CN114857288A - Electric valve and refrigeration cycle system - Google Patents
Electric valve and refrigeration cycle system Download PDFInfo
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- CN114857288A CN114857288A CN202210643214.5A CN202210643214A CN114857288A CN 114857288 A CN114857288 A CN 114857288A CN 202210643214 A CN202210643214 A CN 202210643214A CN 114857288 A CN114857288 A CN 114857288A
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- valve
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 18
- 239000003507 refrigerant Substances 0.000 claims description 10
- 238000007791 dehumidification Methods 0.000 claims description 9
- 230000003247 decreasing effect Effects 0.000 claims 1
- 230000007423 decrease Effects 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 6
- 230000002093 peripheral effect Effects 0.000 description 5
- 238000003466 welding Methods 0.000 description 5
- 229910001369 Brass Inorganic materials 0.000 description 4
- 239000010951 brass Substances 0.000 description 4
- 239000011347 resin Substances 0.000 description 4
- 229920005989 resin Polymers 0.000 description 4
- 229910001220 stainless steel Inorganic materials 0.000 description 4
- 239000010935 stainless steel Substances 0.000 description 4
- 238000013459 approach Methods 0.000 description 2
- 238000005219 brazing Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
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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
- F16K1/385—Valve members of conical shape contacting in the closed position, over a substantial axial length, a seat surface having the same inclination
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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
- F16K1/44—Details of seats or valve members of double-seat valves
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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
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
- F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
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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 small flow rate by a needle valve (4), the deviation of the maximum flow rate in a small flow rate control area is restrained, and the controllable range in the small flow rate control area is made to be a large range. A needle valve (4) having a second conical surface section (44) whose diameter gradually decreases toward the tip is arranged on the axis L of the sub-valve port (33 a). The needle valve (4) is moved back and forth on the axis by a drive unit (5). A small flow control area is obtained by the needle valve (4) and the sub-valve port (33 a). A large flow control area is obtained by the main valve core (3) and the main valve port (13 a). A second straight line part (45) with a constant diameter is provided, which is connected to the minimum diameter part of a second conical table part (44) of the needle valve (4). The second straight line section (45) is held in the sub-valve port (33a) at a position where the second conical surface section (44) is removed from the sub-valve port (33 a).
Description
The invention is a divisional application with the application number of 201910749370.8, the name of the invention is electric valve and refrigeration cycle system, and the application date is 2019, 8 months and 14 days.
Technical Field
The present invention relates to an electrically operated valve used in a refrigeration cycle or the like and a refrigeration cycle.
Background
Currently, as an electrically operated valve provided in a refrigeration cycle of an air conditioner, for example, an electrically operated valve disclosed in japanese patent No. 2898906 (patent document 1) is known. The motor-operated valve is provided with: a main valve body (second valve body) for changing the opening of a main valve port (large diameter valve port) of the valve chamber; an auxiliary valve body (first valve body) for changing the opening degree of an auxiliary valve port (small diameter valve port) formed in the main valve body; and a drive unit for driving an electric motor (stepping motor) for driving the sub-valve body.
Fig. 12 is a diagram showing a relationship (flow rate characteristic) between a drive pulse of an electric motor (a lift amount of a sub valve body) and a flow rate of a refrigerant flowing through an electric valve in the electric valve. In this motor-operated valve, the sub-valve body is driven by the electric motor to change the opening degree of the sub-valve port in a state where the main valve body is seated to close the main valve port, and at this time, the opening degree of the sub-valve port is controlled by a drive pulse of the electric motor, so that a flow rate characteristic in a small flow rate control region is obtained as shown in fig. 12. Then, the sub valve body is lifted by the driving of the electric motor, the sub valve body engages with the main valve body, and the main valve body is lifted together with the sub valve body to open the main valve port, and the opening degree of the main valve port is changed by the main valve body, thereby obtaining a flow rate characteristic which becomes a large flow rate control region as shown in fig. 12. Thus, the electric valve has two stages of a small flow control region and a large flow control region.
Documents of the prior art
Patent document
Patent document 1: japanese patent No. 2898906
Disclosure of Invention
Problems to be solved by the invention
In a conventional motor-operated valve, among a plurality of motor-operated valves, for example, in a motor-operated valve manufactured so as to have a target flow rate characteristic shown by a solid line in fig. 13, the flow rate characteristic varies due to variations in component size and the like. The range of this variation depends on the influence of dimensional tolerance, assembly tolerance, and the like of the components, but in the example of fig. 13, for example, the flow rate characteristic is an upper limit indicated by a dotted line and a lower limit indicated by a broken line with respect to the flow rate characteristic at the center indicated by a solid line. In the flow rate characteristics, an inflection point is present at the boundary between the small flow rate control region and the large flow rate control region, and a deviation occurs at the position of the inflection point. Therefore, in order to perform the pulse control of the motor-operated valve, it is necessary to set a drive pulse smaller than the drive pulse (point a in fig. 13) in which the upper limit of the drive pulse in the small flow rate control region is the minimum as the upper limit in the deviation range, and set the range up to the upper limit as the small flow rate controllable range actually used for the small flow rate control.
