CN110230721B - Electric valve and refrigeration cycle system - Google Patents
Electric valve and refrigeration cycle system Download PDFInfo
- Publication number
- CN110230721B CN110230721B CN201910118151.XA CN201910118151A CN110230721B CN 110230721 B CN110230721 B CN 110230721B CN 201910118151 A CN201910118151 A CN 201910118151A CN 110230721 B CN110230721 B CN 110230721B
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- valve
- valve body
- port
- rotor
- electrically operated
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 10
- 239000012530 fluid Substances 0.000 claims description 38
- 230000007423 decrease Effects 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 description 6
- 230000001174 ascending effect Effects 0.000 description 4
- 230000030279 gene silencing Effects 0.000 description 4
- 239000002184 metal Substances 0.000 description 4
- 229910052751 metal Inorganic materials 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 229910001220 stainless steel Inorganic materials 0.000 description 4
- 239000010935 stainless steel Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000006247 magnetic powder Substances 0.000 description 1
- 230000005389 magnetism Effects 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
- 229910000859 α-Fe Inorganic materials 0.000 description 1
Images
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Details Of Valves (AREA)
- Valve Housings (AREA)
- Lift Valve (AREA)
Abstract
The invention provides an electrically operated valve capable of properly maintaining silence and a refrigeration cycle system using the electrically operated valve. In a state where the valve body portion is closest to the valve seat portion, the maximum outer diameter of the valve body portion becomes the maximum diameter on the valve seat portion side with respect to the lower end of the valve shaft holder, the maximum outer diameter of the valve body portion is larger than the outer diameter of an annular valve seat plane portion formed on the top surface of the valve seat portion, and the position of the valve seat plane portion in the valve center axis direction is located closer to the rotor side than the lowermost end of the inner diameter of the first valve port, which becomes the farthest position from the rotor.
Description
Technical Field
The present invention relates to an electric valve and a refrigeration cycle system using the same.
Background
Conventionally, an electrically operated valve having a structure shown in fig. 8 is known (for example, see patent document 1). That is, when the rotor 103 is rotated by driving the stepping motor, the valve body 114 moves in the valve center axis L direction, which is the center axis of the valve body 114, due to the thread feeding action of the female thread 131a and the male thread 121 a. The opening degree of the port 130b is thereby adjusted, and the flow rate of the fluid flowing into the pipe joint 111 and flowing out of the pipe joint 112 or the flow rate of the fluid flowing into the pipe joint 112 and flowing out of the pipe joint 111 is controlled.
Here, when flow control of various fluids is performed, there is a problem that fluid passing sound is generated, and thus silencing is required. In the indoor unit of the refrigeration cycle of a household air conditioner or a commercial air conditioner using a refrigerant, when the flow rate of the refrigerant is controlled by the motor-operated valve 100, the liquid refrigerant becomes a gas-liquid mixed two-phase flow before and after passing through the valve port 130b, and it is required to exhibit silence particularly in various refrigerant states and operating conditions.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2016-089870
Disclosure of Invention
Problems to be solved by the invention
However, the motor-operated valve 100 is fixed to a fluid pipe, not shown, via the pipe joint 111 and the pipe joint 112, and the valve body 120 and the valve port 130b of the valve seat 130 are exposed in the flow path. Here, the valve body portion 120 is a member provided with the valve body 114 at the lower end of the valve guide 118. Further, the valve guide 118 holds the spool 114 at the lower end and moves in the valve center axis L direction together with the spool 114.
Therefore, in the motor-operated valve 100, when a high pressure difference is generated between the inlet side and the outlet side of the valve port 130b, in particular, when the refrigerant flows from the pipe joint 111 to the pipe joint 112, as shown in fig. 9, the fluid such as the refrigerant flowing from the pipe joint 111 collides with the valve body 120, and the valve body 120 may vibrate in the radial direction (C) due to the collision force. If a sound is generated by the vibration, the silencing performance of the motor-operated valve 100 may not be maintained.
