CN111810654A - Electric valve and refrigeration cycle system - Google Patents
Electric valve and refrigeration cycle system Download PDFInfo
- Publication number
- CN111810654A CN111810654A CN202010214506.8A CN202010214506A CN111810654A CN 111810654 A CN111810654 A CN 111810654A CN 202010214506 A CN202010214506 A CN 202010214506A CN 111810654 A CN111810654 A CN 111810654A
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- China
- Prior art keywords
- main valve
- valve
- main
- guide hole
- chamber
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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
- F16K1/02—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 with screw-spindle
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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
- F16K31/04—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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- 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
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
- F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
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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
- F16K31/44—Mechanical actuating means
- F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating means
- F16K31/508—Mechanical actuating means with screw-spindle or internally threaded actuating means the actuating element being rotatable, non-rising, and driving a non-rotatable axially-sliding element
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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
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Lift Valve (AREA)
Abstract
The invention provides an electric valve and a refrigeration cycle system, in the electric valve for controlling flow in a small flow control area and a large flow control area, the full open position of a main valve core 3 is in a preset position in the large flow control area to stabilize the full open flow, and the vibration of the main valve core 3 is prevented and the noise is prevented. The valve device is provided with a main valve body (3) for opening and closing a main valve port (13a), a needle valve (4) for changing the opening degree of a sub valve port (33a) of a sub valve chamber (3R) of the main valve body (3), a main valve spring (3a) for biasing the main valve body (3) toward the main valve port (13a), and a driving part (5) for driving the needle valve (4) to advance and retreat in the direction of an axis (L). A D-shaped cut surface (3a) is formed on a holding portion (32) of a main valve element (3), and a discharge passage (10) for communicating a back pressure chamber (2R) and a main valve chamber (1R) with respect to the main valve element (3) is provided.
Description
Technical Field
The present invention relates to an electrically operated valve used in a refrigeration cycle system or the like and a refrigeration cycle system.
Background
Conventionally, as an electrically operated valve provided in a refrigeration cycle of an air conditioner, there is an electrically operated valve for controlling flow in a small flow control area and a large flow control area. Such an electrically operated valve is used for mounting in an indoor unit (e.g., a dehumidification valve), and is disclosed in, for example, japanese patent application laid-open No. 2000-227165 (patent document 1).
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open No. 2000-227165
Disclosure of Invention
Problems to be solved by the invention
A conventional electric valve (electric control valve) of patent document 1 is configured such that a main valve element is disposed opposite a large-diameter port (main valve port) on a secondary joint pipe side, the main valve element is guided by a sleeve member, and a back pressure chamber is defined between a valve housing (cover member) and the main valve element. The main valve element is biased toward the main valve port by a compression coil spring provided between the pilot valve element and the main valve element. The opening degree of a pilot port (small-diameter port) provided in the main valve body is controlled by the pilot valve body as a small flow rate control region. Although not described in detail in patent document 1, such an electrically operated valve is used in an indoor unit as a dehumidification valve of a refrigeration cycle, and has a structure in which a large-diameter port is opened by raising a main valve, and a large flow rate of fluid (refrigerant) flows from the large-diameter port side as a large flow rate control region during a heating operation, for example.
However, in such a state of the large flow rate control region during the heating operation, the pressure of the fluid flowing from the large-diameter port raises the main valve element, but the pressure and the main valve spring load cause vibration in the main valve element, and the full-open flow rate during the heating operation varies due to variation in the full-open position of the main valve element, and it is difficult to perform stable control. In addition, there is a problem that noise is generated due to vibration of the main spool.
The subject of the invention is to prevent the vibration of a main valve core in a large flow control area, stabilize the main valve core at a full-open position, stabilize the full-open flow and prevent noise in an electric valve for controlling flow in a small flow control area and a large flow control area.