Further, the flow rate also varies at the point a in fig. 13, and for example, at the upper limit of the flow rate characteristic (the flow rate characteristic of the dotted line), the valve opening degree is too large, and the flow rate may not be reduced completely. Therefore, it is necessary to set the upper limit of the range for controlling the small flow rate to be lower than the point a and to set the range as the range for controlling the small flow rate. Thus, in the conventional motor-operated valve, the range in which control can be performed at a small flow rate has to be narrowed. This is not limited to the two-stage control by the main valve element and the sub valve element, but is also a problem in an electrically operated valve in which the flow rate is controlled by the land portion of the needle valve. For example, the deviation of the maximum flow rate in the small flow rate control region becomes large, and the flow rate may not be reduced completely, and it is necessary to reduce the range of the drive pulse used for controlling the small flow rate in the small flow rate control region, that is, the minute flow rate controllable range, in consideration of the deviation of the flow rate.
The subject of the invention is: in an electrically operated valve for controlling a small flow rate by a needle valve, a small flow rate controllable range actually used for the small flow rate control is set to a wide range while suppressing a variation in the maximum flow rate in a small flow rate control region.
Means for solving the problems
In the electrically operated valve according to claim 1, a needle valve having a truncated cone-shaped truncated cone portion whose diameter gradually decreases toward a tip of a small-diameter valve port side is arranged on an axis of the small-diameter valve port, the needle valve is advanced and retreated in the axial direction by converting a rotational motion of a rotor of an electric motor into a linear motion by a screw feed mechanism, and a flow rate of a refrigerant is controlled according to an opening area of a gap between an opening portion of the small-diameter valve port and at least the truncated cone portion of the needle valve, and the electrically operated valve is characterized in that the needle valve has a straight portion of a constant diameter connected to a minimum diameter portion of the truncated cone portion, and the straight portion is held in the small-diameter valve port at a position where the minimum diameter portion of the truncated cone portion is separated from the small-diameter valve port in the axial direction.
The electrically operated valve of claim 2 is characterized by comprising a main valve body that changes an opening degree of a main valve port of a valve chamber, the main valve body being formed with the small-diameter valve port, the needle valve having a two-stage flow rate control region of a small flow rate control region in which the needle valve changes the opening degree of the small-diameter valve port, and a large flow rate control region in which the main valve body changes the opening degree of the main valve port, the needle valve being configured to engage with the main valve body at a position where the minimum diameter portion of the conical table portion is disengaged from the small-diameter valve port, and the main valve body moving integrally with the needle valve to change the opening degree of the main valve port in an engaged state with the needle valve.
The refrigeration cycle system according to claim 3 includes a compressor, a condenser, an evaporator, and an electronic expansion valve provided between the condenser and the evaporator, and is characterized in that the electronic expansion valve is an electrically operated valve as described in claim 1.
The refrigeration cycle system according to claim 4 is characterized in that the motor-operated valve described in claim 2 is used as the dehumidification valve, and the refrigeration cycle system 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.
The effects of the invention are as follows.
The motor-operated valve according to claim 1 or 2 controls the flow rate of the refrigerant in the small flow rate control region in accordance with the opening area of the gap between the opening portion of the small-diameter valve port and the conical surface portion of the needle valve, and the needle valve has a straight portion of constant diameter connected to the minimum diameter portion of the conical surface portion, and the straight portion is held in the small-diameter valve port at a position where the minimum diameter portion of the conical surface portion comes out of the small-diameter valve port, and changes from the terminal end of the small flow rate control region to the constant flow rate region. Therefore, it is possible to suppress the variation of the maximum flow rate in the small flow rate control region, prevent the phenomenon that the flow rate of the maximum flow rate cannot be reduced, and make the range of the drive pulse actually used for the control of the small flow rate, that is, the small flow rate controllable range, a wide range, and improve the controllability of the small flow rate controllable range.
According to the refrigeration cycle system of the embodiment 3 or 4, the same effect as that of the embodiment 1 or 2 is obtained.
Drawings
Fig. 1 is a longitudinal sectional view of an electric valve according to a first embodiment of the present invention.
Fig. 2 is an enlarged cross-sectional view of a main portion of the needle valve in the electric valve of the first embodiment at a position closest to the sub-valve port.
Fig. 3 is an enlarged cross-sectional view of a main portion of the electric valve according to the first embodiment, in which the needle valve is located between a position closest to the sub-valve port and a position engaged with the main spool.
Fig. 4 is an enlarged cross-sectional view of a main portion of the electric valve according to the first embodiment when the needle valve is in a position of engaging with the main valve body.
Fig. 5 is an enlarged sectional view of a main portion showing a fully opened state of a main valve element in the motor-operated valve of the first embodiment.
Fig. 6 is a diagram showing the relationship between the pulse amount and the flow rate of the drive pulse in the motor-operated valve according to the first embodiment.
Fig. 7 is a longitudinal sectional view of an electric valve according to a second embodiment of the present invention.
