Flow control valve and refrigeration cycle system

Abstract

The present invention provides a flow control valve and a refrigeration cycle system, which can fully suppress the sound of fluid passing through. The flow control valve (10A) comprises: a main valve core (2) (valve body), which has a connecting hole (25) (inlet) and an outflow portion (211) (outlet); and an auxiliary valve port (valve port), which is arranged inside the main valve core (2) and throttles the flow path of the fluid, and a rectifying component (6) is arranged between the auxiliary valve port (24) and the outflow portion (211) to rectify the flow by allowing the fluid to pass through, and the rectifying component (6) has a high resistance portion (61) with high flow path resistance on its center side and a low resistance portion (62) with low flow path resistance on the outside of the high resistance portion (61).

Description

Technical Field

[0001] The invention relates to a flow control valve and a refrigeration cycle system. Background Art

[0002] In the past, as a flow control valve provided in a refrigeration cycle system such as an air conditioner, for example, an expansion valve is disclosed in Patent Document 1, which includes: a valve body having an inlet and an outlet; and a valve port (valve seat) provided inside the valve body and throttling the flow path of the fluid, and is intended to suppress the sound of fluid passage (refrigerant passage sound) by allowing the fluid (refrigerant) to pass through a silencer component (a component composed of a mesh structure or a foamed material) provided between the valve port and the outlet.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: International Publication No. 2015 / 063854 Summary of the invention

[0006] Problems to be solved by the invention

[0007] However, in the conventional flow control valve disclosed in Patent Document 1, the fluid having increased flow velocity through the valve port is concentrated near the center of the silencer and passes through the silencer without decreasing its flow velocity, so that the fluid passage noise may not be sufficiently suppressed.

[0008] An object of the present invention is to provide a flow control valve and a refrigeration cycle system capable of sufficiently suppressing fluid passing noise.

[0009] Solutions to Solve Problems

[0010] The flow control valve of the present invention comprises: a valve body having an inlet and an outlet; and a valve port, which is arranged inside the valve body and throttles the flow path of the fluid, and the flow control valve is characterized in that a rectifying component is arranged between the valve port and the outlet, the rectifying component allows the fluid to pass through and rectify, and the rectifying component has a high resistance portion with high flow path resistance on its center side, and has a low resistance portion with low flow path resistance on the outside of the high resistance portion. In addition, in the present invention, it is preferred that the high resistance portion is set to a range that spans the center of the rectifying component even when the range is narrowed.

[0011] According to the present invention, although the fluid passing through the valve port first flows toward the vicinity of the center of the rectifying component, it is difficult for the high-resistance portion with high flow path resistance to pass through, and thus it also flows toward the low-resistance portion on the outside. After the flow of the fluid is dispersed from the vicinity of the center to the outside, the fluid passes through the roughly entire rectifying component, and the bubbles in the fluid are refined through the roughly entire rectifying component, thereby achieving a silencing effect and fully suppressing the sound of the fluid passing through.

[0012] In this case, it is preferable that the high resistance portion of the flow regulating member is provided in a range larger than the inner diameter of the valve port.

[0013] Furthermore, it is preferred that the high resistance portion of the flow regulating member has a higher filtration density than that of the low resistance portion.

[0014] Furthermore, it is preferable that the high resistance portion of the flow regulating member be formed to have a thickness greater than a thickness of the low resistance portion.

[0015] In addition, it is preferable that a surface of the high resistance portion of the rectifying member facing the valve port is formed to have an inclined surface whose thickness decreases from a center side toward an outer side.

[0016] In addition, it is preferable that a plate having small holes located in the high resistance portion and large holes located in the low resistance portion is provided on a side of the rectifying member that faces the valve port.

[0017] In addition, it is preferred that the valve seat portion constituting the valve port is provided with: a second valve port whose inner diameter increases from the valve port toward the outflow port; and a third valve port whose inner diameter further increases from the second valve port toward the outflow port, and the rectifying member is provided at the third valve port.

