part showing a displacement control valve according to Embodiment 2 of the present invention;

A form for implementing the valve according to the present invention will be described below based on an embodiment. Although the embodiment will be described with a displacement control valve as an example, it can also be applied to other uses.

A displacement control valve according to Embodiment 1 will be described with reference to FIGS. 1 to 5. FIG. In the following description, the left and right sides of the capacity control valve are defined as viewed from the front side of FIG. Specifically, the left side of the paper where the valve housing 10 is arranged is the left side of the displacement control valve, and the right side of the paper where the solenoid 80 is arranged is the right side of the displacement control valve.

The displacement control valve of the present invention is incorporated in a variable displacement compressor (not shown) used in an air conditioning system of an automobile or the like, and variably controls the pressure of a working fluid (hereinafter simply referred to as "fluid") that is a refrigerant. It is. As a result, the discharge amount of the variable displacement compressor is adjusted, and the air conditioning system is adjusted to achieve the target cooling capacity.

First, the variable capacity compressor will be explained. A variable displacement compressor has a casing with a discharge chamber, a suction chamber, a control chamber, and a plurality of cylinders. The variable capacity compressor is provided with a communication passage that directly communicates the discharge chamber and the control chamber. This communication passage is provided with a fixed orifice 9 for balancing the pressures of the discharge chamber and the control chamber (see FIG. 1).

The variable displacement compressor includes a rotating shaft that is rotatably driven by an engine (not shown) installed outside a casing, a swash plate that is tiltably connected to the rotating shaft by a hinge mechanism in a control chamber, and a swash plate. a plurality of pistons connected to the plate and fitted reciprocally within each cylinder. The pressure in the control chamber is determined by using a displacement control valve V1 that is driven to open and close by electromagnetic force. It is appropriately controlled using the control pressure Pc of the control chamber containing the plate. As a result, the stroke amount of the piston changes as the inclination angle of the swash plate changes, and the discharge amount of the variable displacement compressor changes.

As shown in FIG. 1, the displacement control valve V1 of the first embodiment, which is incorporated in the variable displacement compressor, changes depending on the current applied to a coil 86 that constitutes a solenoid 80 as a drive source. , the valve 50 opens and closes. The control pressure Pc in the control chamber is variably controlled by controlling the opening and closing of the valve 50 to change the flow rate flowing out from the control chamber to the suction chamber. In addition, the discharge fluid at the discharge pressure Pd of the discharge chamber is constantly supplied to the control chamber through the fixed orifice 9, so that the control pressure Pc in the control chamber can be increased by closing the valve 50 in the displacement control valve V1. It has become.

As shown in FIG. 1, in the displacement control valve V1 of the first embodiment, the valve 50 is composed of a contact portion 54 as a valve element and a valve seat 40a. The contact portion 54 is provided on the valve portion 51 of the movable body 56 . The valve seat 40 a is provided on a cylindrical valve seat member 40 . The valve seat member 40 is press-fitted into the communication hole portion 10b of the valve housing 10 and fixed.

A tapered contact portion 54 is formed on the right side of the valve portion 51 in the axial direction. The valve 50 is opened and closed by moving the contact portion 54 into contact with and away from the valve seat 40a in the axial direction.

Next, the structure of the displacement control valve V1 will be explained. The capacity control valve V1 is mainly composed of a valve housing 10 and a valve seat member 40 made of a metal material, a solenoid 80 as a drive source, and a movable body 56. As shown in FIG.

As shown in FIGS. 1 and 2, the movable body 56 is composed of a rod portion 20 as a rod element and a valve portion 51 as a valve element. The rod portion 20 extends axially. The valve portion 51 is formed at the axial left end of the rod portion 20 .

The valve portion 51 has a large diameter portion 53 and a contact portion 54 . The large diameter portion 53 has a larger diameter than the rod portion 20 . The contact portion 54 has a tapered shape that gradually decreases in diameter from the large diameter portion 53 toward the rod portion 20 on the right side in the axial direction.

Also, the valve portion 51 is arranged on the left side of the valve seat member 40 in the axial direction. The rod portion 20 is inserted through the valve seat member 40 and extends to the right in the axial direction.

The rod portion 20 is formed with a first small diameter portion 21, a large diameter portion 22, and a second small diameter portion 23 in order from the left side in the axial direction.

The second small diameter portion 23 is slightly larger in diameter than the first small diameter portion 21 . The large diameter portion 22 has a larger diameter than the second small diameter portion 23 . The first small diameter portion 21 and the second small diameter portion 23 may have the same diameter, or the first small diameter portion 21 may have a larger diameter than the second small diameter portion 23 .