Fig. 8 is an enlarged sectional view of a main portion showing a needle valve corresponding to the lowermost end position of the magnetic rotor in the second embodiment.
Fig. 9 is an enlarged cross-sectional view of a principal portion showing a state where refrigerant flows in a gap between a second conical land portion of the needle valve in the second embodiment and the valve port.
Fig. 10 is an enlarged cross-sectional view of a main portion showing a state where a second straight line portion of the needle valve in the second embodiment is located in the valve port.
Fig. 11 is a diagram showing a refrigeration cycle system of the embodiment.
Fig. 12 is a diagram showing a relationship between the pulse amount and the flow rate of the drive pulse in the conventional motor-operated valve.
Fig. 13 is a diagram illustrating a conventional problem.
In the figure:
1-a valve housing, 1R-a valve chamber, 11-a first joint pipe, 12-a second joint pipe, 13-a main valve seat, 13 a-a main valve port, L-an axis, 2-a guide member, 21-a press-in portion, 22-a guide portion, 22 a-a guide hole, 23-a holder portion, 23 a-an internal thread portion, 24-a flange portion, 3-a main valve spool, 3 a-a main valve spring, 31-a main valve portion, 32-a holding portion, 33-a sub valve seat, 33 a-a sub valve port (small diameter valve port), 4-a needle valve, 41-a valve shaft, 42-a first conical land portion, 43-a first straight line portion, 44-a second conical land portion (conical land portion), 45-a second straight line portion (straight line portion), 46-a gasket, 47-a guide boss portion, 5-a drive portion, 5A stepping motor (electric motor), 51-a rotor shaft, 51a external thread portion, 52-magnetism, 52a rotor, a protrusion portion, 53-a stator coil, 5B-screw feed mechanism, 5C-stopper mechanism, 10-valve housing, 10R-valve chamber, 110-first joint pipe, 120-second joint pipe, 130-valve seat member, 130A-valve port (small diameter port), 20-guide member, 210-press-in portion, 220-guide portion, 220A-guide hole, 230-holder portion, 230A-internal thread portion, 240-flange portion, 30-valve holder portion, 40-needle valve, 410-boss portion, 420-first cone portion, 430-first straight portion, 440-second cone portion (cone portion), 450-second straight portion (straight portion), 50-drive portion, 50A-step motor (electric motor), 510-rotor shaft, 510A-external thread portion, 520-magnetic rotor, 530-stator coil, 511-boss portion, 512-flange portion, 50B-screw feed mechanism, 50C-stopper mechanism, 91-first chamber heat exchanger, 92-second indoor heat exchanger, 93-outdoor heat exchanger, 94-compressor, 95-four-way valve, 100-electric valve, 200-electric valve.
Detailed Description
Next, embodiments of an electrically operated valve and a refrigeration cycle system according to the present invention will be described with reference to the drawings. Fig. 1 is a longitudinal sectional view of an electric valve according to a first embodiment, fig. 2 is a main portion enlarged sectional view of the electric valve according to the first embodiment when a needle valve is located at a position closest to a sub-valve port, fig. 3 is a main portion enlarged sectional view of the electric valve according to the first embodiment when the needle valve is located between the position closest to the sub-valve port and a position engaged with a main valve body, fig. 4 is a main portion enlarged sectional view of the electric valve according to the first embodiment when the needle valve is located at the position engaged with the main valve body, and fig. 5 is a main portion enlarged sectional view showing a fully opened state of the main valve body of the electric valve according to the first embodiment. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawings of fig. 1 to 4. The motor-operated valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4, and a drive unit 5.
The valve housing 1 is formed of, for example, brass, stainless steel, or the like, has a substantially cylindrical shape, and has a valve chamber 1R inside thereof. A first joint pipe 11 that communicates with the 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 chamber 1R side of the second joint pipe 12, the inner side of the main valve seat 13 becomes a main valve port 13a, and the second joint pipe 12 is communicated with the valve chamber 1R through the main valve port 13 a. The main valve port 13a is a cylindrical through hole centered on the axis L. The first joint pipe 11 and the second joint pipe 12 are fixed 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 includes a press-fitting portion 21 press-fitted into the inner peripheral surface of the valve housing 1, a substantially columnar guide portion 22 located inside the press-fitting portion 21, a bracket portion 23 extended to the upper portion of the guide portion 22, and an annular flange portion 24 located on the outer periphery of the guide portion 22. The press-fitting portion 21, the guide portion 22, and the holder portion 23 are formed as an integral member made of resin. The flange portion 24 is a metal plate such as brass or stainless steel, for example, and the flange portion 24 is integrated with the resin press-fitting portion 21 and the bracket portion 22 by insert molding.
The guide member 2 is assembled to the valve housing 1, and is fixed to the upper end portion of the valve housing 1 by welding via the flange portion 24. In the guide member 2, a cylindrical guide hole 22a coaxial with the axis L is formed in the guide portion 22, and a female screw portion 23a coaxial with the guide hole 22a and a screw hole thereof are formed in the center of the holder portion 23. The main valve element 3 is disposed in the guide hole 22a of the holder portion 23.