Therefore, the following configuration is considered: as shown in fig. 10, by raising the position of the top surface 130a of the valve seat 130, the fluid flowing into the valve chamber 121 from the pipe joint 111 does not directly collide with the valve body 120. However, in this case, an ascending flow generated when the fluid flowing from the pipe joint 111 collides with the valve seat 130 enters the guide portion 132 that restricts the inclination and movement of the valve body portion 120, and the valve body portion 120 may vibrate, thereby generating noise. Therefore, in this case as well, it is difficult to maintain the quietness.
The purpose of the present invention is to provide an electrically operated valve capable of maintaining appropriate quietness, and a refrigeration cycle system using the electrically operated valve.
Means for solving the problems
[1] The electric valve of the invention converts the rotary motion of the rotor contained in the inner circumference of the housing into the linear motion by the screw feeding mechanism of the external screw member and the internal screw member, and moves the valve body contained in the valve main body in the valve central axis direction as the central axis of the valve body based on the linear motion,
the electrically operated valve is characterized by comprising:
a valve chamber which is a space formed in the valve main body;
a first valve port provided on a side surface of the valve main body and serving as an inlet/outlet of the valve chamber side;
a second valve port provided directly below the valve body in a direction coaxial with the valve body, the second valve port being capable of approaching or separating from the valve body;
a cylindrical valve seat portion in which the second valve port is formed on the rotor side; and
a valve shaft holder that guides the valve body portion in the valve center axis direction,
in a state where the valve body portion is closest to the valve seat portion,
the maximum outer diameter of the valve body portion, which has the maximum diameter on the valve seat portion side with respect to the lower end of the valve shaft holder, is larger than the outer diameter of an annular valve seat flat surface portion formed on the top surface of the valve seat portion,
the position of the valve seat plane portion in the valve center axis direction is located closer to the rotor than a lowermost end of the inner diameter of the first valve port, which is located farthest from the rotor.
In this way, by forming the maximum outer diameter of the valve body portion to be larger than the outer diameter of the valve seat flat surface portion, the valve body portion blocks the fluid, and the fluid is prevented from flowing into the gap between the valve body portion and the housing chamber housing the valve body portion, so that the noise generated by the vibration of the valve body portion can be alleviated, and the quietness can be appropriately maintained.
[2] In addition, the electrically operated valve of the present invention is characterized in that,
the valve core portion includes:
a valve element that adjusts the flow rate of the fluid passing through the second port; and
a valve guide that holds the valve body on the valve seat side and is disposed slidably with respect to the valve shaft holder,
the valve body is fixed to the valve guide.
By fixing the valve body to the valve guide in this manner, the valve body can be prevented from vibrating in the valve guide due to the fluid, and the quietness can be maintained.
[3] In addition, the electrically operated valve of the present invention is characterized in that,
the valve body includes:
a needle portion which is a portion closest to the second valve port; and
and an annular flat surface portion located on an outer periphery of a base end of the needle portion.
Accordingly, the valve body portion is biased upward by the fluid that collides against the flat surface portion, and the contact surface between the thread ridges of the male screw and the female screw in the screw feed mechanism can be constantly maintained, thereby suppressing the occurrence of screw loosening. Therefore, the silencing performance of the electric valve can be appropriately maintained.
[4] In addition, the electrically operated valve of the present invention is characterized in that,
a shoulder portion forming a lower end edge of the valve body portion having the maximum outer diameter,
in a state where the valve body portion is closest to the valve seat portion, a position of the shoulder portion in the valve center axis direction is located closer to the rotor than an uppermost end of a position where an inner diameter of the first valve port is formed closest to the rotor.
Thus, when fluid flows in from the first valve port, even in a state where the valve body portion is closest to the seat portion, it is possible to reduce the possibility that the fluid collides with the valve body portion, and the shoulder portion blocks the upward flow, thereby preventing the upward flow from flowing into the gap between the valve body portion and the housing chamber housing the valve body portion.
[5] In addition, the electrically operated valve of the present invention is characterized in that,
the valve seat portion has a tapered portion whose outer diameter decreases toward the rotor.
