CN113883284A - Electric valve and refrigeration cycle system - Google Patents
Electric valve and refrigeration cycle system Download PDFInfo
- Publication number
- CN113883284A CN113883284A CN202110686206.4A CN202110686206A CN113883284A CN 113883284 A CN113883284 A CN 113883284A CN 202110686206 A CN202110686206 A CN 202110686206A CN 113883284 A CN113883284 A CN 113883284A
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- Prior art keywords
- valve
- sub
- port
- main
- main valve
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 13
- 238000004891 communication Methods 0.000 claims abstract description 21
- 238000005192 partition Methods 0.000 claims description 31
- 230000002093 peripheral effect Effects 0.000 claims description 27
- 238000007791 dehumidification Methods 0.000 claims description 7
- 238000013459 approach Methods 0.000 claims description 6
- 230000003247 decreasing effect Effects 0.000 claims 1
- 239000012530 fluid Substances 0.000 abstract description 40
- 238000011144 upstream manufacturing Methods 0.000 abstract description 6
- 230000004048 modification Effects 0.000 description 15
- 238000012986 modification Methods 0.000 description 15
- 230000001105 regulatory effect Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 5
- 238000003466 welding Methods 0.000 description 3
- 229910001369 Brass Inorganic materials 0.000 description 2
- 239000010951 brass Substances 0.000 description 2
- 230000001687 destabilization Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 230000002123 temporal effect Effects 0.000 description 2
- 238000005219 brazing Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
- F16K1/38—Valve members of conical shape
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The invention provides an electrically operated valve capable of reducing noise and a refrigeration cycle system provided with the electrically operated valve. The motor-operated valve (1) is provided with: a valve housing (2); a main valve element (4) that changes the opening of a main valve port (23a) of a main valve chamber (2R) provided in a valve housing (2); an auxiliary valve body (5) that changes the opening degree of an auxiliary valve port (41b) provided in an auxiliary valve chamber (4R) of the main valve body (4); and a drive unit (6) that drives the sub-valve body (5) to advance and retract in the Z direction, wherein the sub-valve port (41a) has an upper end (412A) that is an opening end and a cylindrical inner circumferential surface (413) that is a small diameter portion. Thus, a rectifying portion can be formed at a position upstream of the minimum throttling portion, and when the fluid flows into the sub-valve chamber (4R) through the first port (21) and the communication hole (421), even if the flow rate becomes unstable, the noise can be reduced by rectifying the fluid.
Description
Technical Field
The present invention relates to an electric valve and a refrigeration cycle system.
Background
Conventionally, there has been proposed an electrically operated valve in which the opening degree of a main valve port can be changed by a main valve body and the opening degree of a sub valve port provided in the main valve body can be changed by a sub valve body (for example, see patent document 1). In the motor-operated valve described in patent document 1, the main valve element includes a main valve portion, a holding portion including a cylindrical needle guide hole, and a sub valve seat, and a portion of the lower side of the needle guide hole forms a sub valve chamber. Further, by forming the through hole in the side surface of the holding portion, the main valve chamber, the sub valve port, and the main valve port are communicated when the sub valve body opens the sub valve port.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open No. 2020 and 034141
Disclosure of Invention
Problems to be solved by the invention
In the motor-operated valve described in patent document 1, a joint is connected to a cylindrical valve housing having a main valve chamber on a side surface and on one end side in an axial direction. When the side joint is the primary side, if the sub-valve port is opened as described above, the fluid flowing in from the joint passes through the communication hole in the side surface of the holding portion, and then flows out from the joint on one end side through the sub-valve port and the main valve port. In this case, if the main valve element is rotatable, the positional relationship between the joint on the side surface and the pilot hole changes, and the flow rate of the fluid passing through the sub-port may change with time. Further, even if the main valve element does not rotate, the flow rate of the fluid passing through the through hole in the side surface of the holding portion differs between a position close to the joint in the side surface and a position far from the joint in the side surface, and the flow rate of the fluid passing through the sub port may become uneven depending on the position. As described above, the flow rate of the fluid passing through the sub-port may become unstable temporally or spatially (hereinafter, temporal change in the flow rate and positional unevenness are collectively referred to simply as "destabilization"), and such destabilization may become a factor of noise.
The invention aims to provide an electric valve capable of reducing noise and a refrigeration cycle system with the electric valve.