The main valve body 3 includes a main valve portion 31 that seats on and unseats from the main valve seat 13, a holding portion 32 having a cylindrical needle guide hole 32a, and a sub valve seat 33. A washer 46 and a guide boss 47 attached to a valve shaft 41 described below are inserted into the needle guide hole 32a of the holding portion 32, and an annular retainer 321 is fitted and fixed to an upper end of the holding portion 32 or fixed thereto by welding or the like. The outer peripheral portion of the upper end of the holding portion 32 is reduced in diameter, a main valve spring 3a is disposed between the outer peripheral portion of the upper end of the holding portion 32 and the upper end portion of the guide hole 22a, and the main valve spring 3a biases the main valve element 3 in the direction of the main valve seat 13 (closing direction). The sub-valve seat 33 is located at the lower end of the needle guide hole 32a, and has a sub-valve port 33a formed at the center thereof as a "small-diameter valve port". The sub-valve port 33a has a circular shape centered on the axis L. At least one of the side surfaces of the holding portion 32 is formed with a communicating hole 32b that communicates the needle guide hole 32a with the valve chamber 1R, and as described later, when the needle valve 4 opens the sub-valve port 33a, the valve chamber 1R, the needle guide hole 32a, the sub-valve port 33a, and the main valve port 13a communicate with each other.
The needle valve 4 integrally includes: a valve shaft 41 formed integrally with the rotor shaft 51 at a lower end portion of the rotor shaft 51 described below and connected to the rotor shaft 51 side; a first conical land portion 42 connected to the valve shaft 41 side; a first straight portion 43 connected to the first frustum portion 42; a second frustum portion 44 connected to the first linear portion 43; and a second straight line portion 45 connected to the second frustum portion 44. The needle valve 4 includes an annular washer 46 disposed on the valve shaft 41, and a guide boss 47 fixed to the valve shaft 41. The guide boss 47 is fixed separately from the valve shaft 41, but the guide boss 47 may be formed integrally with the valve shaft 41. The "frustum portion" and the "linear portion" in the present invention correspond to the second frustum portion 44 and the second linear portion 45, respectively. The first straight portion 43 is formed to have a diameter matching the sub-port 33a and to be inserted into the sub-port 33a, and the side surfaces thereof have the same diameter in the direction of the axis L. The apex angle (the angle formed by the generatrices 180 ° apart from each other in the direction around the axis L) of the second frustum portion 44 is smaller than the apex angle of the first frustum portion 42. The side surface of the second linear portion 45 has a diameter smaller than that of the sub-port 33a and has the same diameter in the direction of the axis L. The washer 46 and the guide boss 47 are slidably inserted into the needle guide hole 32 a.
A housing 14 is hermetically fixed to the upper end of the valve housing 1 by welding or the like, and a driving portion 5 is formed inside and outside the housing 14. The drive unit 5 includes a stepping motor 5A as an "electric motor", a thread feed mechanism 5B for advancing and retracting the needle valve 4 by rotation of the stepping motor 5A, and a stopper mechanism 5C for restricting rotation of the stepping motor 5A.
The stepping motor 5A includes 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 yoke parts and exterior members, which are not shown. 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 23a of the guide member 2, whereby the guide member 2 supports the rotor shaft 51 on the axis L. The female screw portion 23a 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, the magnetic rotor 52 and the rotor shaft 51 are rotated by the driving of the stepping motor 5A, and the rotor shaft 51 is moved in the direction of the axis L by the screw feeding mechanism 5B constituted by the male screw portion 51a of the rotor shaft 51 and the female screw portion 23a of the guide member 2. Then, 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. Thereby controlling the opening degree of the sub-port 33 a. Then, the needle 4 (washer 46) engages with the main valve body 3 (holder 321), and the main valve body 3 moves together with the needle 4 to seat on and unseat from the main valve seat 13. Thereby controlling the flow rate of the refrigerant flowing from the first joint pipe 11 to the second joint pipe 12 or from the second joint pipe 12 to the first joint pipe 11. 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. Fig. 1 and 2 show a state in which the rotor shaft 51 (and the magnetic rotor 52) is located at the lowermost position.
Fig. 6 is a diagram showing the relationship between the pulse amount (valve opening degree) and the flow rate of the drive pulse in the stepping motor 5A, and the detailed operation of the electric valve 100 will be described with reference to fig. 2 to 6.
The motor-operated valve 100 described above operates as follows. First, in the state of fig. 2 (and fig. 1), the main valve portion 31 of the main valve 3 is seated on the main valve seat 13, and is in a valve-closed state in which the main valve port 13a is closed. On the other hand, the first straight portion 43 of the needle valve 4 located closest to the sub-valve port 33a is inserted into the sub-valve port 33a, but the needle valve 4 is not seated on the sub-valve seat 33, and the refrigerant slightly flows through a gap between the outer peripheral surface of the first straight portion 43 and the sub-valve port 33 a. That is, as shown in fig. 6, even if the drive pulse is at the reference point (zero point), a minute flow rate is generated.