Means for solving the problems
The motor-operated valve of the present invention comprises: a valve housing which houses the main valve chamber therein; and a housing joined to an upper portion of the valve housing and accommodating the magnetic rotor therein, the housing having a first joint pipe for fluid inlet and outlet opened to the main valve chamber on a side surface of the valve housing and a second joint pipe for fluid inlet and outlet connected to a main valve port provided at a lower portion of the valve housing, the electric valve including: a main valve body for opening and closing a main valve port of the main valve chamber; 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; a main valve spring that biases the main valve element from a back pressure chamber side of the main valve element to the main valve port side; and a drive unit that drives the sub-valve element to advance and retreat in the axial direction, and that has two-stage flow control regions including a small flow control region and a large flow control region, wherein the small flow control region is: the sub valve body is slidably inserted into a sub valve guide hole of the main valve body in the axial direction, and changes an opening degree of the sub valve port in a state where the main valve body closes the main valve port, and the large flow rate control region is: the main valve element is configured to be in a fully open state at the main valve port, and to flow a large flow rate of fluid flowing from the main valve port from the main valve chamber to a side port, and the electric valve is characterized by being provided with a discharge passage which communicates the back pressure chamber with the main valve chamber and has an opening area larger than a cross-sectional area of a gap between the main valve element and the sub valve element in the sub valve guide hole, the cross-sectional area being orthogonal to the axis.
According to the present invention, even when a high-pressure fluid from the main valve port side flows into the back pressure chamber from the gap between the main valve element and the sub valve guide hole, the high-pressure fluid in the back pressure chamber can be discharged from the discharge pressure passage to the main valve chamber. Further, since the opening area of the discharge passage is larger than the cross-sectional area of the gap, the high-pressure fluid in the back pressure chamber can be quickly discharged to the main valve chamber. Therefore, if the pressure in the back pressure chamber becomes too high, the main valve spring is less likely to be compressed by the main valve spool, and the behavior of the main valve spool becomes unstable and vibration occurs. However, according to the present invention, since the high-pressure fluid in the back pressure chamber can be quickly discharged to the main valve chamber, the main valve spring can be quickly brought into a stable compressed state, the vibration of the main valve body can be prevented in the large flow rate control region to stabilize the full open position, the full open flow rate can be stabilized, and noise due to the vibration can be prevented.
Preferably, the valve device further includes a guide member that guides the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the discharge passage is formed between a D-shaped cut surface on a side portion of the main valve element and an inner circumferential surface of the main valve guide hole.
Preferably, the valve device further includes a guide member that guides the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the relief pressure passage is formed by a groove parallel to the axis in an inner periphery of the main valve guide hole.
Preferably, the valve device further includes a guide member that guides the main spool in the axial direction by inserting the main spool into a main-valve guide hole, and the pressure release path is formed by a groove parallel to the axis on the outer periphery of the main spool.
Preferably, the valve device further includes a guide member that guides the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the pressure release path is formed by a gap between a side portion of the main valve element and an inner peripheral surface of the main valve guide hole.
Preferably, the valve device further includes a guide member that guides the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the pressure release path is formed by a through hole that communicates an upper portion of the main valve guide hole with the inside of the housing.
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.
Further, a refrigeration cycle system of the present invention includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, and an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and is characterized in that the electric valve described in any one of the above is used as the electronic expansion valve.
According to such a refrigeration cycle system, as well as the effect of the motor-operated valve described above during heating operation, it is possible to perform stable control of the full opening flow rate and to configure a system capable of preventing noise.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the electric valve and the refrigeration cycle system of the present invention, in the electric valve having the two-stage flow rate control region, the full open flow rate of the fluid can be stabilized, and noise can be prevented.
Drawings
Fig. 1 is a longitudinal sectional view showing a state of a small flow rate control region of an electric valve according to a first embodiment of the present invention.
Fig. 2 is a vertical cross-sectional view of the main valve element of the motor-operated valve according to the first embodiment during heating operation in the fully open state.
Fig. 3 is a plan cross-sectional view (cross-sectional view a-a in fig. 2) of the main valve body of the motor-operated valve according to the first embodiment during a heating operation in a fully open state.