Since the fluid is guided to the inner side of the maximum outer diameter of the valve body by the tapered portion, the fluid can be more appropriately prevented from flowing into the gap between the valve body and the housing chamber that houses the valve body, and the quietness of the electric valve can be maintained.
[6] In addition, the electrically operated valve of the present invention is characterized in that,
the lowermost end of the first valve port is located closer to the rotor than an inner bottom surface in the valve main body.
Thus, the fluid that has not risen can be made to flow to the lower space near the inner bottom surface in the valve body, and the fluid can be prevented from flowing into the gap between the valve body and the housing chamber that houses the valve body.
[7] Further, the refrigeration cycle system of the present invention includes a compressor, a condenser, an expansion valve, and an evaporator, and is characterized in that,
the motor-operated valve described above is used as the expansion valve.
The effects of the invention are as follows.
According to the present invention, it is possible to provide an electrically operated valve capable of appropriately maintaining quietness and a refrigeration cycle using the electrically operated valve.
Drawings
Fig. 1 is a schematic cross-sectional view of an electrically operated valve according to an embodiment.
Fig. 2 is an enlarged view of a main portion of the electrically operated valve of the embodiment.
Fig. 3 is an enlarged view of a main portion of the motor-operated valve according to the embodiment in a state where the valve core portion is located closest to the valve seat portion.
Fig. 4 is an enlarged view of a main portion of an electric valve having a seat portion provided with a tapered portion according to another embodiment.
Fig. 5 is an enlarged view of a main portion of an electric valve in which a valve seat portion and a valve main body are integrated in another embodiment.
Fig. 6 is an enlarged view of a main portion of an electric valve in which a first port is formed in a side surface of a valve main body according to another embodiment.
Fig. 7 is an enlarged view of a main portion of an electric valve in which a needle portion of a valve body portion is not provided with a flat surface portion according to another embodiment.
Fig. 8 is a schematic cross-sectional view of a conventional motor-operated valve.
Fig. 9 is an enlarged view of a main portion of a conventional motor-operated valve.
Fig. 10 is an enlarged view of a main portion of an electrically operated valve as a comparative example.
In the figure:
2-an electric valve, 4-a rotor, 6-a valve shaft holder, 6 a-a cylindrical small diameter portion, 6 b-a cylindrical large diameter portion, 6 c-an engaging portion, 6 d-an internal thread, 6 f-a flange portion, 6 g-an upper opening portion, 6 h-a housing chamber, 6 k-a lower end of the valve shaft holder, 11-a valve chamber, 11 a-a lower space, 12-a first coupling, 12 a-a first valve port, 15-a second coupling, 16-a valve seat portion, 16 a-a second valve port, 16 b-a valve seat flat portion, 16 c-a tapered portion, 17-a valve core, 17 a-a fixing portion, 17 b-a cap portion, 17 c-a needle portion, 17 c-a base end of the needle portion, 17 d-a flat portion, 17 e-a shoulder portion, 18-a valve guide, 18 a-a through hole, 20-a valve core portion, 21-a top portion, 22-a clearance, 27-a valve spring, 30-a valve main body, 30a internal bottom surface, 33-a bush member, 41-a valve spring, 41 a-external thread, 41 b-flange portion, 41 c-protrusion portion, 51-pressure equalizing hole, 60-housing, 67-rotor housing chamber, 70-gasket, 100-electric valve, 103-rotor, 111-pipe joint, 112-pipe joint, 114-valve core, 118-valve guide, 120-valve core portion, 121-valve chamber, 121 a-external thread, 130-valve seat, 130 a-top surface, 130 b-valve port, 131 a-internal thread, L-valve center axis, M-valve center axis, O-tapered boundary portion, P-lowest end of inner diameter of first valve port, Q-highest end of inner diameter of first valve port, R-axial position of shoulder portion, X-maximum outer diameter of valve core portion, Y-outer diameter of flat portion of valve seat.