Means for solving the problems
The motor-operated valve of the present invention comprises: a valve housing; a main valve body that changes an opening degree of a main valve port of a main valve chamber provided in the valve housing; an auxiliary valve body that changes an opening degree of an auxiliary valve port provided in an auxiliary valve chamber of the main valve body; and a driving portion that drives the sub-valve body to advance and retreat in an axial direction, wherein the valve housing has a first port that opens in a direction intersecting the axial direction and a second port that communicates with the main valve port and opens in the axial direction, the main valve body has a partition wall portion that extends in the direction intersecting the axial direction and that allows the sub-valve body to approach or separate from the main valve body, and a cylindrical portion that extends from the partition wall portion toward a side opposite to the main valve port and that forms the sub-valve chamber by the partition wall portion and the cylindrical portion, the cylindrical portion has at least one communication hole that communicates between the inside and the outside thereof, the sub-valve port has an opening end portion that is a through hole formed in the partition wall portion and an end portion on a side opposite to the main valve port, and a small diameter portion that is located on a side of the main valve port side with respect to the opening end portion, and is formed to have a diameter smaller than that of the opening end portion.
According to the present invention described above, since the sub-valve port has the opening end portion and the small diameter portion, the space between the sub-valve body and the opening end portion can be made larger than the space between the sub-valve body and the small diameter portion. When the fluid flows from the sub valve chamber to the main valve port side through the sub valve port, the fluid passes through a space between the sub valve body and the opening end portion and then a space between the sub valve body and the small diameter portion. In this case, the space between the sub-valve body and the small diameter portion serves as a throttle portion to determine a substantial valve opening degree (opening area), and a larger space is provided on the upstream side thereof, that is, the fluid can be temporarily rectified at a position on the upstream side of the throttle portion. Therefore, when the fluid flows into the sub-valve chamber through the first port and the communication hole of the valve housing, even when the flow rate becomes unstable, the noise can be reduced by rectifying the fluid.
In this case, in the motor-operated valve according to the present invention, it is preferable that the sub-valve port has a tapered portion whose inner diameter decreases toward the main-valve port between the opening end portion and the small-diameter portion. With this configuration, the fluid can easily flow along the tapered portion, and the occurrence of disturbance in the flow of the fluid can be suppressed.
In the motor-operated valve according to the present invention, it is preferable that the sub-valve opening has a stepped portion between the opening end portion and the small diameter portion, and the stepped portion is formed by a cylindrical inner peripheral surface extending in the axial direction and an annular portion extending radially inward from an end portion of the cylindrical inner peripheral surface on the main valve opening side. According to such a configuration, the volume of the space between the cylindrical portion and the sub-valve body can be easily ensured, and the flow of fluid can be easily rectified.
In the motor-operated valve according to the present invention, it is preferable that the small diameter portion is provided on the main valve port side of the axial center portion of the partition wall portion, and is a portion having the smallest inner diameter in the sub valve port. According to such a configuration, the volume can be increased by securing the axial dimension of the space for rectifying the fluid, and the fluid can be easily rectified.
The refrigeration cycle system of the present invention includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidification valve provided in the indoor heat exchanger, and is characterized in that the electric valve described in any one of the above is used as the dehumidification valve. According to the present invention described above, noise can be reduced in the motor-operated valve.
The effects of the invention are as follows.
According to the motor-operated valve and the refrigeration cycle system of the present invention, noise can be reduced.
Drawings
Fig. 1 is a cross-sectional view showing an electrically operated valve according to an embodiment of the present invention.
Fig. 2 is an enlarged cross-sectional view of a main portion of the motor-operated valve when the opening degree of the sub-valve port is minimized.
Fig. 3 is an enlarged cross-sectional view of a main portion of the motor-operated valve when the opening degree of the sub-valve port is intermediate.
Fig. 4 is an enlarged cross-sectional view of a main portion of the motor-operated valve when the opening degree of the sub-valve port is maximized.
Fig. 5 is a cross-sectional view showing a cross section passing through the cylindrical portion in the motor-operated valve.
Fig. 6 is a system diagram showing an example of a refrigeration cycle system provided with the motor-operated valve.
Fig. 7 is an enlarged cross-sectional view showing a main portion of the motor-operated valve according to the first modification when the opening degree of the sub-port is minimum.
Fig. 8 is an enlarged cross-sectional view showing a main portion of the motor-operated valve according to the first modification when the opening degree of the sub-port is maximum.
Fig. 9 is an enlarged cross-sectional view showing a main portion of the motor-operated valve according to the second modification when the opening degree of the sub-port is minimum.
Fig. 10 is an enlarged cross-sectional view of a main portion of a motor-operated valve according to a second modification example, the main portion being a valve body having an intermediate opening degree of a sub-port.
Fig. 11 is an enlarged cross-sectional view showing a main portion of the motor-operated valve according to the second modification when the opening degree of the sub-port is maximum.
Fig. 12 is an enlarged cross-sectional view showing a main portion of the electrically operated valve according to the above embodiment, the main portion being a case where the valve opening degree of the sub-port is set to 0.
Fig. 13 is an enlarged cross-sectional view showing a main portion of the electrically operated valve according to the first modification, the main portion being a case where the valve opening degree of the sub-port is 0.
Fig. 14 is an enlarged cross-sectional view showing a main portion of the electrically operated valve according to the second modification described above, the main portion being a portion in which the valve opening degree of the sub port is 0.