The large-diameter portion 22 is inserted through a guide hole 10e provided in the valve housing 10, which will be described later. A specific structure of the large diameter portion 22 will be described in detail later.

A primary pressure space S1 is formed on the axial left side of the valve housing 10, and the primary pressure space S1 communicates with the control chamber through an inlet port 11 that opens axially leftward. A secondary pressure space S2 is formed axially to the right of the primary pressure space S1 in the valve housing 10, and the secondary pressure space S2 communicates with the discharge chamber through an outlet port 12 penetrating in the radial direction.

A recess 10a is formed in the valve housing 10. The recess 10a is recessed axially rightward from the left end in the axial direction and is open at the left end in the axial direction. The inlet port 11 is an opening at the left end in the axial direction of the recess 10a. The axial left end of the valve housing 10 is closed by a structural member (not shown) forming a control chamber. A space surrounded by this component and the recess 10a is a primary pressure space S1.

In addition, the valve housing 10 is formed with a recess 10c that is recessed leftward in the axial direction on the inner diameter side of the right end in the axial direction. A guide hole 10e and a communicating hole portion 10b are formed between the recessed portion 10a and the recessed portion 10c so as to communicate with each other in the axial direction. The communication hole portion 10b has a smaller diameter than the

recesses

10a and 10c. The guide hole 10e has a diameter smaller than that of the communication hole portion 10b. A space surrounded by the communication hole portion 10b serves as a secondary pressure space S2.

In addition, the valve housing 10 has an annular inner land 10f (see FIG. 2) extending radially inwardly between the communication hole portion 10b and the recess portion 10c. The guide hole 10e is provided on the surface of the inner land 10f and extends in the axial direction.

The valve seat member 40 includes a tubular portion 41 and an annular convex portion 42 (see FIGS. 4 and 5). The cylindrical portion 41 extends cylindrically in the axial direction. The annular convex portion 42 protrudes radially outward from the axial left end of the cylindrical portion 41 . The inner diameter of the tubular portion 41 is formed to be larger than that of the first small diameter portion 21 of the rod portion 20 .

The valve seat member 40 is hermetically fixed to the valve housing 10 by being press-fitted from the left in the axial direction into the communication hole 10b penetrating the bottom of the recess 10a. In addition, since the annular projection 42 abuts against the bottom end surface 10d (see FIGS. 4 and 5) of the recess 10a, the valve seat member 40 is prevented from being excessively inserted into the communication hole 10b. are axially positioned.

In addition, the valve seat member 40 is formed with a valve seat 40a on the inner diameter side of the left end in the axial direction. The valve seat 40a has a tapered shape whose diameter gradually decreases toward the right side in the axial direction.

A flange portion 82d of the center post 82 is internally fitted and fixed to the concave portion 10c of the valve housing 10 from the axial right side. Furthermore, the valve housing 10, the center post 82, and the casing 81 are integrally connected by fitting and fixing the casing 81 from the right side in the axial direction.

A through hole 13 is formed in the valve housing 10 as a communication means extending in the axial direction. The through-holes 13 are open to the bottom surfaces of the

recesses

10a and 10c at both ends in the axial direction. This through hole 13 is formed to have a constant cross section.

As shown in FIG. 1, the solenoid 80 is mainly composed of a casing 81, a center post 82, a rod portion 20, a movable iron core 84, a coil spring 85, a coil 86 and a sleeve 87. there is

The casing 81 has a recess 81b and a through hole 81a. The recessed portion 81b is recessed from the axial left side of the casing 81 toward the right side. The through hole 81a is formed extending axially rightward from the bottom of the recess 81b.

The center post 82 has a substantially cylindrical shape made of a rigid body that is a magnetic material such as iron or silicon steel. Specifically, the center post 82 includes an axially extending cylindrical portion 82b and an annular flange portion 82d. The cylindrical portion 82b has an insertion hole 82c. The rod portion 20 is inserted through the insertion hole 82c so as to reciprocate in the axial direction. The flange portion 82d extends radially from the outer peripheral surface of the left end portion of the cylindrical portion 82b in the axial direction.

The cylindrical portion 82b is inserted into the through hole 81a of the casing 81 from the axial left side. The center post 82 is positioned with respect to the valve housing 10 and the casing 81 by axially holding the flange portion 82 d between the bottom of the recess 10 c of the valve housing 10 and the bottom of the recess 81 b of the casing 81 .

The axial right end of the rod portion 20 is inserted and fixed to the movable core 84 .