Detailed Description
Hereinafter, an electrically operated valve according to an embodiment of the present invention will be described with reference to the drawings. Fig. 1 is a schematic cross-sectional view showing an electric valve 2 according to an embodiment. In the present specification, "upper" or "lower" is defined in the state of fig. 1. That is, the rotor 4 is located above the valve body 17.
In the motor-operated valve 2, a valve main body 30 is integrally connected to a lower portion of an opening side of a cup-shaped housing 60 formed of metal in a cylindrical shape by welding or the like.
Here, the valve main body 30 is made of metal such as stainless steel, and has a valve chamber 11 as a space formed therein. A first pipe joint 12 made of, for example, stainless steel or copper and directly communicating with the valve chamber 11 is fixedly attached to a side surface of the valve main body 30. A first port 12a having a circular cross section, which serves as a fluid inlet and outlet, is formed in the first pipe joint 12 on the valve chamber 11 side. Further, a valve seat portion 16 is assembled to the inner bottom surface 30a of the valve main body 30 so as to protrude from the inner bottom surface 30a, and a second valve port 16a having a circular cross section is formed above the valve seat portion 16. The second port 16a is provided directly below the valve body 17 in a direction coaxial with the valve body 17. A second pipe joint 15 made of, for example, stainless steel or copper, which communicates with the first pipe joint 12 via the second port 16a and the valve chamber 11, is fixedly attached to the valve seat portion 16.
A rotatable rotor 4 is housed in the inner periphery of the housing 60, and a valve shaft 41 is disposed in the axial core portion of the rotor 4 via a bush member 33. The rotor 4 is formed of a resin material containing magnetic powder, a material having magnetism such as a ferrite magnet, or the like. The hub member 33 and the valve shaft 41 are both made of metal such as stainless steel, for example, and the valve shaft 41 coupled to the hub member 33 moves in the vertical direction integrally with the rotor 4 while rotating. A male screw 41a is formed on the outer peripheral surface of the valve shaft 41 near the intermediate portion. In the present embodiment, the valve shaft 41 functions as a male screw member. The spool 17 can be moved toward or away from the second valve port 16 a.
A stator including a yoke, a bobbin, a coil, and the like, which are not shown, is disposed on the outer periphery of the housing 60, and the rotor 4 and the stator constitute a stepping motor.
The valve shaft holder 6 is fixed to the valve body 30 at a position below the bush member 33 of the valve shaft 41 so as to be relatively non-rotatable, and the valve shaft holder 6 forms a screw feed mechanism a with the valve shaft 41 as described below, and has a function of suppressing inclination of the valve shaft 41.
The valve shaft holder 6 includes an upper cylindrical small diameter portion 6a, a lower cylindrical large diameter portion 6b, a fitting portion 6c housed in the inner circumferential portion of the valve body 30, and an annular flange portion 6 f. The flange portion 6f of the valve shaft holder 6 is fixed to the upper end of the valve main body 30 by welding or the like. A housing chamber 6h for housing a valve guide 18 described later is formed inside the valve shaft holder 6. Further, the portion of the valve shaft holder 6 other than the metal flange portion 6f is formed of a resin material.
A female screw 6d is formed at a position extending downward to a predetermined depth from the upper opening 6g of the cylindrical small diameter portion 6a of the valve shaft holder 6. Therefore, in the present embodiment, the valve shaft holder 6 functions as a female screw member. The screw feed mechanism a is configured by a male screw 41a formed on the outer periphery of the valve shaft 41 and a female screw 6d formed on the inner periphery of the cylindrical small diameter portion 6a of the valve shaft holder 6.
Further, a pressure equalizing hole 51 is formed through a side surface of the cylindrical large diameter portion 6b of the valve shaft holder 6, and the housing chamber 6h in the cylindrical large diameter portion 6b and the rotor housing chamber 67 (second back pressure chamber) communicate with each other through the pressure equalizing hole 51. By providing the pressure equalizing hole 51 in this manner, the space of the housing 60 that houses the rotor 4 and the space inside the valve shaft holder 6 communicate with each other, and thus the movement operation of the valve body 17 can be performed smoothly.