Next, the magnetic rotor 52 is rotated by the driving of the stepping motor 5A to raise the needle valve 4, so that the first straight portion 43 of the needle valve 4 is pulled out from the sub-valve port 33a as shown in fig. 3, and a flow path is formed by a gap between the second frustum portion 44 of the needle valve 4 and the sub-valve port 33 a. Here, the diameter of the second conical land portion 44 gradually decreases, the gap with the sub valve port 33a becomes large, the flow passage expands, and the flow rate gradually increases as shown in fig. 6. At this time, since the main valve portion 31 of the main valve body 3 remains seated on the main valve seat 13, the flow rate increases slightly until the second conical land portion 44 of the needle valve 4 comes out of the sub-valve port 33 a. In this way, the opening degree of the sub-port 33a is changed by moving the needle valve 4 from a position closest to the sub-port 33a to a position where the second conical land portion 44 is disengaged from the sub-port 33a, and such a control region is a small flow rate control region. The flow rate in this small flow rate control region is less changed from the pulse amount (valve lift amount) of the drive pulse of the stepping motor 5A than in the large flow rate control region.
Next, as shown in fig. 4, when the needle 4 is raised to a position where it engages with the main valve body 31 and the washer 46 engages with the main valve body 3, the main valve body 3 is raised together with the needle 4. When the valve further ascends, as shown in fig. 5, the main valve body 3 is lifted by the valve shaft 41 (and the washer 46), and the main valve portion 31 is separated from the main valve seat 13 and opened. As described above, the control region for raising the main valve element 3 from the seating position (closed position) to the valve opening position (open position) is a large flow rate control region in which the flow rate changes greatly with respect to the pulse amount (i.e., valve lift amount) of the drive pulse of the stepping motor 5A. Then, in the fully open state in which the main valve element 3 is raised to the valve open position shown in fig. 5, the flow rate becomes maximum. As for the flow rate in the fully open state, the opening area of the gap between the main valve portion 31 and the main valve seat 13 is equal to or larger than the opening areas of the primary joint pipe 11 and the secondary joint pipe 12, and the flow rate is set to a state where the flow rate is not reduced by the main valve portion 31 and the main valve port 13a, that is, to an opening degree at which the electric valve 100 functions as a simple flow path.
Here, from the position shown in fig. 3 to the position shown in fig. 4, there is a moment when a boundary portion (the smallest diameter portion of the conical surface portion) between the second conical surface portion 44 and the second linear portion 45 of the needle valve 4 is pulled out from the sub-valve port 33 a. From this moment until the position shown in fig. 4, only the second linear portion 45 is located within the sub-port 33a, and the opening area of the slit between the sub-port 33a and the second linear portion 45 is constant. Therefore, as shown in fig. 6, a constant flow rate region in which a constant flow rate is maintained is generated from the end of the small flow rate control region to the large flow rate control region. Therefore, according to the present motor-operated valve 100, the deviation of the maximum flow rate in the small flow rate control region can be suppressed, and the flow rate of the maximum flow rate can be sufficiently reduced at the sub-valve port 33 a. Further, the range of the drive pulse actually used for controlling the minute flow rate, that is, the minute flow rate controllable range can be set to a wide range, and controllability of the minute flow rate controllable range can be improved.
Fig. 7 is a longitudinal sectional view of an electric valve of a second embodiment, fig. 8 is a main portion enlarged sectional view showing a needle valve corresponding to a lowermost end position of a magnetic rotor in the second embodiment, fig. 9 is a main portion enlarged sectional view showing a state where refrigerant flows in a gap between a second conical land portion of the needle valve and a valve port in the second embodiment, and fig. 10 is a main portion enlarged sectional view showing a state where a second straight line portion of the needle valve in the second embodiment is located in the valve port. Note that the concept of "top and bottom" in the following description corresponds to the top and bottom in the drawing of fig. 7.
The motor-operated valve 200 includes a valve housing 10, a guide member 20, a valve frame portion 30, a needle valve 40, and a driving portion 50.
The valve housing 10 is formed in a substantially cylindrical shape from brass, stainless steel, or the like, for example, and has a valve chamber 10R inside thereof. A first joint pipe 110 that communicates with the valve chamber 10R is connected to one side of the outer periphery of the valve housing 10, and a second joint pipe 120 is connected to a cylindrical portion that extends downward from the lower end. Further, a valve seat member 130 is fitted to the valve chamber 10R side of the second joint pipe 120. The inside of the valve seat member 130 is a valve port 130a which is a "small diameter valve port", and the second joint pipe 120 is communicated with the valve chamber 10R through the valve port 130 a. The valve port 130a is a cylindrical through hole centered on the axis L. The first joint pipe 110 and the second joint pipe 120 are fixed to the valve housing 10 by brazing or the like.
A guide member 20 is attached to an opening portion at the upper end of the valve housing 10. The guide member 20 includes a press-fitting portion 210 that is press-fitted into the inner circumferential surface of the valve housing 10, a substantially columnar guide portion 220 located inside the press-fitting portion 210, a bracket portion 230 that extends above the guide portion 220, and an annular flange portion 240 located on the outer circumference of the guide portion 220. The press-fitting portion 210, the guide portion 220, and the holder portion 230 are formed as an integral member made of resin. The flange portion 240 is a metal plate such as brass or stainless steel, for example, and the flange portion 240 is integrated with the resin press-fitting portion 210 and the bracket portion 220 by insert molding.