In the figure:
1-electric valve, 2-valve housing, 21-first port, 22-second port, 23 a-main valve port, 2R-main valve chamber, 4-main valve core, 41-partition wall portion, 41a, 41 b-sub valve port, 412-taper portion, 412A-upper end portion (opening end portion), 413-cylindrical inner peripheral surface (small diameter portion), 414-cylindrical inner peripheral surface, 415-annular portion, 416-step portion, 42-cylindrical portion, 421-communication hole, 4R-sub valve chamber, 5-sub valve core, 6-driving portion, 91-first indoor heat exchanger, 92-second indoor heat exchanger, 93-electronic expansion valve, 94-outdoor heat exchanger.
Detailed Description
Embodiments of the present invention will be described with reference to the accompanying drawings. The motor-operated valve 1 of the present embodiment is used in a refrigeration cycle of an air conditioner such as a cabinet air conditioner or a room air conditioner, and includes, as shown in fig. 1, a valve housing 2, a guide member 3, a main valve element 4, a sub valve element 5, and a drive unit 6. The main valve element 4 and the sub valve element 5 are moved in a predetermined axial direction, hereinafter, the axial direction is referred to as a Z direction, two directions orthogonal to the Z direction are referred to as an X direction and a Y direction, and the top and bottom in the Z direction are referred to as fig. 1.
The valve housing 2 is formed in a substantially cylindrical shape, for example, of brass, stainless steel, or the like, and has a main valve chamber 2R inside thereof. The valve housing 2 has a first port 21 opened to one side in the X direction and a second port 22 opened to the lower side in the Z direction on its side surface. The first port 21 is connected to a first joint pipe 11 extending in the X direction, the second port 22 is connected to a second joint pipe 12 extending in the Z direction, and the first joint pipe 11 and the second joint pipe 12 communicate with the main valve chamber 2R. The first joint pipe 11 and the second joint pipe 12 may be fixed to the valve housing 2 by brazing or the like, for example.
A cylindrical main valve seat 23 projecting toward the main valve chamber 2R (toward the upper side) in the Z direction is formed at the lower end portion of the valve housing 2, the inside of the main valve seat 23 becomes a main valve port 23a, and the main valve port 23a communicates with the second port 22. That is, the second joint pipe 12 is communicated with the main valve chamber 2R through the main valve port 23 a. In the present embodiment, the electric valve 1 has the first port 21 as the primary side and the second port 22 as the secondary side, and is configured to allow the fluid (refrigerant) flowing into the main valve chamber 2R from the first joint pipe 11 to flow out from the second joint pipe 12, but the electric valve 1 may be incorporated in a cycle in which the fluid can flow in both directions.
The guide member 3 is mounted to an opening portion at the upper end of the valve housing 2, and includes: a press-fitting portion 31 that is press-fitted into the inner peripheral surface of the valve housing 2; a substantially cylindrical guide portion 32 located inside the press-fitting portion 31; a bracket part 33 extending above the guide part 32; and an annular flange 34 located on the outer periphery of the guide portion 32. The press-fitting portion 31, the guide portion 32, and the holder portion 33 are formed as a single piece of resin. The flange portion 34 is a metal plate made of, for example, brass, stainless steel, or the like, and the flange portion 34 is integrally provided together with the resin-made press-fitting portion 31 and the bracket portion 33 by insert molding.
The guide member 3 is assembled to the valve housing 2, and is fixed to the upper end portion of the valve housing 2 by welding at the flange portion 34. In the guide member 3, a cylindrical guide hole 32a is formed in the guide portion 32 with the Z-direction as the axial direction, and a female screw portion (screw hole) 33a coaxial with the guide hole 32a is formed at the center of the holder portion 33.
The main valve element 4 is disposed in the guide hole 32a of the holder 33, and is formed in a cylindrical shape having the Z direction as an axial direction as a whole. Main spool 4 integrally has: a partition portion 41 extending along the XY plane for the sub-valve 5 to approach or separate from; a cylindrical portion 42 extending from the partition portion 41 toward the opposite side (upper side) of the main valve port 23 a; and a main valve portion 43 that approaches or separates from the main valve seat 23.
The partition wall 41 is a sub-valve seat provided at the lower end of the cylindrical portion 42, and is formed in a plate shape having a predetermined plate thickness (Z-direction dimension). The partition portion 41 and the cylindrical portion 42 form a bottomed cylindrical portion, and the inside of the bottomed cylindrical portion serves as the sub-valve chamber 4R. A sub-valve port 41a as a through hole is formed in the center of the partition wall 41. The cylindrical portion 42 is formed in a cylindrical shape, and its inner peripheral surface forms a needle guide hole 42 a. A washer 53 and a guide boss 54 attached to a valve shaft 51 described below are inserted into the needle guide hole 42a of the cylindrical portion 42, and an annular stopper 44 is fixed to the upper end of the cylindrical portion 42 by fitting, fixing, welding, or the like. A main valve spring 4a is disposed between the stopper 44 and the upper end of the guide hole 32a, and the main valve spring 4a biases the main valve body 4 in the direction of the main valve seat 23 (downward in the Z direction; closing direction).