Further, a cylindrical valve body portion 20 is disposed below the valve shaft 41 so as to be slidable with respect to the housing chamber 6h of the valve shaft holder 6. The valve body portion 20 includes a cylindrical valve guide 18 that slides in the housing chamber 6h, and a valve body 17 that adjusts the flow rate of the fluid passing through the second port 16 a. Further, the spool 17 is fixed below the valve guide 18, and is held by the valve guide 18. Further, a compressed valve spring 27 and a spring seat 35 are accommodated in the valve guide 18. The upper end portion of the spring seat 35 is in point contact with the protrusion 41c of the valve shaft 41.
The top 21 side of the valve guide 18 is bent at substantially right angles by press forming. The top portion 21 is formed with a through hole 18 a. Further, a collar 41b is formed below the valve shaft 41.
Here, the valve shaft 41 is inserted into the through hole 18a of the valve guide 18 in a loosely fitted state so as to be rotatable and radially displaceable with respect to the valve guide 18, and the collar portion 41b is disposed in the valve guide 18 so as to be rotatable and radially displaceable with respect to the valve guide 18. The valve shaft 41 is inserted into the through hole 18a, and the upper surface of the collar portion 41b is disposed to face the top portion 21 of the valve guide 18. The diameter of the collar portion 41b is larger than the diameter of the through hole 18a of the valve guide 18, whereby the valve shaft 41 is prevented from coming off.
The valve shaft 41 and the valve guide 18 are movable in the radial direction relative to each other, and therefore, the concentricity with the valve guide 18 and the valve body 17 can be obtained without requiring a considerably high degree of concentric attachment accuracy with respect to the arrangement positions of the valve shaft holder 6 and the valve shaft 41.
A washer 70 having a through hole formed in the center thereof is provided between the top portion 21 of the valve guide 18 and the flange portion 41b of the valve shaft 41.
Next, a main part of the motor-operated valve 2 of the embodiment will be described. Fig. 2 is an enlarged view of a main part of the motor-operated valve 2 of the embodiment. As shown in fig. 2, the valve body 17 includes a columnar fixing portion 17a fixed to the inner periphery of the valve guide 18, a substantially disk-shaped cover portion 17b closing the lower end of the valve guide 18, and a needle portion 17c having a substantially truncated cone shape and having a function of adjusting the flow rate of the fluid passing through the second port 16 a. The needle portion 17c is located at the lowermost position of the valve body 17.
The lid 17b includes a flat surface 17d as an annular flat surface, and the flat surface 17d is located on the outer periphery of a base end 17 c' of a needle-like portion 17c protruding downward from the lid 17 b. A shoulder 17e is formed on the outer periphery of the flat surface portion 17d, and the shoulder 17e forms a lower end edge of a portion that constitutes a maximum outer diameter X (described later) of the valve body portion 20. Further, a gap 22 is formed between the outer periphery of the valve body portion 20 and the inner periphery of the housing chamber 6h of the valve shaft holder 6.
The maximum outer diameter X of the valve body 20 is a portion that has the maximum diameter in a range below the lower end 6k of the valve shaft holder 6 (see reference symbol S in fig. 3) in a state where the valve body 20 is closest to the seat portion 16. A valve seat flat surface portion 16b as an annular flat surface is formed on the top surface of the valve seat portion 16.
Here, the maximum outer diameter X of the valve body portion 20 is formed larger than the outer diameter Y of the valve seat flat surface portion 16b (X > Y). The position of the valve seat flat surface portion 16b fixedly attached to the second pipe joint 15 is located above (on the rotor 4 side) the lowest end P of the inner diameter of the first port 12a in the valve center axis M direction, which is the center axis of the valve body 17 and the valve body portion 20. Further, the lowermost end P is a position farthest from the rotor 4 in the inner diameter of the first valve port 12 a. The lowermost end P is located above the inner bottom surface 30a in the valve main body 30, and a lower space 11a surrounding the valve seat portion 16 is formed in the vicinity of the inner bottom surface 30a in the valve main body 30.