Fig. 4 (a) is a vertical sectional view during heating operation in the fully open state of the main valve element of the motor-operated valve according to the second embodiment of the present invention, and (B) is a plan sectional view (sectional view a-a).
Fig. 5 (a) is a vertical sectional view during heating operation in the fully open state of the main valve element of the motor-operated valve according to the third embodiment of the present invention, and (B) is a plan sectional view (sectional view a-a).
Fig. 6 (a) is a vertical sectional view during heating operation in a fully open state of a main valve element of a motor-operated valve according to a fourth embodiment of the present invention, and (B) is a plan sectional view (sectional view a-a).
Fig. 7 is a vertical cross-sectional view of a main valve element of a motor-operated valve according to a fifth embodiment of the present invention during heating operation in a fully open state.
Fig. 8 is a vertical cross-sectional view of a main valve element of a motor-operated valve according to a sixth embodiment of the present invention during heating operation in a fully open state.
Fig. 9 is a diagram showing a refrigeration cycle system according to an embodiment of the present invention.
In the figure:
1-a valve housing, 1R-a main valve chamber, 11-a first joint pipe, 12-a second joint pipe, 13-a main valve seat, 13 a-a main valve port, 14-a housing, L-an axis, 2-a guide member, 2A-a main valve guide hole, 2R-a back pressure chamber, 21-a press-in portion, 22-an upper guide portion, 22A-a via hole, 23-a lower guide portion, 24-a holder portion, 24 a-an internal thread portion, 25-a flange portion, 3-a main valve spool, 3 a-a D-shaped cut surface, 3R-a sub valve chamber, 31-a main valve portion, 32-a holding portion, 32A-a needle valve guide hole (sub valve guide hole), 32B-a via hole, 33-a sub valve seat, 33 a-a sub valve port, 34-a holder, 35-a main valve spring, 4-a needle valve (sub valve spool), 41-a needle portion, 42-a washer, 43-a guide boss, 5-a drive portion, 5A step motor, 5B-a screw feed mechanism, 5C-limit mechanism, 51-rotor shaft, 51 a-external thread portion, 52-magnetic rotor, 52 a-protrusion portion, 53-stator coil, 10-discharge passage, 20-discharge passage, 30-discharge passage, 91-first indoor side heat exchanger, 92-second indoor side heat exchanger, 93-electronic expansion valve, 94-outdoor side heat exchanger, 95-compressor, 96-four-way valve, 100-electric valve.
Detailed Description
Embodiments of an electric valve and a refrigeration cycle system according to the present invention will be described below with reference to the drawings. Fig. 1 is a vertical cross-sectional view of a small flow rate control region state of an electric valve of a first embodiment, fig. 2 is a vertical cross-sectional view during a heating operation in a fully open state of a main valve element of the electric valve of the first embodiment, fig. 3 is a plan cross-sectional view during the heating operation in the fully open state of the main valve element of the electric valve of the first embodiment, and fig. 3 is a cross-sectional view a-a of fig. 2. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawings of fig. 1 and 2. The motor-operated valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "sub valve body", and a drive unit 5.
The valve housing 1 is formed into a substantially cylindrical shape, for example, from brass, stainless steel, or the like, and has a main valve chamber 1R inside thereof. A first joint pipe 11 that communicates with the main valve chamber 1R is connected to one side of the outer periphery of the valve housing 1, and a second joint pipe 12 is connected to a cylindrical portion that extends downward from the lower end. A cylindrical main valve seat 13 is formed on the valve housing 1 on the main valve chamber 1R side of the second joint pipe 12, the inner side of the main valve seat 13 is a main valve port 13a, and the second joint pipe 12 is communicated with the main valve chamber 1R through the main valve port 13 a. The main valve port 13a is a cylindrical through hole (through hole) centered on the axis L. The first joint pipe 11 and the second joint pipe 12 are fastened to the valve housing 1 by brazing or the like.