As shown in fig. 5, the cylindrical portion 42 has a plurality of (four in the present embodiment, or more than one) communication holes 421 for communicating the inside and the outside thereof. The four communication holes 421 are arranged at equal intervals in the circumferential direction around the Z direction. Fig. 5 shows a state in which two communication holes 421 are aligned in the X direction and the other two communication holes 421 are aligned in the Y direction, but main valve element 4 is rotatable with respect to valve housing 2, and the position of communication hole 421 may be changed by the rotation of main valve element 4. That is, the positional relationship of the communication hole 421 and the first port 21 may vary. The main valve chamber 2R, the sub valve chamber 4R, the sub valve port 41a, and the main valve port 23a are communicated with each other by forming the communication hole 421 in the cylindrical portion 42.
The main valve portion 43 is formed in a substantially cylindrical shape such that the cylindrical portion 42 extends downward from the partition portion 41. The main valve portion 43 may be seated (abutted) on the main valve seat 23 or may be slightly separated from the main valve seat in the fully closed state.
The sub-valve body 5 is a needle valve, is provided at the lower end portion of a rotor shaft 61 described below, and integrally includes a valve shaft 51 connected to the rotor shaft 61 side and a needle portion 52 connected to the lower end of the valve shaft 51. The sub-valve body 5 further includes an annular washer 53 disposed on the valve shaft 51 and a guide boss 54 fixed to the valve shaft 51. The guide boss 54 is fixed separately from the valve shaft 51, but the guide boss 54 may be formed integrally with the valve shaft 51. The washer 53 and the guide boss 54 are slidably inserted into the needle guide hole 42 a.
The driving section 6 is provided inside and outside a housing 24 fixed to the upper end of the valve housing 2, and includes a stepping motor 6A, a screw feed mechanism 6B for advancing and retracting the sub-valve body 5 by rotation of the stepping motor 6A, and a stopper mechanism 6C for restricting rotation of the stepping motor 6A. The housing 24 is hermetically fixed to the valve housing 2 by welding or the like, for example.
The stepping motor 6A includes a rotor shaft 61, a magnetic rotor 62 rotatably disposed inside the casing 24, a stator coil 63 disposed on the outer periphery of the casing 24 so as to face the magnetic rotor 62, and other yokes, exterior members, and the like, which are not shown. The rotor shaft 61 is attached to the center of the magnetic rotor 62 via a bushing, and a male screw portion 61a is formed on the outer periphery of the rotor shaft 61 on the guide member 3 side. The male screw portion 61a is screwed into the female screw portion 33a of the guide member 3, whereby the guide member 3 supports the rotor shaft 61 on the axis in the Z direction. The female screw portion 33a of the guide member 3 and the male screw portion 61a of the rotor shaft 61 constitute a screw feeding mechanism 6B.
Here, the opening and closing operations of the main valve element 4 and the sub valve element 5 in the motor-operated valve 1 will be described in detail. When the magnetic rotor 62 and the rotor shaft 61 are rotated by the driving of the stepping motor 6A, the rotor shaft 61 is moved in the Z direction by the screw feeding mechanism 6B of the male screw portion 61a of the rotor shaft 61 and the female screw portion 33a of the guide member 3. Thereby, the sub-valve body 5 moves forward and backward in the Z direction to approach or separate from the sub-port 41a, and controls the valve opening degree of the sub-port 41 a. Then, the sub-valve body 5 (washer 53) engages with the main valve body 4 (stopper 44), and the main valve body 4 moves together with the sub-valve body 5 and approaches or separates from the main valve seat 23. Thereby, the flow rate of the refrigerant flowing from the first joint pipe 11 toward the second joint pipe 12 is controlled.
The magnetic rotor 62 is provided with a projection 62a, and the projection 62a regulates the lowermost end position and the uppermost end position of the rotor shaft 61 (and the magnetic rotor 62) by operating the rotation limiting mechanism 6C in accordance with the rotation of the magnetic rotor 62. Fig. 1 shows a state in which the rotor shaft 61 (and the magnetic rotor 62) is located at the lowermost position.
The detailed shapes of the sub-port 41a and the sub-valve body 5 and the relationship therebetween will be described below with reference to fig. 2 to 4. Fig. 2 shows a state in which the sub-valve body 5 is positioned at the lowermost position and the valve opening of the sub-valve opening 41a is minimum, fig. 3 shows a state in which the sub-valve body 5 is positioned above the lowermost position and the valve opening is medium, and fig. 5 shows a state in which the sub-valve body 5 is positioned at the uppermost position and the valve opening of the sub-valve opening 41a is maximum. The sub-valve body 5 does not abut against the partition wall 41 at the lowermost end position, and fluid can pass through the sub-port 41 a. In the uppermost position, the lower end (tip end) of the sub-valve body 5 is positioned in the sub-valve port 41 a.