[0018] Preferably, the valve body further includes: a valve body that adjusts the opening area of ​​the valve port by moving forward and backward in the axial direction; and a drive unit that drives the valve body forward and backward.

[0019] The refrigeration cycle system of the present invention is characterized by comprising the above-mentioned flow control valve.

[0020] According to the present invention, as in the above-mentioned flow control valve, sufficient suppression of fluid passage noise can be achieved, and thus a silent refrigeration cycle system can be achieved.

[0021] Effects of the Invention

[0022] According to the flow control valve and the refrigeration cycle system of the present invention, it is possible to fully suppress the fluid passing noise. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a longitudinal sectional view showing a flow control valve according to a first embodiment of the present invention.

[0024] Figure 2 This is a longitudinal sectional view showing an enlarged view of a main part of the flow control valve.

[0025] Figure 3 This is a longitudinal sectional view showing an enlarged view of a main part of a flow control valve according to a second embodiment of the present invention.

[0026] Figure 4 This is a longitudinal sectional view showing an enlarged view of a main part of a flow control valve according to a third embodiment of the present invention.

[0027] Figure 5 This is a longitudinal sectional view showing an enlarged view of a main part of a flow control valve according to a fourth embodiment of the present invention.

[0028] Figure 6 This is a diagram showing an example of the refrigeration cycle system of the present invention.

[0029] Figure 7 It is a longitudinal sectional view showing a flow control valve according to another embodiment of the present invention.

[0030] Figure 8 This is a longitudinal sectional view showing an enlarged view of a main part of the flow control valve.

[0031] In the figure:

[0032] 10, 10A~10E—flow control valve; 25—connecting hole (inflow port); 33—inflow hole (inflow port); 211—outflow portion (outflow port); 2—main valve core (valve body); 20—valve core (valve body) for solenoid valve; 24—auxiliary valve port (valve port); 26—throttling hole (valve port); 6—rectifying component; 61—high resistance portion; 61a—conical portion; 62—low resistance portion; 7—plate material; 7a—small hole; 7b—large hole; 21—main valve portion (valve seat portion); 5—expanded diameter portion (second valve port); 21a—first step portion (third valve port); L—axis line; 3—auxiliary valve core (valve core); 90—refrigeration cycle system. DETAILED DESCRIPTION

[0033] based on Figure 1 and Figure 2 The flow control valve of the first embodiment of the present invention is described. The flow control valve 10A of this embodiment is a two-stage electric valve, which includes a valve housing 1, a main valve port 14 formed in the valve housing 1, a main valve core 2 (valve body) capable of opening and closing the main valve port 14, an auxiliary valve port 24 (valve port) in the main valve core 2, an auxiliary valve core 3 (valve core) capable of opening and closing the auxiliary valve port 24, and a stepping motor 4 (driving unit). In addition, the concept of "up and down" in the following description is the same as Figure 1 The upper and lower parts in the accompanying drawings correspond to each other.

[0034] The valve housing 1 has a cylindrical valve housing member 1A and a support member 1B fixed to the upper end opening of the valve housing member 1A. The valve housing member 1A has a cylindrical main valve chamber 1C formed therein, and a primary joint pipe 11 is installed on the valve housing member 1A, which is connected to the main valve chamber 1C from the side and allows a fluid such as a refrigerant to flow in, and a secondary joint pipe 12 is installed on the valve housing member 1A, which is connected to the main valve chamber 1C from the bottom side and allows a fluid to flow out. The support member 1B is a resin molded product and is welded and fixed to the valve housing member 1A by a metal fixing portion 15.

[0035] The main valve port 14 is formed in a circular cross-sectional shape from a main valve seat 13 provided at a position where the main valve chamber 1C and the secondary joint pipe 12 communicate with each other in the valve housing member 1A toward the secondary joint pipe 12 side.