When a fluid flows into the valve chamber 11 from the first pipe joint 12 through the first port 12a, the fluid collides with the seat portion 16, thereby generating an upward flow in the valve center axis M direction and a downward flow in the valve center axis M direction. The ascending flow is split such that a part thereof is folded back downward after colliding against the flat surface portion 17d and the shoulder portion 17e, and the other part thereof flows from the shoulder portion 17e toward the inner side surface of the valve main body 30, thereby avoiding the inflow into the gap 22 between the valve body portion 20 and the housing chamber 6 h. Then, the upward flow collides with the flat surface portion 17d, thereby biasing the valve body portion 20 upward. On the other hand, the downward flow flows into the lower space 11 a.
As shown in fig. 3, in a state where the valve body portion 20 is closest to the valve seat portion 16, the position R of the shoulder portion 17e in the valve center axis M direction is located above the uppermost end Q of the inner diameter of the first port 12a (on the rotor 4 side). Further, the uppermost end Q is a position closest to the rotor 4 in the inner diameter of the first valve port 12 a. Accordingly, even in a state where the valve body portion 20 is closest to the seat portion 16, it is possible to reduce the amount of collision of the fluid flowing into the valve chamber 11 through the first port 12a against the valve body portion 20, and to prevent the upward flow caused by the collision of the fluid against the seat portion 16 from being blocked by the shoulder portion 17e and flowing into the gap 22.
According to the motor-operated valve 2 of this embodiment, when the seat portion 16 protrudes from the inner bottom surface 30a in the valve main body 30 and the position of the seat flat surface portion 16b is located above the lowermost end P of the inner diameter of the first port 12a in the valve center axis M direction, the maximum outer diameter X of the valve body portion 20 is formed to be larger than the outer diameter Y of the seat flat surface portion 16b (X > Y), whereby the valve body portion 20 blocks the upward flow and prevents the upward flow from flowing into the gap 22. Further, the valve body portion 20 is biased upward by the upward flow that hits the flat surface portion 17d, and the contact surface between the thread of the male screw 41a and the thread of the female screw 6d can be constantly maintained, whereby occurrence of thread loosening can be suppressed. Therefore, noise generated by the vibration of the valve body 20 can be mitigated, and the quietness can be reliably maintained.
Further, in a state where the valve body portion 20 is closest to the valve seat portion 16, the position R of the shoulder portion 17e in the valve center axis M direction is located above the uppermost end Q of the inner diameter of the first port 12a, so that even in this state, the fluid flowing in from the first port 12a can be reliably prevented from flowing into the gap 22, and the noise generated by the vibration of the valve body portion 20 can be more reliably suppressed.
Further, since the valve body 17 is fixed to the valve guide 18, the valve body 17 does not vibrate in the valve guide 18 due to the fluid, and the silence of the electric valve 2 can be maintained. Further, since the lower space 11a is formed in the valve main body 30 in the vicinity of the inner bottom surface 30a, the fluid flowing from the first port 12a and branched to the lower space 11a can be made to flow, and the fluid can be prevented from flowing into the gap 22.
In the above-described embodiment, as shown in fig. 4, the valve seat portion 16 may have a tapered portion 16c whose outer diameter decreases upward. In this case, the ascending flow is guided to a position inside the maximum outer diameter X of the valve body 20 by the tapered portion 16 c. Therefore, the upward flow can be more reliably prevented from flowing into the gap 22, and the silencing performance of the motor-operated valve 2 can be maintained. It is particularly preferable that the tapered boundary portion O of the tapered portion 16c, which is a portion where the outer periphery of the valve seat portion 16 starts to incline, be located below the lowest end P of the inner diameter of the first port 12a (on the valve chamber inner bottom surface 30a side). In this case, the inflow of the ascending current into the gap 22 can be further appropriately avoided.