The sub-valve port 41a includes: a tapered portion 412 whose inner diameter gradually decreases from the upper end surface 411 toward the lower side (the main valve port 23a side); and a cylindrical inner circumferential surface 413 (having a constant inner diameter) extending downward from the lower end of the tapered portion 412. The upper end portion 412A of the tapered portion 412 is an open end portion located at an end of the partition portion 41 on the opposite side from the main valve port 23 a. The cylindrical inner peripheral surface 413 is located closer to the main valve port 23a than the upper end 412A, and is formed to have a smaller diameter than the upper end 412A, thereby forming a smaller diameter portion. The cylindrical inner peripheral surface 413 has the smallest inner diameter at the sub-valve port 41 a.
The tapered portion 412 is formed over more than half of the entire sub-port 41 a. That is, the cylindrical inner peripheral surface 413 is provided closer to the main valve port 23a than the Z-direction central portion of the partition wall 41. The cylindrical inner circumferential surface 413 is preferably provided in a region on the Z-direction lower side 1/3 of the partition wall 41.
The needle portion 52 of the sub-valve 5 includes, in order from the Z-direction upper side, a first straight portion 521 formed continuously with the valve shaft 51 and having a constant outer diameter, a first tapered portion 522 having an outer diameter that gradually decreases toward the Z-direction lower side, a second straight portion 523 having a constant outer diameter, and a second tapered portion 524 having a truncated cone shape having an outer diameter that gradually decreases toward the Z-direction lower side.
The inclination angle of the first tapered portion 522 with respect to the Z direction is smaller than the inclination angle of the tapered portion 412 of the sub-valve port 41a with respect to the Z direction. That is, as shown in fig. 2, in a state where the first tapered portion 522 and the tapered portion 412 face each other, the interval therebetween increases toward the Z-direction upper side. The outer diameter of the second straight portion 523 is smaller than the inner diameter of the cylindrical inner peripheral surface 413.
In the state shown in fig. 2, the lower end portion of the first flat portion 521, the entire first tapered portion 522, the entire second flat portion 523, and the upper end portion of the second tapered portion 524 are located inside the sub-valve port 41 a. The distance between the sub valve body 5 and the sub valve port 41a is smallest between the second straight portion 523 and the cylindrical inner peripheral surface 413, and this position becomes the minimum throttle portion a 1. The larger the interval between the sub-valve body 5 and the sub-valve port 41a, the larger the cross-sectional area through which the fluid can pass, and the easier the fluid can pass, so the following description will be made focusing on the interval between the sub-valve body 5 and the sub-valve port 41 a. A passage a2 is formed between the first flat portion 521 and the tapered portion 412 and a passage A3 is formed between the first tapered portion 522 and the tapered portion 412 on the upper side of the minimum throttle portion a 1. At the passage portion A3, the distance between the sub valve body 5 and the sub valve port 41a is larger than the minimum throttle portion a1, and at the passage portion a2, the distance between the sub valve body 5 and the sub valve port 41a is larger than the passage portion A3.
In this way, a portion having a large interval between the sub-valve body 5 and the sub-valve port 41a is formed above the minimum throttle portion a1 (upstream side when the first port 21 is primary side), and the fluid easily passes through this portion, so this portion becomes a rectifying portion in which the fluid is rectified. At this time, both the first passage section a1 and the second passage section a2 may function as a rectifying section, or only one may function as a rectifying section. That is, it is difficult to obtain the flow regulating effect when the distance between the sub-valve body 5 and the sub-valve port 41a is excessively large or small, and a portion having an appropriate distance may be a flow regulating portion. In this way, the rectifying portion may be formed at the opening end portion (the upper end portion 412A), or may be formed at a position between the opening end portion and the small diameter portion. In the illustrated example, the second passage portion a2 mainly functions as a rectifying portion.
In the state shown in fig. 3, the lower portion of the first tapered portion 522, the entire second flat portion 523, and the entire second tapered portion 524 are located inside the sub-valve port 41 a. The distance between the sub-valve body 5 and the sub-valve port 41a is smallest between the second tapered portion 524 and the upper end portion of the cylindrical inner peripheral surface 413 (the boundary portion with the tapered portion 412), and this position becomes the minimum throttle portion a 4. As in the state shown in fig. 2, a portion where the distance between the sub-valve body 5 and the sub-valve port 41a is large is formed above the minimum throttle portion a4, and this portion serves as a flow regulating portion. In the illustrated example, mainly the passage portion a5 between the first tapered portion 522 or the second straight portion 523 and the tapered portion 412 functions as a rectifying portion.