[0036] The main valve core 2 is a part for opening and closing the main valve port 14, and has a valve core main part 2A, a stopper part 2B, and an auxiliary valve seat 2C. The valve core main part 2A has a main valve part 21 (valve seat part) that is seated or unseated relative to the main valve seat 13. The valve core main part 2A has a cylindrical part 22 with the axis L direction as the axial direction, an auxiliary valve chamber 23 formed inside the cylindrical part 22 and through which fluid flows, and an auxiliary valve port 24 that passes through the auxiliary valve seat 2C along the axis L direction. The cylindrical part 22 has a plurality of communication holes 25 (inflow ports) formed on its circumferential surface, and a through hole 26 formed on its inner circumferential surface along the axis L direction. The auxiliary valve chamber 23 is connected to the main valve chamber 1C through the communication holes 25. The stopper part 2B is formed in an annular shape and fixed to the upper end of the valve core main part 2A, and a rotor shaft 46 is inserted inside it to limit the rising position of the auxiliary valve core 3 provided at the lower end of the rotor shaft 46. The auxiliary valve seat 2C is arranged on the secondary joint pipe 12 side of the auxiliary valve chamber 23. In addition, the stopper 2B is formed with a step shape from its upper end to the lower side, and a main valve spring 27 is arranged between the step shape and the top surface of the support member 1B. The main valve spring 27 applies force to the main valve seat 13 direction (closing direction) through the main valve core 2.

[0037] The auxiliary valve port 24 is formed in a circular cross-section from the auxiliary valve seat 2C to the secondary joint pipe 12 side in the main valve core 2. In addition, the inner side of the cylindrical portion 22 is provided with: a cylindrical expansion portion 5 (second valve port) that is radially expanded compared to the auxiliary valve port 24 on the downstream side of the auxiliary valve port 24, a cylindrical first step portion 21a (third valve port) that is radially expanded compared to the expansion portion 5 on the downstream side of the expansion portion 5, and a cylindrical second step portion 21b that is radially expanded compared to the first step portion 21a. In addition, a cylindrical rectifying component 6 formed of a porous material or a metal mesh, etc., through which a fluid passes, is embedded in the first step portion 21a, and an annular retaining portion 21c is embedded in the second step portion 21b to retain the outer periphery of the lower end of the rectifying component 6, and an outflow portion 211 (outflow port) of the fluid is formed on the inner peripheral surface of the retaining portion 21c.

[0038] The auxiliary valve core 3 is a portion that changes the opening of the auxiliary valve port 24 formed on the main valve core 2. The auxiliary valve core 3 is composed of a cylindrical auxiliary valve base 3A, an auxiliary valve portion 3B protruding downward from the auxiliary valve base 3A, a thrust washer 3C provided on the upper side of the auxiliary valve base 3A, and an auxiliary valve spring (not shown) provided inside the auxiliary valve base 3A. The auxiliary valve base 3A is inserted into the insertion hole 26 of the main valve core 2, and is supported to be able to move forward and backward freely in the up and down directions along the axis L direction and to rotate freely around the axis L. The auxiliary valve portion 3B has a rod portion 31 and a needle portion 32 at the lower end of the rod portion 31. The needle portion 32 forms a throttling portion 33 for allowing fluid to pass through the gap with the auxiliary valve port 24. And, as Figure 2 As shown, the needle 32 has a flow control portion 32a which is inserted into the auxiliary valve port 24 and whose diameter gradually decreases toward the outlet side of the auxiliary valve port 24. The thrust washer 3C can abut against the upper surface of the auxiliary valve base 3A and the lower surface of the stopper 2B, and the friction between the abutting surfaces becomes extremely small. In addition, an insertion hole is provided in the upper part of the auxiliary valve base 3A, and the rotor shaft 46 is inserted therethrough. An auxiliary valve spring is provided between a flange portion (not shown) formed at the lower end of the rotor shaft 46 and the upper end of the auxiliary valve portion 3B joined to the bottom of the auxiliary valve base 3A. By the auxiliary valve spring, the auxiliary valve core 3 is urged toward the auxiliary valve seat 2C direction (closing direction) relative to the rotor shaft 46 (magnetic rotor 44). In addition, the auxiliary valve base 3A may be formed integrally with the rotor shaft 46 and the auxiliary valve portion 3B. In this case, the auxiliary valve base 3A may be formed into a solid shape and the auxiliary valve spring may be omitted.