The coil spring 85 is a compression spring and is arranged between the center post 82 and the movable iron core 84. The axial left end of the coil spring 85 is fitted into a recess 82e formed in the axial right end of the cylindrical portion 82b of the center post 82. As shown in FIG. That is, the coil spring 85 urges the movable iron core 84 axially rightward, which is the valve closing direction of the valve 50 .

A coil 86 is an excitation coil wound around the outside of the center post 82 via a bobbin.

The sleeve 87 has a cylindrical shape with a bottom. A part of the center post 82 , the movable iron core 84 , the coil spring 85 and a part of the rod portion 20 are housed in the sleeve 87 .

The back space S3 inside the solenoid 80 is mainly the space inside the sleeve 87 on the back side of the valve portion 51 separated from the secondary pressure space S2. Specifically, it includes the space between the recess 10 c and the left end of the center post 82 , the space inside the center post 82 , and the left and right spaces of the movable iron core 84 inside the sleeve 87 .

Next, the structures of the large diameter portion 22 of the rod portion 20 and the guide hole 10e of the valve housing 10 will be described with reference to FIGS. 2 and 3. FIG.

As shown in FIGS. 2 and 3, the large-diameter portion 22 is formed with a first portion 24, a second portion 25, and a third portion 26 in order from the right side in the axial direction. The first portion 24 and the second portion 25 are arranged within the guide hole 10e. Further, the third portion 26 is arranged on the left side of the guide hole 10e in the axial direction, that is, in the secondary pressure space S2.

The first portion 24 has a smaller diameter than the second portion 25. The second portion 25 has a smaller diameter than the third portion 26 . That is, the diameter of the large diameter portion 22 increases stepwise from the right side in the axial direction toward the left side in the axial direction.

The outer peripheral surface 24a of the first portion 24, the outer peripheral surface 25a of the second portion 25, and the outer peripheral surface 26a of the third portion 26 are axial portions extending parallel to each other in the axial direction. A right end surface 25b of the second portion 25 and a right end surface 26b of the third portion 26 are radial portions extending in the radial direction.

Specifically, the right end surface 25b of the second portion 25 extends radially perpendicular to the outer peripheral surface 24a of the first portion 24 and the outer peripheral surface 25a of the second portion 25. As shown in FIG. A right end surface 26b of the third portion 26 extends radially perpendicular to the outer peripheral surface 25a of the second portion 25 and the outer peripheral surface 26a of the third portion 26 .

A tapered surface portion 27 (see FIG. 2) is formed between the outer peripheral surface 26a of the third portion 26 and the first small diameter portion 21 of the rod portion 20, the diameter of which decreases toward the left in the axial direction.

A first portion 14, a second portion 15, and a third portion 16 are formed in the valve housing 10 in order from the right side in the axial direction, and these

portions

14, 15, and 16 define the guide hole 10e.

The inner peripheral surface 14a of the first portion 14 extends from the right surface of the inner land 10f in parallel with the outer peripheral surface 24a of the first portion 24 of the large-diameter portion 22, and then slopes so as to reduce its diameter leftward in the axial direction. extended.

The inner peripheral surface 15a of the second portion 15 extends parallel to the outer peripheral surface 24a of the first portion 24 of the large diameter portion 22 from the axial left end of the inner peripheral surface 14a. A left end surface 15b of the second portion 15 extends perpendicularly to the outer diameter direction from the axial left end of the inner peripheral surface 15a.

Specifically, the left end face 15b extends parallel to the right end face 25b of the second portion 25. That is, the right end surface 25b and the left end surface 15b are a pair of axially opposed surfaces that face each other in the axial direction. In addition, the inner peripheral surface 15a and the outer peripheral surface 24a form a pair of radially facing surfaces facing each other in the radial direction.

The inner peripheral surface 16a of the third portion 16 extends axially leftward from the outer diameter end of the left end surface 15b in parallel with the outer peripheral surface 25a of the second portion 25 of the large diameter portion 22 . A left end surface 16b of the third portion 16 extends perpendicularly to the outer diameter direction from the left end of the inner peripheral surface 16a. In other words, the left end surface 16b is the left end side surface of the inner land 10f.

Further, the left end face 16b extends parallel to the right end face 26b of the third portion 26. That is, the right end surface 26b and the left end surface 16b are a pair of axially opposed surfaces that face each other in the axial direction. In addition, the inner peripheral surface 16a and the outer peripheral surface 25a form a pair of radially facing surfaces facing each other in the radial direction.

Between the first portion 24, the second portion 25 and the third portion 26 of the large diameter portion 22 of the rod portion 20 and the first portion 14, the second portion 15 and the third portion 16 of the valve housing 10, A gap S10 is formed connecting the secondary pressure space S2 and the rear space S3.