In the state shown in fig. 4, only the lower side portion of the second tapered portion 524 is located inside the sub-valve port 41 a. The distance between the sub-valve body 5 and the sub-valve port 41a is smallest between the tip end of the second tapered portion 524 and the tapered portion 412, and this position becomes the minimum throttle portion a 6. That is, the minimum throttle portion is not formed on the cylindrical inner circumferential surface 413 as the small diameter portion. As in the state shown in fig. 2 and 3, a passage a7, which is a portion where the distance between the sub-valve body 5 and the sub-valve port 41a is large, is formed above the minimum throttle portion a6, and this passage a7 serves as a flow regulating portion.
Since the sub-port 41a has the tapered portion 412, when at least a part of the needle portion 52 is located inside the sub-port 41a, the minimum throttle portion and the flow regulating portion located above the minimum throttle portion are formed in the same manner as described above. That is, in the needle portion 52, a portion facing the sub-valve port 41a in the XY plane changes between the state shown in fig. 3 and the state shown in fig. 5, but a minimum throttle portion and a flow straightening portion are formed. The sub-valve 5 may be moved beyond this range.
When the fluid flowing into the main valve chamber 2R from the first port 21 flows into the sub valve chamber 4R through the communication hole 421 of the main valve 4, the flow rate may be different between the four communication holes 421. Namely, there is a tendency that: the flow rate is likely to increase as the communication hole 421 is closer to the first port 21 (toward the first port 21 side), and the flow rate is likely to decrease as the communication hole 421 is farther from the first port 21 (not toward the first port 21 side). Therefore, the flow rate of the fluid that reaches the sub-valve port 41a through the four communication holes 421 also varies, and the flow rate of the fluid may vary depending on the position in the vicinity of the sub-valve port 41a, and may be uneven.
Further, since the positional relationship between the communication hole 421 and the first port 21 may change due to the rotation of the main valve 4, the flow rate of the fluid passing through the communication hole 421 may change with time, and the flow rate of the fluid may become unstable with time near the sub-valve port 41 a.
Even when the spatial or temporal instability of the flow rate occurs as described above, the flow rate of the fluid passing through the sub-port 41a is rectified by the rectifying portion, and then is regulated by throttling at the minimum throttling portion that determines the substantial valve opening degree.
Next, an example of a refrigeration cycle system provided with the motor-operated valve 1 of the present embodiment will be described with reference to fig. 6. This refrigeration cycle system is used for an air conditioner such as a household air conditioner. The motor-operated valve 1 is provided as a "dehumidification control valve" between the first indoor heat exchanger 91 (which operates as a cooler during dehumidification) and the second indoor heat exchanger 92 (which operates as a heater during dehumidification). The motor-operated valve 1, the first indoor heat exchanger 91, the second indoor heat exchanger 92, the electronic expansion valve 93, the outdoor heat exchanger 94, the compressor 95, and the four-way valve 96 constitute a heat pump refrigeration cycle. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated valve 1 are installed indoors, and the electronic expansion valve 93, the outdoor heat exchanger 94, the compressor 95, and the four-way valve 96 are installed outdoors, thereby constituting a cooling/heating apparatus.
According to the present embodiment described above, the sub-valve port 41a has the upper end portion 412A as the opening end portion and the cylindrical inner peripheral surface 413 as the small diameter portion, and thus the rectifying portion can be formed at the upstream side of the minimum throttle portion. Therefore, when the fluid flows into the sub valve chamber 4R through the first port 21 and the communication hole 421, even when the flow rate becomes unstable, the noise can be reduced by rectifying the fluid.
Further, since the sub-port 41a has the tapered portion 412, the fluid easily flows along the tapered portion 412, and the occurrence of disturbance in the flow of the fluid can be suppressed.
Further, by providing the cylindrical inner peripheral surface 413 as the small diameter portion closer to the main valve port 23a than the Z-direction central portion of the partition wall portion 41, the volume can be increased by securing the Z-direction dimension of the space for rectifying the fluid, and the fluid can be easily rectified.
The present invention is not limited to the above-described embodiments, and includes other configurations and the like that can achieve the object of the present invention, and the present invention also includes modifications and the like described below. For example, in the above-described embodiment, the sub-port 41a has the tapered portion 412, and the sub-valve body 5 has the tapered portions 522 and 524, but the combination of the shapes of the sub-port and the sub-valve body is not limited to this.