[0039] The stepper motor 4 is a member that moves the sub-valve core 3 forward and backward in the direction of the axis L, and also moves the main valve core 2 forward and backward in the direction of the axis L via the sub-valve core 3. The stepper motor 4 includes a screw feed mechanism 42 that moves the sub-valve core 3 forward and backward by the rotation of a magnetic rotor 44, and a stopper mechanism 43 that limits the rotation of the magnetic rotor 44. The stepper motor 4 includes a magnetic rotor 44 whose outer periphery is magnetized to multiple poles, a stator coil 45 disposed on the outer periphery of a housing 18, and a rotor shaft 46 fixed to the magnetic rotor 44. The rotor shaft 46 is fixed to the magnetic rotor 44 via a fixing member 46a, and extends in the direction of the axis L, and its upper end is inserted into a guide 47 of the stopper mechanism 43. An external thread portion 46b is integrally formed at the middle portion of the rotor shaft 46, and the external thread portion 46b is screwed into the internal thread portion 17 of the support member 1B, thereby constituting the screw feed mechanism 42. When the magnetic rotor 44 rotates, the external thread portion 46 b of the rotor shaft 46 is guided by the internal thread portion 17 , whereby the magnetic rotor 44 and the rotor shaft 46 move forward and backward in the axis L direction, and the sub valve element 3 also rises or falls along the axis L accordingly.

[0040] The stopper mechanism 43 includes a cylindrical guide 47 hanging from the top of the housing 18, a spiral guide wire body 48 fixed to the outer periphery of the guide 47, and a movable slider 49 that is guided by the guide wire body 48 and can rotate and move up and down. The movable slider 49 is provided with a claw 49a protruding radially outward, and the magnetic rotor 44 is provided with an extension 44a extending upward and abutting against the claw 49a. When the magnetic rotor 44 rotates, the extension 44a presses the claw 49a, thereby the movable slider 49 rotates and moves up and down following the guide wire body 48. The guide wire body 48 is formed with an upper end stopper 48a that defines the uppermost position of the magnetic rotor 44 and a lower end stopper 48b that defines the lowermost position of the magnetic rotor 44. The movable slider 49 comes into contact with the upper end stopper 48 a and the lower end stopper 48 b to stop the rotation of the movable slider 49 . This restricts the rotation of the magnetic rotor 44 and stops the ascending or descending of the sub-valve element 3 .

[0041] In this embodiment, if Figure 2 As shown in FIG. 1 , the rectifying member 6 includes a high resistance portion 61 having a high flow resistance on the center side thereof and a low resistance portion 62 having a low flow resistance on the outside of the high resistance portion 61. Furthermore, the high resistance portion 61 of the rectifying member 6 is set to a range spanning the center of the rectifying member 6. In addition, the high resistance portion 61 is set to a range larger than the inner diameter of the auxiliary valve port 24, and further, the high resistance portion 61 of the rectifying member 6 has a higher filtration density than the low resistance portion 62. Specifically, the filtration density of the high resistance portion 61 is set to be 1.2 times higher than the filtration density of the low resistance portion 62.

[0042] The flow control valve 10A constructed as described above operates as follows. First, assume that the flow control valve 10A is in a closed valve state in which the main valve portion 21 of the main valve core 2 is seated on the main valve seat 13 and the main valve port 14 is closed. Furthermore, when the sub-valve core 3 of the flow control valve 10A is located at the position closest to the sub-valve port 24, the sub-valve core 3 is not seated on the sub-valve seat 2C, and a flow path is formed through the gap between the outer peripheral surface of the needle portion 32 of the sub-valve core 3 and the inner peripheral surface of the sub-valve port 24. Therefore, the fluid flowing from the primary joint pipe 11 into the main valve chamber 1C passes through the communication hole 25 of the valve core main portion 2A and flows into the sub-valve chamber 23. The fluid flowing into the sub-valve chamber 23 flows to the lower side of the main valve portion 21 through the gap between the outer peripheral surface of the needle portion 32 of the sub-valve core 3 and the sub-valve port 24, and flows out from the main valve port 14 toward the secondary joint pipe 12. That is, even if the valve opening is zero (the sub-valve portion 3B is at the lowest position), a small flow rate is generated.