Hereinafter, in the gap S10, the portion between the outer peripheral surface 24a of the first portion 24 and the inner peripheral surface 14a of the first portion 14 is defined as the first gap S11, and the outer peripheral surface 24a of the first portion 24 and the second portion 15 are defined as the first gap S11. The second gap S12 is the portion between the inner peripheral surface 15a of the second portion 25, the third gap S13 is the portion between the right end surface 25b of the second portion 25 and the left end surface 15b of the second portion 15, and the outer periphery of the second portion 25 A portion between the surface 25a and the inner peripheral surface 16a of the third portion 16 is defined as a fourth gap S14, and a portion between the right end surface 26b of the third portion 26 and the left end surface 16b of the third portion 16 is defined as a fifth gap S15. described as.

The gap S10 is formed with a plurality of bent portions E bent in a substantially L shape. Specifically, a bent portion E1 is formed by the second gap S12 and the third gap S13. A bent portion E2 is formed by the third gap S13 and the fourth gap S14. A bent portion E3 is formed by the fourth gap S14 and the fifth gap S15.

The second gap S12, the third gap S13, and the fourth gap S14 in the gap S10, that is, the bent portion E1 and the bent portion E2 form a crank shape. In other words, the second gap S12 extends axially rightward from the inner diameter side of the third gap S13, and the fourth gap S14 extends axially leftward from the outer diameter side of the third gap S13.

Further, the radial distance Δ12 between the outer peripheral surface 24a and the inner peripheral surface 15a in the second gap S12 and the radial distance Δ14 between the outer peripheral surface 25a and the inner peripheral surface 16a in the fourth gap S14 are substantially the same. There is (Δ12=Δ14). Note that the radial distance Δ12 of the second gap S12 and the radial distance Δ14 of the fourth gap S14 may be different.

Also, the second gap S12 and the fourth gap S14 are minute gaps. The inner peripheral surface 15a of the second portion 15 and the inner peripheral surface 16a of the third portion 16 of the valve housing 10 slide on the outer peripheral surface 24a of the first portion 24 and the outer peripheral surface 25a of the second portion 25 of the rod portion 20. It is a guide part that guides movement.

Next, the opening/closing operation of the capacity control valve V1 will be described.

First, the non-energized state of the displacement control valve V1 will be described. As shown in FIGS. 1 and 4, when the displacement control valve V1 is in a non-energized state, the movable iron core 84 is pressed axially rightward by the biasing force of the coil spring 85, that is, in the valve closing direction. The contact portion 54 of the valve portion 51 is seated on the valve seat 40a, and the valve 50 is closed.

Specifically, the valve portion 51, which is also tapered to expand axially leftward, contacts the valve seat 40a, which is tapered to expand axially leftward. The contact part 54 contacts and is seated.

At this time, as shown in FIG. 3, the right end surface 25b of the second portion 25 of the rod portion 20 and the left end surface 15b of the second portion 15 of the valve housing 10 are axially separated by a slight axial distance Δ13. away. Further, the right end surface 26b of the third portion 26 of the rod portion 20 and the left end surface 16b of the third portion 16 of the valve housing 10 are separated in the axial direction by a slight axial distance Δ15.

The lengths of the axial distance Δ13 and the axial distance Δ15 are substantially the same (Δ13=Δ15). In this embodiment, the lengths of the axial distance Δ13 and the axial distance Δ15 are substantially the same, but they may be different.

Also, when the valve 50 is closed, the axial distances Δ13, Δ15 are longer than the radial distances Δ12, Δ14 (Δ13, Δ15>Δ12, Δ14).

When the valve 50 is closed, the right end face 25b of the rod portion 20 and the left end face 15b of the valve housing 10, and the right end face 26b of the rod portion 20 and the left end face 16b of the valve housing 10 are the most in the movable region of the movable body 56. Axial proximity. In other words, when the valve 50 is closed, the channel cross-sectional areas of the third gap S13 and the fifth gap S15 are the smallest.

Returning to FIG. 4, when the valve 50 is closed, the effective pressure-receiving area A of the valve portion 51, the effective pressure-receiving area B of the large-diameter portion 22, and the right axial direction are positive, and the valve portion 51 has a primary pressure space S1 The force (F P1 ) due to the pressure P1 of the working fluid in the secondary pressure space S2 (F _P1 )=(P1×(AB)) and the force (F _P2 ) due to the pressure P2 of the working fluid in the secondary pressure space S2=−(P2×(A −B)) and the biasing force (F _sp ) of the coil spring 85 (that is, the force F _rod =F _P1 −F _P2 +F _sp acts on the valve portion 51, with the right direction being positive). ing).