In the first modification shown in fig. 7 and 8, the sub-port 41a has the same shape as that of the above-described embodiment, and the needle portion 52A of the sub-valve body 5A includes, in order from the upper side in the Z direction, a first straight portion 521, a first tapered portion 522, and a second straight portion 525. Fig. 7 shows a state in which the sub-valve body 5A is positioned at the lowermost position and the valve opening degree of the sub-valve opening 41a is minimum, and fig. 8 shows a state in which the sub-valve body 5A is positioned at the uppermost position and the valve opening degree of the sub-valve opening 41a is maximum. The sub-valve body 5A does not abut against the partition wall 41 at the lowermost end position, and fluid can pass through the sub-port 41 a. The sub-valve body 5A has a lower end portion (tip end portion) disposed inside the sub-valve port 41a at any one of the lowermost end position and the uppermost end position, and when the sub-valve body 5A moves between the lowermost end position and the uppermost end position, the second straight portion 525 of the needle portion 52A faces the sub-valve port 41a in the XY plane.
In the state shown in fig. 7, a minimum throttle portion A8 is formed between the lower end of the second straight portion 525 and the tapered portion 412, and a passage portion a9 between the second straight portion 525 and the upper end portion 412A of the tapered portion 412 functions as a rectifying portion. Similarly, in the state shown in fig. 8, a minimum throttle portion a10 is formed between the lower end of the second straight portion 525 and the tapered portion 412, and a passage portion a11 between the second straight portion 525 and the upper end 412A of the tapered portion 412 functions as a rectifying portion.
In the first modification, the cylindrical inner peripheral surface 413 is formed to have a smaller dimension in the Z direction than in the above embodiment, but the cylindrical inner peripheral surface may be omitted as long as the dimension of the cylindrical inner peripheral surface is appropriately set, and the entire sub-valve port may be formed as the tapered portion. Further, a cylindrical inner peripheral surface may be formed on the upper end side of the sub-valve port, and a tapered portion may be formed on the lower side thereof.
In a second modification shown in fig. 9 to 11, the sub-port 41b has a cylindrical inner peripheral surface 414 and an annular portion 415, and the sub-valve body 5 has the same shape as that of the above-described embodiment. Fig. 9 shows a state in which the sub-valve body 5 is positioned at the lowermost position and the valve opening of the sub-valve opening 41b is minimum, fig. 10 shows a state in which the sub-valve body 5 is positioned above the lowermost position and the valve opening is medium, and fig. 11 shows a state in which the sub-valve body 5 is positioned at the uppermost position and the opening of the sub-valve opening 41b is maximum. The sub-valve body 5 does not abut against the partition wall 41 at the lowermost end position, and fluid can pass through the sub-port 41 b. In the uppermost position, the lower end portion (tip end portion) of the sub-valve body 5 is disposed inside the valve port 41 b.
The cylindrical inner circumferential surface 414 extends downward in the Z direction with the upper end surface 411 of the partition wall portion 41 as an open end, and has a substantially constant inner diameter. The annular portion 415 is formed in a plate shape extending along the XY plane from a lower end portion of the cylindrical inner circumferential surface 414 toward the inner circumferential side. The inner diameter of the annular portion 415 is smaller than the inner diameter of the cylindrical inner peripheral surface 414, and a stepped portion 416 is formed between the cylindrical inner peripheral surface 414 and the annular portion 415. The outer diameter of the second straight portion 523 is smaller than the inner diameter of the through hole of the annular portion 415.
In the state shown in fig. 9, a minimum throttle portion a12 is formed between the second flat portion 523 and the annular portion 415, and a passage portion having a larger interval between the sub-port 41b and the needle portion 52 than the minimum throttle portion a12 is formed above the minimum throttle portion a 12. In such a passage portion, for example, mainly the passage portion a13 between the first straight portion 521 and the cylindrical inner peripheral surface 414 functions as a rectifying portion. In the state shown in fig. 10, a minimum throttle portion a14 is formed between the tip end portion of the second tapered portion 524 and the annular portion 415, and a passage portion having a larger interval between the sub-port 41b and the needle portion 52 than the minimum throttle portion a14 is formed above the minimum throttle portion a. In such a passage portion, for example, the passage portion a15 mainly between the first tapered portion 522 and the cylindrical inner peripheral surface 414 functions as a rectifying portion. In the state shown in fig. 11, a minimum throttle portion a16 is formed between the distal end portion of the second tapered portion 524 and the cylindrical inner peripheral surface 414, and a passage portion (passage portion a17 between the second tapered portion 524 and the cylindrical inner peripheral surface 414) in which the distance between the sub-port 41b and the needle-like portion 52 is larger than the minimum throttle portion a16 is formed above the minimum throttle portion a, and the passage portion a17 functions as a rectifying portion.
Further, as the above-described embodiment, the first modification, and the second modification, combinations of the shapes of the sub valve port and the sub valve body are exemplified, but the shapes are not limited to the above-described examples as long as they are appropriately combined. For example, the sub-valve port may have both a tapered portion and a stepped portion, or the sub-valve port may have an opening end portion and a small diameter portion, and a rectifying portion having a larger volume than the minimum throttle portion may be formed at a position upstream of the minimum throttle portion.