[0043] Next, the stepper motor 4 is driven to rotate the magnetic rotor 44 to raise the auxiliary valve core 3, thereby the needle 32 of the auxiliary valve portion 3B of the auxiliary valve core 3 rises inside the auxiliary valve port 24, and the flow path based on the gap between the needle 32 of the auxiliary valve portion 3B and the auxiliary valve port 24 is expanded, and the flow rate gradually increases. At this time, the main valve portion 21 of the main valve core 2 remains seated on the main valve seat 13, so the increase in flow rate is small. In this way, the control area for changing the opening of the auxiliary valve core 3 in the state of closing the main valve core 2 is a small flow control area. Next, when the auxiliary valve core 3 is further raised, the thrust washer 3C abuts against the limiter 2B, the main valve core 2 is pulled up by the auxiliary valve core 3, and the main valve portion 21 is unseated from the main valve seat 13. In this way, the control area for changing the opening of the main valve port 14 by unseating the main valve core 2 is a large flow control area, and the change of flow in this large flow control area is large. In the fully open state where the main valve core 2 is farthest from the main valve port 14, the flow rate becomes the largest.

[0044] According to the above embodiment, Figure 2 As shown, although the fluid passing through the auxiliary valve port 24 first flows toward the vicinity of the center of the rectifying component 6, it is difficult to pass through the high resistance portion 61 with high flow resistance, and therefore it also flows toward the low resistance portion 62 on the outside. After the flow of the fluid is dispersed from the vicinity of the center to the outside, the fluid passes through the roughly entire rectifying component 6, and the bubbles in the fluid are refined through the roughly entire rectifying component 6, thereby achieving a silencing effect particularly in the small flow control area, and being able to fully suppress the sound of the fluid passing through.

[0045] In the present embodiment, the high resistance portion 61 of the rectifying member 6 is set to a range larger than the inner diameter of the auxiliary valve port 24. Due to such a structure, more fluid with a fast flow rate flows toward the high resistance portion 61, and more fluid also flows toward the outer low resistance portion 62, which can further obtain the silencing effect based on the rectifying member 6, and can achieve more sufficient suppression of the fluid passing sound.

[0046] In this embodiment, the high resistance portion 61 of the rectifying member 6 has a higher filtration density than the low resistance portion 62. With such a structure, the rectifying member 6 can be easily configured by joining members having different filtration densities.

[0047] Next, based on Figure 3The flow control valve of the second embodiment of the present invention is described. The flow control valve 10B of this embodiment is a two-stage electric valve having a valve housing 1, a main valve port 14 formed in the valve housing 1, a main valve core 2 (valve body) capable of opening and closing the main valve port 14, an auxiliary valve port 24 (valve port) in the main valve core 2, an auxiliary valve core 3 (valve core) capable of opening and closing the auxiliary valve port 24, and a stepping motor 4 (driving unit), similarly to the flow control valve 10A of the first embodiment. In the flow control valve 10B of this embodiment, a part of the structure of the main valve core 2 is different from that of the flow control valve 10A of the first embodiment. The differences are described in detail below.

[0048] In the flow control valve 10B of the present embodiment, the high resistance portion 61 and the low resistance portion 62 of the rectifying member 6 provided in the main valve body 2 have the same filtration density, and the high resistance portion 61 is formed to be thicker than the low resistance portion 62, which is different from the flow control valve 10A of the first embodiment. In addition, specifically, in the flow control valve 10B of the present embodiment, in the rectifying member 6, the thickness of the high resistance portion 61 is set to be 1.2 times or more of the thickness of the low resistance portion 62.