Further, in the above-described embodiment, the description has been given of the case where the valve seat portion 16 as an independent member is incorporated in the inner bottom surface 30a of the valve main body 30 as an example, but as shown in fig. 5, the valve seat portion 16 may be formed as an integral member of the valve main body 30 and the valve seat portion 16 while protruding from the inner bottom surface 30a of the valve main body 30. In this case, the first port 12a may be a separate member from the first pipe joint 12. For example, as shown in fig. 6, the first port 12a may be formed in a side surface of the valve main body 30.
Further, in the above-described embodiment, the description has been given of the case where the fluid flows into the valve chamber 11 in the forward direction through the first port 12a, but the fluid may flow into the valve chamber 11 in the reverse direction through the second pipe joint 15, the seat portion 16, and the second port 16 a. In this case, the fluid also collides with the flat surface portion 17d and the shoulder portion 17e and then turns back downward, or flows from the shoulder portion 17e to the inner side surface of the valve main body 30, thereby avoiding the fluid from flowing into the gap 22 between the valve body portion 20 and the housing chamber 6 h. Then, the fluid collides with the flat surface portion 17d, thereby biasing the valve body portion 20 upward.
In the above-described embodiment, the flat surface portion 17d may not be formed in the lid portion 17 b. For example, as shown in fig. 7, a shoulder 17e may be formed at the boundary between the needle-like portion 17c and the outer peripheral surface of the cap portion 17 b. The shoulder 17e forms an edge of the outer periphery of the base end of the needle-like portion 17c protruding downward of the lid portion 17 b. In this case, the area of the outer peripheral surface of the needle portion 17c is large, and the angle of inclination of the outer peripheral surface with respect to the valve center axis M is large, whereby the fluid is guided in the direction of the inner side surface of the valve main body 30, and the fluid is prevented from flowing into the gap 22.
In the above-described embodiment, the case where the flat surface portion 17d is a flat surface is assumed, but unevenness may be present. The flat surface 17d may not be a plane orthogonal to the valve center axis M, and may be inclined with respect to a plane orthogonal to the valve center axis M.
In the above embodiment, the needle-like portion 17c may have a substantially conical shape with a tapered tip.
In a refrigeration cycle including, for example, a compressor, a condenser, an expansion valve, an evaporator, and the like, the motor-operated valve 2 of the above-described embodiment is used as the expansion valve provided between the condenser and the evaporator.
Claims (7)
1. An electrically operated valve in which a rotary motion of a rotor housed in an inner periphery of a housing is converted into a linear motion by a screw feed mechanism of a male screw member and a female screw member, and a valve body housed in a valve body is moved in a valve center axis direction as a center axis of the valve body based on the linear motion,
the electrically operated valve is characterized by comprising:
a valve chamber which is a space formed in the valve main body;
a first valve port provided on a side surface of the valve main body and serving as an inlet/outlet of the valve chamber side;
a second valve port provided directly below the valve body in a direction coaxial with the valve body, the second valve port being capable of approaching or separating from the valve body;
a cylindrical valve seat portion in which the second valve port is formed on the rotor side; and
a valve shaft holder that guides the valve body portion in the valve center axis direction,
in a state where the valve body portion is closest to the valve seat portion,
the maximum outer diameter of the valve body portion, which has the maximum diameter on the valve seat portion side with respect to the lower end of the valve shaft holder, is larger than the outer diameter of an annular valve seat flat surface portion formed on the top surface of the valve seat portion,
the position of the valve seat plane portion in the valve center axis direction is located closer to the rotor than a lowermost end of the inner diameter of the first valve port which is located farthest from the rotor,
the tapered boundary portion of the portion where the outer periphery of the valve seat portion begins to incline is located closer to the inner bottom surface of the valve chamber than the lowermost end of the inner diameter of the first valve port,
the valve seat portion has a tapered portion whose outer diameter decreases toward the rotor.
2. Electrically operated valve according to claim 1,
the valve core portion includes:
a valve element that adjusts the flow rate of the fluid passing through the second port; and
a valve guide that holds the valve body on the valve seat side and is disposed slidably with respect to the valve shaft holder,
the valve body is fixed to the valve guide.