In the above embodiment, the sub-valve body 5 does not abut against the partition wall portion 41 at the lowermost end position, and the fluid can pass through the sub-valve port 41a, but as shown in the specific examples of fig. 12 to 14, the sub-valve body may be configured so as to be unable to pass through the fluid by abutting against the partition wall portion. Fig. 12 corresponds to the shape of the above embodiment, and the first tapered portion 522 abuts on the boundary portion between the tapered portion 412 and the cylindrical inner circumferential surface 413. Fig. 13 corresponds to the first modification described above, and the vicinity of the first straight portion 521 of the first tapered portion 522 abuts on the upper end portion 412A. Fig. 14 corresponds to the second modification described above, and the first tapered portion 522 abuts against the upper end portion of the annular portion 415. The combination of the positions at which the sub valve body and the sub valve port are in contact with each other is not limited to the above combination.
In the above embodiment, the cylindrical inner circumferential surface 413 as the small diameter portion is provided closer to the main valve port 23a than the center portion in the Z direction of the partition wall portion 41, but the position of the small diameter portion is not limited to this. For example, when the dimension of the partition wall in the Z direction is sufficiently large and the volume of the rectifying portion is easily secured, the small diameter portion may be set to be opposite to the main valve port from the center portion of the partition wall in the Z direction.
In the above embodiment, the cylindrical inner circumferential surface 413 as the small diameter portion is a portion having the smallest inner diameter of the sub valve port 41a and is located at the position closest to the main valve port 23a side of the partition wall portion 41, but may be formed in a shape (constricted shape) in which the inner diameter is increased again as going from the small diameter portion to the main valve port side, for example.
While the embodiments of the present invention have been described in detail with reference to the drawings, the specific configurations are not limited to the embodiments described above, and the present invention also includes design changes and the like within a range not departing from the gist of the present invention.
Claims (5)
1. An electrically operated valve comprising: a valve housing; a main valve body that changes an opening degree of a main valve port of a main valve chamber provided in the valve housing; an auxiliary valve body that changes an opening degree of an auxiliary valve port provided in an auxiliary valve chamber of the main valve body; and a driving part for driving the auxiliary valve core to move forward and backward along the axial direction,
the above-mentioned electric valve is characterized in that,
the valve housing has a first port that opens in a direction intersecting the axial direction and a second port that communicates with the main valve port and opens in the axial direction,
the main valve element includes a partition wall portion extending in a direction intersecting the axial direction and allowing the sub valve element to approach or separate from the main valve element, and a cylindrical portion extending from the partition wall portion toward a side opposite to the main valve port and forming the sub valve chamber by the partition wall portion and the cylindrical portion,
at least one communication hole for communicating the inside and outside of the cylindrical portion is formed in the cylindrical portion,
the sub-port has an opening end portion which is a through hole formed in the partition wall portion and is an end portion on the opposite side of the main port, and a small diameter portion which is located on the main port side of the opening end portion and is formed to have a diameter smaller than that of the opening end portion.
2. Electrically operated valve according to claim 1,
the sub-valve port has a tapered portion between the opening end portion and the small diameter portion, the inner diameter of the tapered portion decreasing toward the main valve port.
3. Electrically operated valve according to claim 1 or 2,
the sub-valve opening has a stepped portion between the opening end portion and the small diameter portion, and the stepped portion is formed by a cylindrical inner peripheral surface extending in the axial direction and an annular portion extending radially inward from an end portion of the cylindrical inner peripheral surface on the main valve opening side.
4. An electrically operated valve according to any one of claims 1 to 3,
the small diameter portion is provided closer to the main valve port than the axial center portion of the partition wall portion, and is a portion having the smallest inner diameter in the sub valve port.
5. A refrigeration cycle system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve arranged between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidification valve arranged on the indoor heat exchanger,
use of an electrically operated valve as claimed in any one of claims 1 to 4 as said dehumidification valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020115133A JP7409982B2 (en) | 2020-07-02 | 2020-07-02 | Electric valve and refrigeration cycle system |
| JP2020-115133 | 2020-07-02 |
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| Publication Number | Publication Date |
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| CN113883284A true CN113883284A (en) | 2022-01-04 |
| CN113883284B CN113883284B (en) | 2024-03-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202110686206.4A Active CN113883284B (en) | 2020-07-02 | 2021-06-21 | Electric valve and refrigeration cycle system |
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| Country | Link |
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| JP (1) | JP7409982B2 (en) |
| CN (1) | CN113883284B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114352751A (en) * | 2022-01-20 | 2022-04-15 | 广东威灵电机制造有限公司 | Electronic expansion valve, refrigeration equipment and automobile |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2617337A (en) * | 2022-04-04 | 2023-10-11 | Weir Minerals Netherlands Bv | Valve |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN113883284B (en) | 2024-03-01 |
| JP7409982B2 (en) | 2024-01-09 |
| JP2022012948A (en) | 2022-01-18 |
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