[0049] In the flow control valve 10B of the present embodiment described above, the difference in flow resistance is caused by the difference in thickness between the high resistance portion 61 and the low resistance portion 62 in the rectifying member 6. Therefore, according to the flow control valve 10B of the present embodiment, it is possible to achieve substantially the same effects as the flow control valve 10A of the first embodiment.

[0050] Next, based on Figure 4 The flow control valve of the third embodiment of the present invention is described. The flow control valve 10C of this embodiment is a two-stage electric valve having a valve housing 1, a main valve port 14 formed in the valve housing 1, a main valve core 2 (valve body) capable of opening and closing the main valve port 14, an auxiliary valve port 24 (valve port) in the main valve core 2, an auxiliary valve core 3 (valve core) capable of opening and closing the auxiliary valve port 24, and a stepping motor 4 (driving unit), similarly to the flow control valve 10A of the first embodiment. In the flow control valve 10C of this embodiment, a part of the structure of the main valve core 2 is different from that of the flow control valve 10A of the first embodiment. The differences are described in detail below.

[0051] In the flow control valve 10C of the present embodiment, the high resistance portion 61 and the low resistance portion 62 of the rectifying member 6 provided in the main valve body 2 have the same filtration density, and the high resistance portion 61 is formed with a conical portion 61a having an inclined surface whose thickness decreases from the center side toward the outside on the surface facing the auxiliary valve port 24, which is different from the flow control valve 10A of the first embodiment. In addition, specifically, in the flow control valve 10C of the present embodiment, in the rectifying member 6, the average thickness of the high resistance portion 61 including the conical portion 61a is set to be 1.2 times or more of the thickness of the low resistance portion 62.

[0052] In the flow control valve 10C of the present embodiment described above, the flow resistance is different due to the difference in shape between the high resistance portion 61 and the low resistance portion 62 in the rectifying member 6. Therefore, according to the flow control valve 10C of the present embodiment, it is possible to achieve substantially the same effects as the flow control valve 10A of the first embodiment.

[0053] Next, based on Figure 5 A flow control valve according to a fourth embodiment of the present invention is described. The flow control valve 10D of this embodiment is a two-stage electric valve having a valve housing 1, a main valve port 14 formed in the valve housing 1, a main valve core 2 (valve body) capable of opening and closing the main valve port 14, an auxiliary valve port 24 (valve port) in the main valve core 2, an auxiliary valve core 3 (valve core) capable of opening and closing the auxiliary valve port 24, and a stepping motor 4 (driving unit), similarly to the flow control valve 10A of the first embodiment. In the flow control valve 10D of this embodiment, a part of the structure of the main valve core 2 is different from that of the flow control valve 10A of the first embodiment. The differences are described in detail below.

[0054] In the flow control valve 10D of the present embodiment, the high resistance portion 61 and the low resistance portion 62 of the rectifying member 6 provided in the main valve body 2 have the same filtration density, and a plate 7 having small holes 7a, ... located in the high resistance portion 61 and large holes 7b, ... located in the low resistance portion 62 is provided on the side of the rectifying member 6 facing the auxiliary valve port 24, which is different from the flow control valve 10A of the first embodiment. In addition, specifically, the small holes 7a, ... and the large holes 7b, ... in the plate 7 of the flow control valve 10D of the present embodiment are provided at equal intervals on the circumference centered on the axis L in a plan view. In addition, in the flow control valve 10D of the present embodiment, the total opening area of ​​the large holes 7b, ... is set to be 1.2 times or more of the total opening area of ​​the small holes 7a, ... of the plate 7 in the rectifying member 6. In addition, the range (radius) of the high resistance portion 61 in the present embodiment is the range on the axis L side connecting the axis L and the inner diameter of the large hole 7b. In addition, the number, size, shape, and arrangement of the small holes 7a, ... and the large holes 7b, ... may be varied within the scope of exerting the performance of the present invention. That is, for example, only one small hole 7a may be provided at the center of the rectifying member 6, and one or more large holes 7b may be provided in a continuous annular shape so as to surround the small hole 7a.

