CN114076206A - Electric valve and refrigeration cycle system - Google Patents
Electric valve and refrigeration cycle system Download PDFInfo
- Publication number
- CN114076206A CN114076206A CN202110861987.6A CN202110861987A CN114076206A CN 114076206 A CN114076206 A CN 114076206A CN 202110861987 A CN202110861987 A CN 202110861987A CN 114076206 A CN114076206 A CN 114076206A
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- valve
- guide
- screw
- frame
- support member
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 14
- 230000002093 peripheral effect Effects 0.000 claims description 25
- 238000007906 compression Methods 0.000 abstract description 12
- 230000006835 compression Effects 0.000 abstract description 11
- 238000007789 sealing Methods 0.000 abstract description 3
- 239000003507 refrigerant Substances 0.000 description 9
- 238000004891 communication Methods 0.000 description 8
- 239000002184 metal Substances 0.000 description 5
- 238000005299 abrasion Methods 0.000 description 4
- 210000000078 claw Anatomy 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000000465 moulding Methods 0.000 description 3
- 239000011347 resin Substances 0.000 description 3
- 229920005989 resin Polymers 0.000 description 3
- 229910001369 Brass Inorganic materials 0.000 description 2
- 239000004734 Polyphenylene sulfide Substances 0.000 description 2
- 239000010951 brass Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000001771 impaired effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 229920000069 polyphenylene sulfide Polymers 0.000 description 2
- 230000006837 decompression Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
- F16K1/38—Valve members of conical shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/02—Construction of housing; Use of materials therefor of lift valves
- F16K27/0254—Construction of housing; Use of materials therefor of lift valves with conical shaped valve members
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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
- F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
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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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Electromagnetism (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Lift Valve (AREA)
Abstract
The invention provides an electrically operated valve and a refrigeration cycle system capable of improving sealing performance and durability by suppressing eccentricity and inclination of a valve part relative to a valve port. The motor-operated valve (10) is provided with a valve body (1) having a valve port (13), a valve element (2) for opening and closing the valve port (13), a drive unit (3) for driving and rotating a screw shaft (32), and a screw feed mechanism (4) for moving the screw shaft (32) forward and backward in the direction of an axis (L) in accordance with the rotation of the screw shaft (32). The valve body (2) has a valve portion (2A), a valve frame (2B), and a compression spring (2D), and the screw feed mechanism (4) has a support member (4A) fixed to the valve body (1), a female screw portion (41a) provided in the support member (4A), and a male screw portion (32B) provided in the screw shaft (32) and screwed into the female screw portion (41 a). A guide member (5) is provided on the valve body (1) on the valve port (13) side of the support member (4A) and guides the valve frame (2B) in the axis (L) direction.
Description
Technical Field
The present invention relates to an electric valve and a refrigeration cycle system.
Background
As an electrically operated valve provided in a refrigeration cycle of an air conditioner, an electrically operated valve is known, which includes: a valve housing (valve body) having a valve chamber therein and connected to primary and secondary joints; an electric motor (drive unit) having a magnetic rotor and a rotor shaft (drive shaft) that are driven to rotate by electromagnetic force from a coil; a screw feed mechanism that moves a rotor shaft that is driven to rotate by an electric motor forward and backward in an axial direction; and a valve element that is driven to advance and retreat in the axial direction by the advance and retreat movement of the rotor shaft (see, for example, patent document 1). In this electrically operated valve, a guide member (support member) is fixed to the valve body, a male screw portion of the rotor shaft is screwed into a female screw portion of the guide member, a valve holder of the valve body is guided by a guide hole of the guide member, and a needle valve (valve portion) of the valve body, which is driven by an electric motor to advance and retract in the axial direction, opens and closes a valve port of the valve chamber.
Documents of the prior art
Patent document
Patent document 1: japanese patent laid-open publication No. 2019-190496
Disclosure of Invention
Problems to be solved by the invention
However, in the conventional motor-operated valve described in patent document 1, the valve body is guided by the guide hole provided in the guide member provided at a position away from the valve port, and therefore there is a problem that it is difficult to improve the accuracy of guiding the valve body with respect to the axis. Further, the guide member is formed of a resin molded product, and may be welded and fixed to the valve body via a metal fixing member, but when the guide member is welded and fixed to the valve body via a metal fixing member, if the molding accuracy and the positional accuracy at the time of fixing are low, the guide hole may be eccentric or inclined with respect to the axis, and the guide accuracy of the valve body may be lowered. If the eccentricity or inclination of the guide hole occurs in this manner, the valve portion may be seated in a state displaced from the center of the valve port or inclined with respect to the axis, and a valve leakage of the refrigerant may occur even when the valve is closed, and stress concentration may occur at the contact portion between the deflected valve portion and the valve seat portion, causing local deformation or abrasion, and deteriorating durability.