The guide member 20 is assembled to the valve housing 10, and is fixed to the upper end portion of the valve housing 10 by welding via the flange portion 240. In the guide member 20, a cylindrical guide hole 220a coaxial with the axis L is formed in the guide portion 220, and a female screw portion 230a coaxial with the guide hole 220a and a screw hole thereof are formed in the center of the holder portion 230. Further, the guide member 20 and the valve chamber 10R are provided with a valve mount portion 30 and a needle valve 40.
The valve cage portion 30 includes an annular thrust washer 310, a cylindrical guide tube 320, a spring seat 330, and a coil spring 340. The guide tube 320 has an annular top portion 320a formed by bending an upper end portion inward. On the other hand, the rotor shaft 510 described below has a boss portion 511 at an end portion on a lower end side than the male screw portion 510a, and a flange portion 512 is integrally formed on the boss portion 511. Also, the boss 511 is embedded in the top portion 320a and mounted with the thrust washer 310. A spring seat 330 is provided in the guide pipe 320 so as to be movable in the direction of the axis L, and the needle valve 40 is fixed to the lower end of the guide pipe 320 in a state where the spring seat 330 and the coil spring 340 are housed.
The needle valve 40 integrally includes: a boss 410 fixed to the guide tube 320; a first frustum portion 420 formed at a lower portion of the boss portion 410; a first linear portion 430 connected to the first frustum portion 420; a second frustum portion 440 connected to the first linear portion 430; and a second straight portion 450 connected to the second frustum portion 440. The "frustum portion" and the "linear portion" in the present invention correspond to the second frustum portion 440 and the second linear portion 450, respectively. The first linear portion 430 is formed to have a diameter matching the valve port 130a and to be inserted into the valve port 130a, and has a side surface having the same diameter in the direction of the axis L. The vertex angle of the second frustum portion 440 (the angle formed by the generatrices 180 ° apart from each other in the direction around the axis L) is smaller than the vertex angle of the first frustum portion 420. The side surface of the second linear portion 450 has a diameter smaller than that of the valve port 130a and has the same diameter in the direction of the axis L.
A housing 140 is hermetically fixed to the upper end of the valve housing 10 by welding or the like, and a driving portion 50 is formed inside and outside the housing 140. The drive unit 50 includes a stepping motor 50A as an "electric motor", a thread feeding mechanism 50B for advancing and retreating the needle valve 40 by rotation of the stepping motor 50A, and a stopper mechanism 50C for restricting rotation of the stepping motor 50A.
The stepping motor 50A includes a rotor shaft 510, a magnetic rotor 520 rotatably disposed inside the housing 140, a stator coil 530 disposed on the outer periphery of the housing 140 so as to face the magnetic rotor 520, and other yoke parts and exterior members, which are not shown. The rotor shaft 510 is attached to the center of the magnetic rotor 520 via a bushing, and a male screw portion 510a is formed on the outer periphery of the rotor shaft 510 on the guide member 20 side. The male screw portion 510a is screwed into the female screw portion 230a of the guide member 20, whereby the guide member 20 supports the rotor shaft 510 on the axis L. The female screw portion 230a of the guide member 20 and the male screw portion 510a of the rotor shaft 510 constitute a screw feeding mechanism 50B.
According to the above configuration, the magnetic rotor 520 and the rotor shaft 510 are rotated by the driving of the stepping motor 50A, and the rotor shaft 510 is moved in the direction of the axis L by the screw feeding mechanism 50B constituted by the male screw portion 510A of the rotor shaft 510 and the female screw portion 230A of the guide member 20. Further, the needle valve 40 moves forward and backward in the direction of the axis L, and the needle valve 40 approaches or separates from the valve port 130 a. The opening degree of the valve port 130a is controlled by this, and the flow rate of the refrigerant flowing from the first joint pipe 110 to the second joint pipe 120 or from the second joint pipe 120 to the first joint pipe 110 is controlled. The magnetic rotor 520 has a protrusion 520a, and the protrusion 520a operates the rotation restricting mechanism 50C to restrict the lowermost end position and the uppermost end position of the rotor shaft 510 (and the magnetic rotor 520) in accordance with the rotation of the magnetic rotor 520. Fig. 7 and 8 show a state in which the rotor shaft 510 (and the magnetic rotor 520) is located at the lowermost position.
The above motor-operated valve 200 operates as follows. First, in the state of fig. 7 and 8, the first linear portion 430 of the needle valve 40 located closest to the valve port 130a is inserted into the valve port 130a, and a small amount of refrigerant flows through a gap between the outer peripheral surface of the first linear portion 430 and the valve port 130 a.