[0055] In the flow control valve 10D of the present embodiment described above, the plate 7 having the small holes 7a, ... and the large holes 7b, ... is provided as an additional component on the rectifying component 6, thereby generating a difference in flow path resistance. Therefore, according to the flow control valve 10D of the present embodiment, it is possible to achieve substantially the same effects as the flow control valve 10A of the first embodiment.

[0056] Next, based on Figure 6 The refrigeration cycle system of the present invention will be described. Figure 6 This is a diagram showing an example of the refrigeration cycle system of the present invention.

[0057] Should Figure 6 The refrigeration cycle system 90 shown is used for air conditioners such as household air conditioners. The flow control valve 10 (10A, 10B, 10C, 10D) of the above embodiment is arranged between the first indoor heat exchanger 91 (operating as a cooler during dehumidification) and the second indoor heat exchanger 92 (operating as a heater during dehumidification) of the air conditioner. The flow control valve 10, the compressor 95, the four-way valve 96, the outdoor heat exchanger 94 and the electronic expansion valve 93 together constitute a heat pump type refrigeration cycle. The first indoor heat exchanger 91, the second indoor heat exchanger 92 and the two-stage electric valve 10 are arranged indoors, and the compressor 95, the four-way valve 96, the outdoor heat exchanger 94 and the electronic expansion valve 93 are arranged outdoors to constitute a cooling and heating device.

[0058] The flow control valve 10 as a dehumidification valve is set to a fully open state through the main valve core 2 during cooling or heating other than dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are set as one indoor heat exchanger. Moreover, the integrated indoor heat exchanger and outdoor heat exchanger 94 selectively function as an "evaporator" and a "condenser". That is, the electronic expansion valve 93 is set between the evaporator and the condenser.

[0059] According to the refrigeration cycle system 90, since the flow control valve 10 of the above embodiment is provided on the fluid path, it is possible to suppress the fluid passage sound particularly in the small flow control area, thereby forming a silent refrigeration cycle system.

[0060] Next, based on Figure 7 and Figure 8 A flow control valve according to another embodiment of the present invention is described. The flow control valve 10E of this embodiment is an electromagnetic valve including a valve housing 111, a valve port 140 formed in the valve housing 111, an electromagnetic valve valve core 20 (valve body) capable of opening and closing the valve port 140, and an electromagnetic solenoid device 40 (driving unit). Figure 7 and Figure 8 All of them are diagrams showing the solenoid valve body 20 in a fully closed state.

[0061] The flow control valve 10E of the present embodiment has the following structure: a disc-shaped porous filter component 25 is embedded in a cylindrical recess formed at the lower end of the solenoid valve core 20, a cylindrical throttling component 27 having a throttling hole 26 (valve port) at the center is embedded downstream thereof, and the rectifying component 6 used in the flow control valve 10A of the first embodiment is embedded downstream thereof.

[0062] The flow control valve 10E of this embodiment is a structure that allows the electromagnetic valve valve core 20 to move up and down along the axis L direction through the electromagnetic solenoid device 40, and can control the opening of the valve port 140 formed in the valve housing 111 to be fully open or fully closed (throttling state). When the electromagnetic valve valve core 20 is fully open, the flow control valve 10E becomes a valve with a large flow control area, and the fluid flowing in from the primary joint pipe 11 flows into the secondary joint pipe 12 via the valve chamber 11C and the valve port 140. On the other hand, if Figure 8 As shown, when the solenoid valve core 20 is in a fully closed state, the fluid flowing in from the primary joint pipe 11 flows through the cylindrical filter member 32 from the inflow hole 33 (inflow port) through the filter member 25 into the throttle hole 26, and after passing through the rectifying member 6, flows into the secondary joint pipe 12 from the lower end 20a (outflow port) of the recess. In addition, the rectifying member 6 may use any rectifying member 6 used in the flow control valves 10B to 10D of the second to fourth embodiments.