A guide member 2 is attached to an opening portion at the upper end of the valve housing 1. The guide member 2 has: a press-in portion 21 press-fitted into the inner peripheral surface of the valve housing 1; substantially columnar guides 22, 23 having a smaller diameter than the press-fitting portion 21 and located above and below the press-fitting portion 21; a bracket part 24 extending from the upper part of the guide part 22; and an annular flange 25 provided on the outer periphery of the press-fitting portion 21. The press-fitting portion 21, the guide portions 22 and 23, and the holder portion 24 are formed as a single resin member. The flange portion 25 is a metal plate such as brass or stainless steel, for example, and the flange portion 25 is integrated with the resin press-fitting portion 21 by insert molding.
The guide member 2 is assembled to the valve housing 1 by the press-fitting portion 21, and is fixed to the upper end portion of the valve housing 1 by welding via the flange portion 25. In the guide member 2, a cylindrical main valve guide hole 2A coaxial with the axis L is formed inside the press-fitting portion 21 and the upper and lower guide portions 22 and 23, and a female screw portion 24a coaxial with the main valve guide hole 2A and a screw hole thereof are formed in the center of the bracket portion 24. The main valve element 3 is disposed inside the lower guide portion 23 and inside the main valve guide hole 2A.
A main valve spring 35 is disposed between the retainer 34 and the upper end portion of the main valve guide hole 2A, and the main valve spring 35 biases the main valve body 3 in the direction of the main valve seat 13 (closing direction). A cylindrical sub-valve port 33a centered on the axis L is formed in the center of the sub-valve seat 33. Further, a through hole 32b that communicates the sub-valve chamber 3R with the main valve chamber 1R is formed in at least one portion of the side surface of the holding portion 32, and when the needle valve 4 serving as a sub-valve body opens the sub-valve port 33a, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a communicate with each other.
The needle valve 4 is integrally provided with a truncated cone-shaped needle portion 41, and the truncated cone-shaped needle portion 41 is integrally formed with a rotor shaft 51 described later at a lower end portion of the rotor shaft 51, and has a diameter gradually decreasing toward a tip end continuous to the rotor shaft 51 side. The needle valve 4 includes an annular washer 42 made of a lubricating resin and attached to the rotor shaft 51, and a guide boss 43 formed integrally with the rotor shaft 51. The washer 42 and the guide boss 43 are slidably inserted into the needle valve guide hole 32 a. That is, a predetermined gap is provided between the outer periphery of the washer 42 and the inner periphery of the needle guide hole 32 a.
The housing 14 is hermetically fixed to the upper end of the valve housing 1 by welding or the like, and the driving portion 5 is formed inside and outside the housing 14. The drive unit 5 includes a stepping motor 5A, a thread feed mechanism 5B that advances and retracts the needle valve 4 by rotation of the stepping motor 5A, and a stopper mechanism 5C that restricts rotation of the stepping motor 5A.
The stepping motor 5A is constituted by: a rotor shaft 51; a magnetic rotor 52 rotatably disposed inside the housing 14; a stator coil 53 disposed on the outer periphery of the housing 14 so as to face the magnetic rotor 52; and other unshown magnetic yokes, exterior members, and the like. The rotor shaft 51 is attached to the center of the magnetic rotor 52 via a bushing, and a male screw portion 51a is formed on the outer periphery of the rotor shaft 51 on the guide member 2 side. The male screw portion 51a is screwed into the female screw portion 24a of the guide member 2, whereby the guide member 2 supports the rotor shaft 51 on the axis L. The female screw portion 24a of the guide member 2 and the male screw portion 51a of the rotor shaft 51 constitute a screw feeding mechanism 5B.
According to the above configuration, when the stepping motor 5A is driven, the magnetic rotor 52 and the rotor shaft 51 rotate, and the rotor shaft 51 moves in the axis L direction together with the magnetic rotor 52 by the screw feeding mechanism 5B in which the male screw portion 51a of the rotor shaft 51 and the female screw portion 24a of the guide member 2. The needle valve 4 moves forward and backward in the direction of the axis L, and the needle valve 4 approaches or separates from the sub-valve port 33 a. When the needle 4 is lifted, the washer 42 engages with the holder 34 of the main valve 3, and the main valve 3 moves together with the needle 4 and is unseated from the main valve seat 13. The magnetic rotor 52 is provided with a projection 52a, and the projection 52a operates the rotation restricting mechanism 5C to restrict the lowermost end position and the uppermost end position of the rotor shaft 51 (and the magnetic rotor 52) in accordance with the rotation of the magnetic rotor 52.