At this time, the working fluid in the primary pressure space S1 acts on the left end surface of the valve portion 51 in the axial direction. Since the primary pressure space S1 and the back space S3 communicate with each other through the through hole 13 provided in the valve housing 10, the working fluid in the primary pressure space S1 flows into the back space S3. .

Thus, the working fluid flowing into the primary pressure space S1 and the back space S3 is the working fluid supplied from the inlet port 11 and having the same primary pressure P1. Further, since the effective pressure receiving area A of the valve portion 51 and the effective pressure receiving area B of the large diameter portion 22 are equal (A=B), the forces acting on the valve portion 51 due to the pressures P1 and P2 of the working fluid (F _P1 ), (F _P2 ) are both nearly zero.

That is, a force F _rod =F _sp substantially acts on the valve portion 51 with the rightward direction as positive. As a result, the valve portion 51 is pressed in the valve closing direction to close the valve 50 .

Next, the energized state of the capacity control valve V1 will be described. As shown in FIG. 5, when the displacement control valve V1 is energized (that is, during normal control, so-called duty control), the electromagnetic force (F _sol ) generated by applying a current to the solenoid 80 is the force F _rod (F _sol > F _rod ), the movable iron core 84 is pulled toward the center post 82, that is, toward the left in the axial direction, and the movable body 56 fixed to the movable iron core 84 moves toward the left in the axial direction, that is, in the valve opening direction. By moving together, the contact portion 54 of the valve portion 51 is separated from the valve seat 40a, and the valve 50 is opened.

When the valve 50 is open, the right end face 25b of the rod portion 20 and the left end face 15b of the valve housing 10 are axially separated by an axial distance Δ13'. Further, the right end surface 26b of the rod portion 20 and the left end surface 16b of the valve housing 10 are axially separated by an axial distance Δ15'. The axial distances Δ13' and Δ15' when the valve is open are longer than the axial distances Δ13 and Δ15 when the valve is closed (Δ13, Δ15<Δ13', Δ15'). Also, the axial distances Δ13' and Δ15' are the same distance.

On the other hand, the radial distance Δ12 of the second gap S12 and the radial distance Δ14 of the fourth gap S14 do not change regardless of the opening of the valve 50.

At this time, an electromagnetic force (F _sol ) acts on the valve portion 51 to the left in the axial direction, and a force F _rod acts to the right in the axial direction (that is, when the right direction is positive, the force F _rod - F _sol at work).

Thus, the displacement control valve V1 is controlled by the valve opening of the valve 50, which is adjusted by the balance between the electromagnetic force (F _sol ) of the solenoid 80 and the biasing force (F _sp ) of the coil spring 85. The pressure P1 of the working fluid in S1 can be controlled accordingly.

Next, the flow of the working fluid within the gap S10 when the valve is closed will be described.

Returning to FIG. 3, when the valve 50 is closed, the working fluid flows in the first gap S11 to the left in the axial direction, that is, from the high-pressure side rear space S3 toward the low-pressure side secondary pressure space S2 as indicated by the arrow FL1. flow. In addition, in FIG. 3, the thickness and length of the arrows are shown extremely for convenience of explanation.

The working fluid flowing through the first gap S11 flows into the second gap S12, which has a flow passage cross-sectional area smaller than that of the first gap S11, as indicated by an arrow FL2. Since the second gap S12 functions as a throttle, pressure loss occurs in the working fluid flowing through the second gap S12 due to friction between the outer peripheral surface 24a of the first portion 24 and the inner peripheral surface 15a of the second portion 15. .

The working fluid flowing through the second gap S12 flows into the third gap S13, which has a flow passage cross-sectional area larger than that of the first gap S11, as indicated by an arrow FL3. When the working fluid flowing in the axial direction along the second gap S12 is deflected at approximately 90 degrees toward the third gap S13 extending in the radially outer direction, pressure loss in the working fluid increases. For convenience of explanation, it is shown as an example that a vortex is generated in the vicinity of the connecting portion between the second gap S12 and the third gap S13. Illustrations of vortices are the same thereafter.

The working fluid flowing through the third gap S13 flows into the fourth gap S14, which has a flow passage cross-sectional area smaller than that of the third gap S13, as indicated by an arrow FL4. When the working fluid flowing in the outer diameter direction along the third gap S13 is deflected at approximately 90 degrees toward the axially extending fourth gap S14, pressure loss occurs in the working fluid.

Further, since the fourth gap S14 functions as a throttle, the working fluid flowing through the fourth gap S14 experiences pressure loss due to friction between the outer peripheral surface 25a of the second portion 25 and the inner peripheral surface 16a of the third portion 16. occurs.