Next, the magnetic rotor 520 is rotated by the driving of the stepping motor 50A to lift the needle valve 40, so that the first straight line portion 430 of the needle valve 40 is pulled out from the valve port 130A to form a flow path by a gap between the second frustum portion 440 of the needle valve 40 and the valve port 130A, as shown in fig. 9. Here, the diameter of the second conical land portion 440 gradually decreases, the gap with the valve port 130a increases, the flow path expands, and the flow rate gradually increases as in fig. 6. In this way, the control region in which the opening degree is changed by the gap between the second conical surface portion 440 of the needle valve 40 and the valve port 130A is a small flow rate control region, and the flow rate in this small flow rate control region is smaller than the change in the pulse amount (i.e., valve lift amount) of the drive pulse of the stepping motor 50A than in the large flow rate control region.
Here, from the position shown in fig. 9 to the position shown in fig. 10, there is a moment when the boundary portion (the smallest diameter portion of the frustum portion) between the second frustum portion 440 and the second linear portion 450 of the needle valve 40 escapes from the valve port 130 a. From this moment on, only the second linear portion 450 is located in the valve port 130a, so that the opening area of the slit between the valve port 130a and the second linear portion 450 is constant. When the second linear portion 450 is disengaged from the valve port 130a, a large flow rate control region in which the flow rate sharply increases toward the fully open state is formed. Thus, a constant flow rate region in which a constant flow rate is maintained is generated from the end of the small flow rate control region to the large flow rate control region. Therefore, according to the present motor-operated valve 200, the deviation of the maximum flow rate in the small flow rate control region can be suppressed, and the flow rate of the maximum flow rate can be sufficiently reduced at the valve port 130 a. Further, the range of the drive pulse actually used for controlling the minute flow rate, that is, the minute flow rate controllable range can be set to a wide range, and controllability of the minute flow rate controllable range can be improved.
Next, a refrigeration cycle system of the present invention will be described with reference to fig. 11. This refrigeration cycle system is used for an air conditioner such as a household air conditioner. The motor-operated valve 100 of the first embodiment 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 200 of the second embodiment is provided as an "electronic expansion valve" between the second indoor heat exchanger 92 and the outdoor heat exchanger 93. The motor-operated valve 100, the motor-operated valve 200, the outdoor heat exchanger 93, the compressor 94, and the four-way valve 95 constitute a heat pump refrigeration cycle. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the electric valve 100 are installed indoors, and the outdoor heat exchanger 93, the compressor 94, the four-way valve 95, and the electric valve 200 are installed outdoors, thereby configuring a cooling/heating apparatus.
In the motor-operated valve 100 according to the first embodiment of the dehumidification valve, the main valve element is fully opened during cooling or heating other than during dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 constitute one indoor heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 93 alternatively functions as an "evaporator" or a "condenser". That is, the motor-operated valve 200 as an electronic expansion valve is provided between the evaporator and the condenser.
In the above embodiment, the screw feeding mechanism is configured by forming the female screw portions 23a, 230a in the guide members 2, 20 and forming the male screw portions 51a, 510a in the rotor shafts 51, 510, but the screw feeding mechanism is not limited to the combination of the screws, and the female screw portions and the male screw portions may be formed in the guide members and the rotor shafts, respectively, and the female screw and the male screw may be configured as electric valves arranged in opposite directions.
While 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 the embodiments described above, and the present invention includes design changes and the like within a range not departing from the gist of the present invention.
Claims (6)
1. An electric valve in which a needle valve is disposed on the axis of a small-diameter valve port, the needle valve is advanced and retreated in the axial direction by converting the rotary motion of a rotor of an electric motor into linear motion by a screw feed mechanism, and the flow rate of a refrigerant is controlled in accordance with the opening area of the gap between the opening of the small-diameter valve port and the needle valve,
the above-mentioned electric valve is characterized in that,
a main valve body for changing the opening degree of a main valve port of a valve chamber, the main valve body having the small-diameter valve port,
the valve has a two-stage flow control region including a small flow control region in which the needle valve changes the opening degree of the small-diameter valve port and a large flow control region in which the main valve changes the opening degree of the main valve port,
the needle valve moves to the side opposite to the small-diameter valve port side and engages with the main valve body, the main valve body moves integrally with the needle valve in the engaged state of the needle valve engagement to change the opening degree of the main valve port,
in the engaged state, the needle valve is configured such that a tip end portion of the needle valve is held in the small-diameter valve port.
2. Electrically operated valve according to claim 1,
the needle valve includes:
a truncated cone-shaped truncated cone portion having a diameter gradually decreasing toward a tip on the small-diameter valve port side; and
a straight portion having a constant diameter, which is provided so as to be connected to a base end side having a largest diameter of the truncated cone portion and is positioned in the small-diameter valve port when the needle valve moves maximally toward the small-diameter valve port,
the needle valve is not seated on the small-diameter valve port even when it moves maximally toward the small-diameter valve port, and a flow path is formed between the straight portion and the small-diameter valve port.
3. Electrically operated valve according to claim 2,
the length of the straight portion of the needle valve is smaller than the outer diameter of the straight portion.