In the small flow rate control area state of fig. 1, in a state where the main valve body 3 is seated on the main valve seat 13, the main valve port 13a is closed, and the opening degree of the sub valve port 33a is controlled by the needle valve 4, thereby controlling the small flow rate. For example, when the needle valve 4 and the main valve element 3 are lifted in a state where the compressor of the refrigeration cycle is stopped and the fluid (refrigerant) is stopped, the main valve port 13a is in a fully open state as shown in fig. 2. Thus, during the heating operation in which the refrigerant flows in the direction of the broken-line arrow shown in the refrigeration cycle of fig. 6, a large flow of fluid (refrigerant) flows from the second joint pipe 12 to the first joint pipe 11 of the electric valve 100.
The main valve body 3 is disposed in a main valve guide hole 2A of the guide member 2, and an upper space of the main valve body 3 in the main valve guide hole 2A becomes a back pressure chamber 2R with respect to the main valve body 3. As shown in fig. 2 and 3, a D-shaped cut surface 3a parallel to the axis L is formed at one position on the outer periphery of the holding portion 32 of the main valve spool 3, and a pressure discharge passage 10 for communicating the back pressure chamber 2R and the main valve chamber 1R is formed between the main valve guide hole 2A and the D-shaped cut surface 3 a. The cross-sectional area of the pressure discharge passage 10 perpendicular to the axis L, that is, the opening area, is larger than the smaller cross-sectional area (referred to as the gap cross-sectional area of the needle valve portion) of the cross-sectional area of the gap of the guide boss portion 43 or the washer 42 of the needle valve 4 (sub-valve body) perpendicular to the axis L in the needle valve guide hole 32a (sub-valve guide hole).
When a large flow rate of fluid flows from the second joint pipe 12 in the state of fig. 2 as a heating operation, the high-pressure fluid flows into the back pressure chamber 2R through the gap between the needle guide hole 32a and the guide boss 43 of the needle 4 and the washer 42, but the fluid in the back pressure chamber 2R is discharged to the main valve chamber 1R through the discharge passage 10. Since the cross-sectional area of the exhaust passage 10 is larger than the cross-sectional area of the gap of the needle portion, the back pressure chamber 2R does not generate a high pressure, but a high pressure acts on the lower portion of the main valve body 3, and a lower pressure acts on the upper portion of the back pressure chamber side of the main valve body 3 than on the lower portion of the main valve body 3. Therefore, the main valve spool 3 is raised against the biasing force of the main valve spring 35 by the pressure difference of the fluid acting on the upper and lower sides of the main valve spool 3, and the main valve spring 35 is held in a state of not being fully compressed at the position of the main valve spool 3 in the axis L direction, that is, the fully open position. In this embodiment, a through hole 22a for conducting the back pressure chamber 2R and the inside of the housing 14 is formed in at least one portion of the side surface of the guide portion 22 of the guide member 2. As shown in fig. 3, a through hole 25a for conducting the main valve chamber 1R and the inside of the housing 14 is formed in the flange portion 25 of the guide member 2. The back pressure chamber 2R and the main valve chamber 1R are also communicated through the through hole 22a, the inside of the housing 14, and the through hole 25 a.
As described above, the main valve spool 3 is raised by the high-pressure fluid from the main valve port 13a side, and the main valve spring 35 is compressed and held at the predetermined position, so that the full open position of the main valve spool 3 is stabilized at the predetermined position, and therefore the flow rate of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 (full open flow rate) is stabilized. In addition, since vibration of main valve element 3 is prevented, noise can be prevented.