The working fluid flowing through the fourth gap S14 flows into the fifth gap S15, which has a flow passage cross-sectional area larger than that of the fourth gap S14, as indicated by an arrow FL5. When the working fluid axially flowing along the fourth gap S14 is deflected at approximately 90 degrees toward the fifth gap S15 extending in the radially outer direction, pressure loss occurs in the working fluid.

As described above, the gap S10 is formed between the rod portion 20 and the valve housing 10 to connect the secondary pressure space S2 and the rear space S3. This gap S10 has a bent portion E and is at least partially defined by a guide hole 10e. The second gap S12, the third gap S13, and the fourth gap S14 are defined by the inner peripheral surface of the valve housing 10 and the outer peripheral surface of the rod portion 20 that form the guide hole 10e.

According to this, when the direction of the working fluid flowing through the gap S10 from the back space S3 on the high pressure side toward the secondary pressure space S2 changes at the bend E, pressure loss of the working fluid occurs. Leakage of the working fluid to the secondary pressure space S2 can be reduced.

In addition, a plurality of bends E1 to E3 are formed in the gap S10, and pressure loss occurs in the working fluid at each of the bends E1 to E3, so that the fluid pressure of the working fluid increases toward the secondary pressure space S2. Decrease gradually. In the fifth gap S15 closest to the secondary pressure space S2 in the gap S10, the pressure difference between the fluid pressure and the fluid pressure in the secondary pressure space S2 is almost eliminated. A state in which there is almost no fluid leakage can be achieved.

Also, when the valve 50 is closed, the channel cross-sectional areas of the bent portions E1 to E3 are the smallest. Specifically, the flow channel cross-sectional areas of the bends E1 to E3 change according to the valve opening degree, and when the valve 50 is closed, the flow channel cross-sectional areas of the third gap S13 and the fifth gap S15 Since it is the smallest, it is possible to increase the pressure loss of the working fluid that occurs at the bent portion when the valve is closed.

Also, when the valve 50 is closed, the right end surface 25b of the second portion 25 of the rod portion 20 and the left end surface 15b of the second portion 15 of the valve housing 10 are separated in the axial direction. Similarly, the right end face 26b of the third portion 26 of the rod portion 20 and the left end face 16b of the third portion 16 of the valve housing 10 are axially separated from each other. According to this, when the valve 50 is closed, the right end face 25b and the left end face 15b, and the right end face 26b and the left end face 16b do not come into contact with each other, so that the valve portion 51 can be reliably seated on the valve seat 40a.

Further, between the outer peripheral surface of the rod portion 20 and the inner peripheral surface of the valve housing 10 forming the guide hole 10e, the right end surface 25b of the second portion 25 of the rod portion 20 and the second portion 15 of the valve housing 10 are positioned. A left end face 15b is formed. According to this, the bent portions E1 and E2 are respectively formed on both sides in the radial direction of the third gap S13 formed between the right end face 25b and the left end face 15b. S13 and the fourth gap S14 are crank-shaped, and the direction of flow of the working fluid changes at each of the bent portions E1 and E2, so the pressure loss of the working fluid can be increased.

Also, the right end surface 26b, which is the side surface of the rod portion 20, and the left end surface 16b, which is the side surface of the valve housing 10, face each other in the axial direction. According to this, since the bent portion E3 is formed on the outlet side of the gap S10, that is, on the side of the secondary pressure space S2, it is possible to effectively prevent the working fluid from flowing out of the gap S10 into the secondary pressure space S2. can.

The right end faces 25b, 26b of the rod portion 20 and the left end faces 15b, 16b of the valve housing 10 are orthogonal to the axial direction. That is, the pressure loss of the working fluid can be increased at the bends E1 to E3 including the right end faces 25b, 26b and the left end faces 15b, 16b.

Furthermore, the axial length of the inner

peripheral surfaces

15a and 16a that are continuous with the left end surfaces 15b and 16b, the axial length of the outer

peripheral surfaces

24a and 25a that are continuous with the right end surfaces 25b and 26b, that is, the second Since the axial length of the gap S12 and the fourth gap S14 can be ensured long, the sealing performance of the gap S10 is improved.

Also, the effective pressure receiving area B of the large diameter portion 22 , that is, the effective pressure receiving area B of the rod portion 20 is equal to the effective pressure receiving area A of the valve portion 51 , that is, the effective pressure receiving area A of the valve 50 . According to this, the force due to the fluid pressure in the back space S3 acting on the rod portion 20 and the force due to the fluid pressure in the primary pressure space S1 acting on the valve portion 51 are canceled. In addition, since the force due to the fluid pressure in the secondary pressure space S2 acting on the rod portion 20 and the force due to the fluid pressure in the secondary pressure space S2 acting on the valve portion 51 are canceled, the primary pressure The movable body 56 can be moved accurately regardless of the fluid pressure in the space S1, the secondary pressure space S2, and the back space S3.