3. Electrically operated valve according to claim 2,
the valve body includes:
a needle portion which is a portion closest to the second valve port; and
and an annular flat surface portion located on an outer periphery of a base end of the needle portion.
4. An electrically operated valve according to any one of claims 1 to 3,
a shoulder portion forming a lower end edge of the valve body portion having the maximum outer diameter,
in a state where the valve body portion is closest to the valve seat portion, a position of the shoulder portion in the valve center axis direction is located closer to the rotor than an uppermost end of an inner diameter of the first valve port, which is located closest to the rotor.
5. An electrically operated valve according to any one of claims 1 to 3,
the lowermost end of the first valve port is located closer to the rotor than an inner bottom surface in the valve main body.
6. Electrically operated valve according to claim 4,
the lowermost end of the first valve port is located closer to the rotor than an inner bottom surface in the valve main body.
7. A refrigeration cycle system comprises a compressor, a condenser, an expansion valve and an evaporator, and is characterized in that,
an electrically operated valve as claimed in any one of claims 1 to 6 is used as the expansion valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018039422A JP6799024B2 (en) | 2018-03-06 | 2018-03-06 | Solenoid valve and refrigeration cycle system |
| JP2018-039422 | 2018-03-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110230721A CN110230721A (en) | 2019-09-13 |
| CN110230721B true CN110230721B (en) | 2021-08-06 |
Family
ID=67860333
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910118151.XA Active CN110230721B (en) | 2018-03-06 | 2019-02-15 | Electric valve and refrigeration cycle system |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6799024B2 (en) |
| CN (1) | CN110230721B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7271486B2 (en) * | 2020-09-25 | 2023-05-11 | 株式会社鷺宮製作所 | Electric valve and refrigeration cycle system |
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|---|---|---|---|---|
| CN2345806Y (en) * | 1998-05-13 | 1999-10-27 | 朱连生 | Gas cylinder residual-air pressure valve |
| CN102678505A (en) * | 2012-05-19 | 2012-09-19 | 浙江大元泵业有限公司 | Automatic well pump |
| CN202451936U (en) * | 2011-12-02 | 2012-09-26 | 浙江盾安机械有限公司 | Solenoid valve |
| JP2016089870A (en) * | 2014-10-30 | 2016-05-23 | 株式会社鷺宮製作所 | Solenoid valve |
| CN106352616A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Temperature expansion valve and freezing circulation |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59123270U (en) * | 1983-02-07 | 1984-08-20 | 太平洋工業株式会社 | Valve seat shape of expansion valve for heat pump |
| JPH11336918A (en) * | 1998-05-22 | 1999-12-07 | Tosok Corp | Control valve |
| JP4684305B2 (en) * | 2001-09-03 | 2011-05-18 | 株式会社鷺宮製作所 | Motorized valve |
| CN102853126B (en) * | 2011-06-27 | 2015-03-11 | 浙江三花股份有限公司 | Flow control valve |
| JP6410421B2 (en) * | 2013-11-01 | 2018-10-24 | 株式会社不二工機 | Electrically driven valve |
-
2018
- 2018-03-06 JP JP2018039422A patent/JP6799024B2/en active Active
-
2019
- 2019-02-15 CN CN201910118151.XA patent/CN110230721B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2345806Y (en) * | 1998-05-13 | 1999-10-27 | 朱连生 | Gas cylinder residual-air pressure valve |
| CN202451936U (en) * | 2011-12-02 | 2012-09-26 | 浙江盾安机械有限公司 | Solenoid valve |
| CN102678505A (en) * | 2012-05-19 | 2012-09-19 | 浙江大元泵业有限公司 | Automatic well pump |
| JP2016089870A (en) * | 2014-10-30 | 2016-05-23 | 株式会社鷺宮製作所 | Solenoid valve |
| CN106352616A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Temperature expansion valve and freezing circulation |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2019152303A (en) | 2019-09-12 |
| JP6799024B2 (en) | 2020-12-09 |
| CN110230721A (en) | 2019-09-13 |
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