Fig. 4, 5 and 6 (a) are vertical sectional views and (B) are plan sectional views (a-a sectional views) of the main valve element of the motor-operated valve according to the second, third and fourth embodiments of the present invention during the heating operation in the fully open state. Note that, in the following second, third, and fourth embodiments, the configuration of the pressure release path is different from that of the first embodiment, and the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 1 to 3, and overlapping descriptions are appropriately omitted.
In the second embodiment of fig. 4, in the guide member 2, grooves parallel to the axis L are formed at two locations on the inner peripheral surface of the main valve guide hole 2A of the upper and lower guide portions 22 and 23 and the press-fitting portion 21, and cutouts are formed at two locations on the flange portion 25 corresponding to the grooves, thereby forming the pressure discharge passages 20 and 20 for conducting the back pressure chamber 2R and the main valve chamber 1R. The cross-sectional area of the groove perpendicular to the axis L is larger than the gap cross-sectional area of the needle valve portion.
In the second embodiment, although the high-pressure fluid flows into the back pressure chamber 2R through the gap between the needle guide hole 32a and the guide boss 43 and the washer 42 of the needle 4, the fluid in the back pressure chamber 2R is discharged to the main valve chamber 1R through the discharge passage 20. Therefore, as in the first embodiment, since the main valve spool 3 is raised by the high-pressure fluid from the main valve port 13a side without the back pressure chamber 2R becoming high-pressure and the main valve spring 35 is compressed and held at the predetermined position, the full open position of the main valve spool 3 is stabilized at the predetermined position, and thus the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. In addition, since vibration of main valve element 3 is prevented, noise can be prevented.
In the third embodiment of fig. 5, grooves parallel to the axis L are formed at two locations on the outer peripheral surface of the main valve element 3, thereby forming the exhaust pressure passages 20 ', 20' that communicate the back pressure chamber 2R with the main valve chamber 1R. The cross-sectional area of the groove perpendicular to the axis L is larger than the gap cross-sectional area of the needle valve portion.
In the third embodiment, although the high-pressure fluid flows into the back pressure chamber 2R through the gap between the needle guide hole 32a and the guide boss 43 and the washer 42 of the needle 4, the fluid in the back pressure chamber 2R is discharged to the main valve chamber 1R through the discharge passage 20'. Therefore, as in the first embodiment, since the main valve spool 3 is raised by the high-pressure fluid from the main valve port 13a side without the back pressure chamber 2R becoming high-pressure and the main valve spring 35 is compressed and held at the predetermined position, the full open position of the main valve spool 3 is stabilized at the predetermined position, and thus the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. In addition, since vibration of main valve element 3 is prevented, noise can be prevented.
In the fourth embodiment of fig. 6, the diameter of the inner periphery of the main valve guide hole 2A, which penetrates the upper and lower guide portions 22 and 23 and the press-fitting portion 21 in the guide member 2, is made slightly larger than that of the first embodiment, and a pressure release passage 30, which communicates the back pressure chamber 2R and the main valve chamber 1R, is formed between the main valve guide hole 2A and the outer periphery of the holding portion 32 of the main valve element 3.
In the fourth embodiment, although the high-pressure fluid flows into the back pressure chamber 2R through the gap between the needle guide hole 32a and the guide boss 43 and the washer 42 of the needle 4, the fluid in the back pressure chamber 2R is discharged to the main valve chamber 1R through the discharge passage 30. Therefore, as in the first embodiment, since the main valve spool 3 is raised by the high-pressure fluid from the main valve port 13a side without the back pressure chamber 2R becoming high-pressure and the main valve spring 35 is compressed and held at the predetermined position, the full open position of the main valve spool 3 is stabilized at the predetermined position, and thus the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. In addition, since vibration of main valve element 3 is prevented, noise can be prevented.
Fig. 7 and 8 are vertical sectional views of the main valve element of the motor-operated valve according to the fifth and sixth embodiments of the present invention during heating operation in the fully open state. In the following fifth and sixth embodiments, the configuration of the pressure discharge path is different from that of the first embodiment, and the same elements as those of the first embodiment are denoted by the same reference numerals as those of fig. 2, and overlapping descriptions are omitted as appropriate.