In addition, the outer peripheral surface of the large diameter portion 22 and the guide hole 10e increase in diameter in a stepped manner toward the left side in the axial direction. According to this, the assembly is completed by inserting the movable body 56 into the guide hole 10e from the left side in the axial direction, so that the displacement control valve V1 can be easily assembled.

In the first embodiment, the left end surface 15b of the valve housing 10 and the right end surface 25b of the rod portion 20, and the left end surface 16b of the valve housing 10 and the right end surface 26b of the rod portion 20, which are surfaces facing each other in the axial direction, Although the configuration orthogonal to the axial direction is illustrated, the opposing surface may be inclined in the axial direction.

In the first embodiment, the primary pressure space, the secondary pressure space, and the rear space are formed in this order from the left in the axial direction. position may be reversed. For reference, Fig. 6 shows Modified Example 1 in which the arrangement of the primary pressure space S1' and the secondary pressure space S2' is opposite to that of Example 1 in the axial direction.

Also, in the above embodiment, a normally closed valve has been described, but the valve is not limited to this, and may be a normally open valve. For reference, by arranging the coil spring 851 between the movable iron core 84 and the sleeve 87, the contact portion 54 of the valve portion 51 is separated from the valve seat 40a when the current is not supplied, and the valve 501 is opened. Example 2 is shown in FIG.

Next, a displacement control valve according to Embodiment 2 will be described with reference to FIG. It should be noted that descriptions of configurations that are the same as those of the first embodiment will be omitted.

As shown in FIG. 8, in the displacement control valve V2 of the second embodiment, an inner land 10g extending in the radial direction is formed between the recess 10a and the communication hole 10b in the valve housing 10. As shown in FIG. A through hole 10h is formed through the inner land 10g in the axial direction.

Further, the guide hole 101e of the valve housing 10 is formed so as to increase in diameter in a stepwise manner toward the right side in the axial direction. Specifically, the inner peripheral surface of the valve housing 10 forming the guide hole 101e has two surfaces 102 extending in the axial direction and one surface 103 extending radially between the axial surfaces 102. there is

The movable body 561 has a valve portion 511 at its left end in the axial direction. The valve portion 511 has a larger diameter than the through hole 10h. The valve portion 511 is arranged on the axial right side of the inner land 10g, that is, in the secondary pressure space S2.

The movable body 561 is biased leftward in the axial direction by a coil spring (not shown). As a result, the left end surface 511a of the valve portion 511 comes into contact with the edge portion 511b, which is the valve seat of the through hole 10h in the inner land 10g, and the valve 502 is closed. Thus, in the second embodiment, the left end surface 511a of the valve portion 511 and the edge portion 511b of the through hole 10h in the inner land 10g constitute the valve 502. As shown in FIG.

The outer peripheral surface of the insertion portion 221 of the rod portion 201, which is inserted through the guide hole 101e, is formed so as to increase in diameter stepwise toward the right side in the axial direction. Specifically, the outer peripheral surface of the insertion portion 221 has two surfaces 202 extending in the axial direction and one surface 203 extending radially between the surfaces 202 in the axial direction. Moreover, the rod portion 201 has a facing surface 204 axially facing the right surface 10j of the inner land 10f of the valve housing 10 .

The surface 102 of the valve housing 10 and the surface 202 of the insertion portion 221 are radially opposed surfaces that face each other in the radial direction. Further, the surface 103 of the valve housing 10 and the surface 203 of the insertion portion 221, and the right surface 10j of the valve housing 10 and the opposed surface 204 of the rod portion 201 are axially opposed surfaces that face each other in the axial direction.

When the valve 502 is closed, the surface 103 of the valve housing 10 and the surface 203 of the insertion portion 221 are closest to each other in the movable area of the movable body 561 and face each other. In addition, the right surface 10j of the valve housing 10 and the opposing surface 204 of the rod portion 201 are arranged closest to each other in the movable area of the movable body 561 so as to face each other.

In this way, since a plurality of bent portions are formed in the gap between the rod portion 201 and the valve housing 10, pressure loss occurs when the working fluid flows through the gap, and the back space when the valve 502 is closed. It is possible to suppress the working fluid from leaking from S3 to the secondary pressure space S2.