[0063] In the flow control valve 10E of the present embodiment, for example, compared with the case where a filter member with uniform filtration density is provided instead of the rectifying component 6, the fluid passes through substantially the entire rectifying component 6, and the bubbles in the fluid are refined through substantially the entire rectifying component 6, thereby being able to obtain a silencing effect particularly in a small flow control area, and being able to fully suppress the sound of the fluid passing through.

[0064] The above describes in detail the methods for implementing the present invention based on the first to fourth embodiments and other embodiments with reference to the drawings, but the specific structure is not limited to these embodiments, and design changes that do not depart from the gist of the present invention are included in the present invention.

[0065] For example, in the first to fourth embodiments, the range of the high resistance portion 61 is made larger than the inner diameter of the auxiliary valve port 24, but it is not limited to this, and it can also be smaller than the inner diameter of the auxiliary valve port 24. In addition, as for the high resistance portion 61 of the rectifying member 6 in the second and third embodiments, the high resistance portion 61 can also have a higher filtration density than the low resistance portion 62 as in the first embodiment. In addition, in the first to fourth embodiments, the rectifying member 6 is provided in the lower end portion of the main valve portion 21, but it is not limited to this, for example, the rectifying member 6 can also be provided in the main valve port 14 of the valve housing 1 or in the secondary joint pipe 12. In this case, the silencing effect in the large flow control area can also be obtained.

[0066] Furthermore, in the above-described example of the present invention, the flow control valve 10 is used for a general air conditioner, but the present invention is not limited thereto and may be used for a multi-split air conditioner, a refrigerator, etc. for a building.

Claims

1. A flow control valve, comprising: a valve housing; a main valve port disposed in the valve housing; a valve body capable of opening and closing the main valve port and having an inlet and an outlet; and a valve port disposed on an axis inside the valve body and throttling a flow path of a fluid, The flow control valve is characterized in that The valve body comprises: a cylindrical second valve port, which is arranged on the outflow side of the valve port and has a larger inner diameter than the valve port; and a cylindrical third valve port, which is arranged on the outflow side of the second valve port and has a larger inner diameter than the second valve port. The third valve port is provided with a rectifying component, which rectifyingly allows the fluid to pass through. The rectifying member includes a high resistance portion with high flow resistance arranged opposite to the valve port at at least the end portion on the valve port side of the center side and on the axis core, and includes a low resistance portion with low flow resistance on the outside of the high resistance portion. The area of ​​the flow path through the rectifying member is larger than the area of ​​the inner diameter of the end portion on the outflow port side of the second valve port. The high resistance portion is set to a range larger than the inner diameter of the valve port. The fluid passing through the valve port directly contacts the high resistance portion on the center side, disperses from the high resistance portion to the low resistance portion on the outside, and passes through substantially the entirety of the high resistance portion and the low resistance portion of the rectifying member. A valve element having a needle portion at a front end and being movable in an axial direction is inserted into the valve port, and a throttle portion is formed by a gap between the needle portion and the valve port.

2. The flow control valve according to claim 1, It is characterized in that The high resistance portion of the rectifying member is provided to have a range larger than the inner diameter of the valve port.

3. The flow control valve according to claim 1 or 2, It is characterized in that The high resistance portion of the rectification member has a higher filtration density than the low resistance portion.

4. The flow control valve according to claim 1 or 2, It is characterized in that The high resistance portion of the flow regulating member is formed to have a thickness greater than a thickness of the low resistance portion.

5. The flow control valve according to claim 1 or 2, It is characterized in that The surface of the high resistance portion of the rectifying member facing the valve port is formed to have an inclined surface whose thickness decreases from the center side toward the outside.

6. The flow control valve according to claim 1 or 2, It is characterized in that A plate is provided on one side of the rectifying component opposite to the valve port, and the plate has a small hole located in the high resistance portion and a large hole located in the low resistance portion.

7. The flow control valve according to claim 1 or 2, It is characterized in that Also available: The valve core adjusts the opening area of ​​the valve port by moving forward and backward in the axial direction; and A driving unit drives the valve core to move forward and backward.

8. A refrigeration cycle system, It is characterized in that A flow control valve according to any one of claims 1 to 7 is provided.

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