In the fifth embodiment of fig. 7, the inner diameter of a through hole 22 a' that communicates the back pressure chamber 2R with the inside of the housing 14 in the guide portion 22 on the upper side of the guide member 2 is made larger than that in the first embodiment, and a road drainage is formed. The flow passage cross-sectional area of the through hole 22 a' is larger than the gap cross-sectional area of the needle valve.
In the sixth embodiment of fig. 8, a plurality of (two in the figure) through holes 22a ″ that communicate the back pressure chamber 2R with the inside of the housing 14 are provided in the guide portion 22 on the upper side of the guide member 2 to form a passage. The sum of the channel cross-sectional areas of the plurality of through holes 22a ″ is larger than the gap cross-sectional area of the needle valve portion.
In the fifth and sixth embodiments, the high-pressure fluid also flows into the back pressure chamber 2R through the gap between the needle guide hole 32a and the guide boss 43 of the needle 4 and the washer 42, but the fluid in the back pressure chamber 2R is discharged from the housing 14 to the main valve chamber 1R through the communication passage 22 a' or 22a ″ serving as a discharge passage through the communication hole 25a of the flange 25. Therefore, as in the first embodiment, since the main valve spool 3 is raised by the high-pressure fluid from the main valve port 13a side without the back pressure chamber 2R becoming high-pressure and the main valve spring 35 is compressed and held at the predetermined position, the full open position of the main valve spool 3 is stabilized at the predetermined position, and thus the flow rate (full open flow rate) of the fluid flowing from the second joint pipe 12 to the first joint pipe 11 is stabilized. In addition, since vibration of main valve element 3 is prevented, noise can be prevented.
The refrigeration cycle system of the present invention will be described below with reference to fig. 9. The refrigeration cycle is used for, for example, an air conditioner such as a household air conditioner. The motor-operated valve 100 of each of the embodiments described above is provided between the first indoor-side heat exchanger 91 (which operates as a cooler during dehumidification) and the second indoor-side heat exchanger 92 (which operates as a heater during dehumidification) of the air conditioner, and constitutes a heat pump refrigeration cycle together with the compressor 95, the four-way valve 96, the outdoor-side heat exchanger 94, and the electronic expansion valve 93. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated valve 100 are installed indoors, and the compressor 95, the four-way valve 96, the outdoor heat exchanger 94, and the electronic expansion valve 93 are installed outdoors to constitute a cooling/heating apparatus.
The motor-operated valve 100 as the embodiment of the dehumidification valve is configured to fully open the main valve body at the time of cooling or heating other than the time of dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are one indoor heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 function alternatively as an "evaporator" and a "condenser". That is, the electric valve 93 serving as an electronic expansion valve is provided between the evaporator and the condenser.
The refrigeration cycle described above is an example in which the motor-operated valve of the present invention is used as the dehumidification valve, but the motor-operated valve of the present invention can also be applied to the motor-operated valve 93 which is the above-described electronic expansion valve. In this case, the dehumidification valve may be present or absent.
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 modifications and the like as described below are also included in the present invention. For example, in the above-described embodiment, the motor-operated valve 100 used for an air conditioner such as a home air conditioner is exemplified, but the motor-operated valve of the present invention is not limited to the home air conditioner, and may be a service air conditioner, and may be applied to various refrigerators and the like as well as the air conditioner.
Although the embodiments of the present invention have been described in detail with reference to the drawings, and other embodiments have been described in detail, the specific configurations are not limited to these embodiments, and design changes and the like that do not depart from the spirit and scope of the present invention are also included in the present invention.