Although the embodiments of the present invention have been described above with reference to the drawings, the specific configuration is not limited to these embodiments, and any changes or additions within the scope of the present invention are included in the present invention. be

For example, in Examples 1 and 2, the configuration in which the valve element and the rod element are integrated was exemplified, but the configuration is not limited to this, and the valve element and the rod element may be configured as separate members. Also, although the valve element has been exemplified as having a tapered shape, it can be freely changed.

Also, in the first embodiment, the coil spring 85 is a push spring, but it may be a pull spring, for example. Further, the spring is not limited to the coil spring, and a leaf spring or the like may be used.

Also, in the first and second embodiments, the coil spring is arranged in the back space, but the place where the biasing means is arranged may be freely changed. For example, the biasing means may be arranged in the primary pressure space or the secondary pressure space.

In the first and second embodiments, the effective pressure-receiving area of the valve element and the effective pressure-receiving area of the rod element are equal. good too.

Also, in the first and second embodiments, the example in which the valve is a capacity control valve has been described, but it may be an expansion valve or the like arranged between the condenser and the evaporator in an air conditioning system, for example.

In the first and second embodiments, the communication means is a through-hole provided in the valve housing, but the communication means is not limited to this, and the communication means is a communication passage that directly communicates the back space and the control chamber. may

Further, in Examples 1 and 2, the diameter of the outer peripheral surface of the insertion portion of the rod and the guide hole increased or decreased in a stepwise manner toward the left side in the axial direction. As long as a portion is formed, it does not have to be expanded or contracted stepwise. Moreover, the outer peripheral surface of the insertion portion of the rod and the number of stages of the guide holes may be freely changed.

Also, in the first and second embodiments, the through holes provided in the valve housing itself are used as the guide holes, but the valve housing may be formed of a plurality of members. For example, the valve housing may be formed of a valve housing main body and a cylindrical body fitted and fixed to the valve housing main body, and the through hole of the cylindrical body may serve as the guide hole.

In addition, in Examples 1 and 2, the form in which a plurality of bent portions are formed in the gap between the rod and the valve housing was exemplified, but at least one bent portion may be formed in the gap.

Further, in Examples 1 and 2, the flow channel cross-sectional area of the bent portion is the smallest when the valve is closed. It may be smaller.

10 valve housing 10e guide hole 11 inlet port 12 outlet port 13 through hole (communication means)
15a inner peripheral surface (radial facing surface)
15b Left end surface (axially opposed surface)
16a inner peripheral surface (diametrically opposed surface)
16b Left end surface (axially facing surface)
20 rod part (rod element, rod)
22 large-diameter portion 24a outer peripheral surface (radially facing surface)
25a outer peripheral surface (radial facing surface)
25b Right end surface (axially facing surface)
26b Right end surface (axially facing surface)
40 valve seat member 40a valve seat 50 valve 51 valve portion (valve element, valve body)
54 contact part 56 movable body 80 solenoid (driving source)
201 rod part (rod element, rod)
221

insertion parts

501, 502 valve 511 valve part (valve element, valve body)
511a Left end face 511b End (valve seat)
561 movable bodies A, B effective pressure receiving areas E, E1, E2, E3 bending portions S1, S1' primary pressure spaces S2, S2' secondary pressure spaces S3 rear space S10 gap S11 first gap S12 second gap S13 third Gap S14 Fourth gap S15 Fifth gap V1, V2 Capacity control valve

Claims

a valve housing having a primary pressure space, a secondary pressure space, and a rear space adjacent to one of the primary pressure space and the secondary pressure space;
a valve seat disposed between the primary pressure space and the secondary pressure space;
a rod inserted through a guide hole of the valve housing provided between the one space and the back space and axially driven by a drive source;
a valve body that is seated or separated from the valve seat by driving the rod;
a communication means for communicating between the back space and the other of the primary pressure space and the secondary pressure space,
A valve, wherein a gap connecting the one space and the back space is formed between the rod and the valve housing, and the gap has a bent portion.
The valve according to claim 1, wherein the channel cross-sectional area of the bent portion is the smallest when the valve is closed.
2. The valve according to claim 1, wherein a pair of axially opposing surfaces forming said bent portion are axially separated from each other when said valve is closed.
The valve according to claim 3, wherein the side surface of the rod and the side surface of the valve housing are the pair of axially opposed surfaces.
The valve according to claim 3, wherein the pair of axially opposed surfaces are orthogonal to the axial direction.
The valve according to claim 1, wherein said bend has a crank shape.
The valve according to any one of claims 1 to 6, wherein the effective pressure-receiving area of said rod is equal to the effective pressure-receiving area of said valve.