4. Electrically operated valve according to claim 2,
the small-diameter valve port is formed in a cylindrical shape with the axis as a central axis,
a tapered cylindrical portion having a smallest diameter portion formed by opening an end portion of the cylindrical small-diameter valve port on a side opposite to the needle valve side,
a boundary between the straight portion and the conical portion in the needle valve is positioned inside the cylindrical small-diameter valve port when the needle valve moves maximally toward the small-diameter valve port.
5. Electrically operated valve according to claim 1,
the main valve element includes:
a holding portion formed in a cylindrical shape, in which the needle valve is disposed inside, and which engages with the needle valve that moves to a side opposite to the small-diameter valve port side; and
and a main valve portion which is located at an end of the holding portion on the main valve port side with respect to the small-diameter valve port, is formed in a tapered ring shape having a tip end tapered from a portion having a diameter larger than the diameter of the holding portion and the main valve port to a tip end having a diameter smaller than the diameter of the main valve port, and changes an opening degree of the main valve port.
6. 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 according to claim 1 as the above-mentioned dehumidification valve.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018163360A JP6978391B2 (en) | 2018-08-31 | 2018-08-31 | Electric valve and refrigeration cycle system |
| JP2018-163360 | 2018-08-31 | ||
| CN201910749370.8A CN110873218B (en) | 2018-08-31 | 2019-08-14 | Electric valve and refrigeration cycle system |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910749370.8A Division CN110873218B (en) | 2018-08-31 | 2019-08-14 | Electric valve and refrigeration cycle system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114857288A true CN114857288A (en) | 2022-08-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910749370.8A Active CN110873218B (en) | 2018-08-31 | 2019-08-14 | Electric valve and refrigeration cycle system |
| CN202210643214.5A Pending CN114857288A (en) | 2018-08-31 | 2019-08-14 | Electric valve and refrigeration cycle system |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910749370.8A Active CN110873218B (en) | 2018-08-31 | 2019-08-14 | Electric valve and refrigeration cycle system |
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| Country | Link |
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| JP (1) | JP6978391B2 (en) |
| CN (2) | CN110873218B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7491734B2 (en) * | 2020-05-15 | 2024-05-28 | 株式会社鷺宮製作所 | Motor-operated valve and refrigeration cycle system |
| JP7349415B2 (en) * | 2020-07-09 | 2023-09-22 | 株式会社鷺宮製作所 | Two-stage electric valve and refrigeration cycle system |
| JP7519265B2 (en) | 2020-10-26 | 2024-07-19 | 株式会社鷺宮製作所 | Motor-operated valve and refrigeration cycle system |
| JP7406518B2 (en) * | 2021-03-03 | 2023-12-27 | 株式会社鷺宮製作所 | pressure regulating valve |
| JP7410580B2 (en) | 2021-07-19 | 2024-01-10 | 株式会社不二工機 | electric valve |
| JP7545057B2 (en) * | 2021-09-29 | 2024-09-04 | ダイキン工業株式会社 | Air Conditioning Equipment |
| JP7545056B2 (en) * | 2021-09-29 | 2024-09-04 | ダイキン工業株式会社 | Air Conditioning Equipment |
| JP7284421B2 (en) * | 2021-10-26 | 2023-05-31 | ダイキン工業株式会社 | air conditioner |
| JP7495625B2 (en) * | 2021-10-26 | 2024-06-05 | ダイキン工業株式会社 | Air Conditioning Equipment |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS49146541U (en) * | 1973-04-13 | 1974-12-18 | ||
| JP3997077B2 (en) * | 2001-11-14 | 2007-10-24 | 株式会社鷺宮製作所 | Motorized valve |
| JP5022120B2 (en) * | 2007-07-03 | 2012-09-12 | 株式会社不二工機 | Motorized valves for air conditioning systems |
| JP2010019378A (en) * | 2008-07-11 | 2010-01-28 | Denso Corp | Expansion valve |
| JP2012117584A (en) * | 2010-11-30 | 2012-06-21 | Saginomiya Seisakusho Inc | Electric flow control valve |
| JP6031078B2 (en) * | 2014-11-12 | 2016-11-24 | 株式会社鷺宮製作所 | Throttle device and refrigeration cycle system including the same |
| CN105588239B (en) * | 2015-03-06 | 2018-08-03 | 海信（山东）空调有限公司 | A kind of air-conditioning system |
| CN107356025B (en) * | 2016-05-10 | 2021-08-10 | 浙江三花智能控制股份有限公司 | Electronic expansion valve |
| JP6359593B2 (en) * | 2016-06-14 | 2018-07-18 | 株式会社鷺宮製作所 | Motorized valve |
| JP6552457B2 (en) * | 2016-06-22 | 2019-07-31 | 株式会社鷺宮製作所 | Motorized valve |
-
2018
- 2018-08-31 JP JP2018163360A patent/JP6978391B2/en active Active
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2019
- 2019-08-14 CN CN201910749370.8A patent/CN110873218B/en active Active
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| JP2020034140A (en) | 2020-03-05 |
| CN110873218B (en) | 2022-05-10 |
| CN110873218A (en) | 2020-03-10 |
| JP6978391B2 (en) | 2021-12-08 |
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