Claims (8)
1. An electrically operated valve, comprising: a valve housing which houses the main valve chamber therein; and a housing which is joined to an upper portion of the valve housing and which accommodates the magnetic rotor therein,
a first joint pipe for fluid inlet and outlet opened to the main valve chamber is provided on a side surface of the valve housing, and a second joint pipe for fluid inlet and outlet connected to a main valve port provided in a lower portion of the valve housing,
the electrically operated valve includes: a main valve body for opening and closing a main valve port of the main valve chamber; 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; a main valve spring that biases the main valve element from a back pressure chamber side of the main valve element to the main valve port side; and a driving part which drives the auxiliary valve core to advance and retreat in the axial direction,
a two-stage flow control zone having a small flow control zone and a large flow control zone, wherein the small flow control zone is: the sub valve body is slidably inserted into a sub valve guide hole of the main valve body in the axial direction, and changes an opening degree of the sub valve port in a state where the main valve body closes the main valve port, and the large flow rate control region is: the main valve body is configured to have the main valve port in a fully open state, and to allow a large flow rate of fluid flowing from the main valve port to flow from the main valve chamber to a side port,
the above-mentioned electric valve is characterized in that,
the valve device is provided with a discharge passage which communicates the back pressure chamber with the main valve chamber and has an opening area larger than a cross-sectional area of a gap between the main valve element and the sub valve element in the sub valve guide hole, the cross-sectional area being orthogonal to the axis.
2. Electrically operated valve according to claim 1,
the valve device is provided with a guide member for guiding the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the discharge passage is formed between a D-shaped cut surface on a side of the main valve element and an inner peripheral surface of the main valve guide hole.
3. Electrically operated valve according to claim 1,
the main valve device is provided with a guide member for guiding the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the relief pressure passage is formed by a groove parallel to the axis in the inner periphery of the main valve guide hole.
4. Electrically operated valve according to claim 1,
the valve device is provided with a guide member for guiding the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the pressure release path is formed by a groove parallel to the axis on the outer periphery of the main valve element.
5. Electrically operated valve according to claim 1,
the valve device is provided with a guide member for guiding the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the pressure release path is formed by a gap between a side portion of the main valve element and an inner peripheral surface of the main valve guide hole.
6. Electrically operated valve according to claim 1,
the main valve device is provided with a guide member for guiding the main valve element in the axial direction by inserting the main valve element into a main valve guide hole, and the pressure release path is formed by a through hole for communicating an upper portion of the main valve guide hole with the inside of the housing.
7. 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,
the above-described refrigeration cycle system is characterized in that,
use of an electrically operated valve as claimed in any one of claims 1 to 6 as the above-mentioned dehumidification valve.
8. A refrigeration cycle system comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and an electronic expansion valve arranged between the indoor heat exchanger and the outdoor heat exchanger,
the above-described refrigeration cycle system is characterized in that,
use of an electrically operated valve as claimed in any one of claims 1 to 6 as said electronic expansion valve.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210803825.1A CN115076379A (en) | 2019-04-12 | 2020-03-24 | Electric valve and refrigeration cycle system |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2019-076311 | 2019-04-12 | ||
| JP2019076311A JP7055768B2 (en) | 2019-04-12 | 2019-04-12 | Solenoid valve and refrigeration cycle system |
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| CN202210803825.1A Division CN115076379A (en) | 2019-04-12 | 2020-03-24 | Electric valve and refrigeration cycle system |
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| CN111810654A true CN111810654A (en) | 2020-10-23 |
| CN111810654B CN111810654B (en) | 2022-06-17 |
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| CN202010214506.8A Active CN111810654B (en) | 2019-04-12 | 2020-03-24 | Electric valve and refrigeration cycle system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114562602A (en) * | 2020-11-27 | 2022-05-31 | 株式会社鹭宫制作所 | Electric valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112923070A (en) * | 2021-01-22 | 2021-06-08 | 浙江恒森实业集团有限公司 | Electronic expansion valve assembly with good noise reduction stability |
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- 2020-03-24 CN CN202010214506.8A patent/CN111810654B/en active Active
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2022095807A (en) | 2022-06-28 |
| JP2020173003A (en) | 2020-10-22 |
| CN111810654B (en) | 2022-06-17 |
| JP7055768B2 (en) | 2022-04-18 |
| CN115076379A (en) | 2022-09-20 |
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