The invention aims to provide an electric valve and a refrigeration cycle system which can improve the sealing performance and durability by inhibiting the eccentricity and inclination of a valve part relative to a valve port.
Means for solving the problems
The motor-operated valve of the present invention comprises: a valve body having a valve port; a valve element for opening and closing the valve port; a driving part for driving the driving shaft to rotate; and a screw feeding mechanism for moving the drive shaft forward and backward in the axial direction in accordance with the rotation of the drive shaft, wherein the valve body includes: a valve section that moves closer to or away from the valve port in accordance with the forward and backward movement of the drive shaft; a cylindrical valve frame provided over a distal end portion of the drive shaft and a proximal end portion of the valve portion; and a spring member which is provided in the valve frame and biases the valve portion in a valve closing direction, wherein the screw feeding mechanism includes: a support member fixed to the valve main body; a first screw portion provided in the support member and screwed to the drive shaft; and a second screw portion provided on the drive shaft and screwed to the first screw portion, wherein the valve body is provided with a guide portion that is positioned closer to the valve port than the support member and guides the valve frame in an axial direction.
According to the present invention, the valve body is configured to include the valve portion, the valve frame, and the spring member, the screw feeding mechanism is configured to include the first screw portion of the support member and the second screw portion of the drive shaft, and the valve frame is guided in the axial direction by the guide portion located closer to the valve port than the support member, whereby the accuracy of guiding the valve frame with respect to the axial line can be improved, and the eccentricity and inclination of the valve portion with respect to the valve port can be suppressed. Therefore, by seating the valve portion not eccentrically or obliquely with respect to the valve port, occurrence of valve leakage when the valve is closed can be suppressed, and local deformation and abrasion of the contact portion between the valve portion and the valve port can be suppressed to improve durability.
In this case, the guide portion is preferably formed of a cylindrical guide member fixed to the valve body, or a guide surface formed integrally with the valve body. According to this configuration, when the guide portion is formed of a guide member separate from the valve body, the guide member can be selected from a material and a molding method different from those of the valve body. On the other hand, when the guide portion is formed by the guide surface formed integrally with the valve body, the number of components can be reduced, and the positional accuracy of the valve port and the guide surface can be improved, thereby improving the guide accuracy of the valve frame. The guide surface may be provided on the opposite side (drive portion side) of the valve port with the valve chamber interposed therebetween, or may be formed by an inner surface of a cylindrical portion extending in the axial direction from a valve seat portion constituting the valve port.
Preferably, the support member has a cylindrical portion provided on the valve port side of the first screw portion and covering the outer peripheral surface of the valve holder, and a clearance dimension S2 between the inner peripheral surface of the guide portion and the outer peripheral surface of the valve holder is smaller than a clearance dimension S1 between the inner peripheral surface of the cylindrical portion and the outer peripheral surface of the valve holder. According to this configuration, the clearance dimension S2 between the inner peripheral surface of the guide portion and the outer peripheral surface of the valve holder is smaller than the clearance dimension S1 between the inner peripheral surface of the cylindrical portion of the support member and the outer peripheral surface of the valve holder (S1 > S2), so that even when the cylindrical portion of the support member is eccentric or inclined with respect to the axis, the cylindrical portion is less likely to interfere with the valve holder, and the accuracy of guiding the valve body can be prevented from being impaired.
Preferably, a length dimension L1 of a portion of the guide portion that guides the valve frame in the axial direction is larger than an outer diameter dimension L2 of the valve frame. According to this configuration, the length L1 of the portion where the valve frame is guided by the guide portion is larger than the outer diameter L2 of the valve frame (L1 > L2), so that the guide length of the valve frame can be ensured and the inclination of the valve frame can be suppressed.
Preferably, when the valve body is in the fully open position, a distal end portion of the valve frame is disposed to protrude further toward the valve port than a distal end portion of the guide portion. According to this configuration, the valve body in the fully open position has the valve seat protruding beyond the front end of the guide portion, and the flow of the fluid in the valve chamber can be stabilized. That is, when the valve frame is submerged in the guide portion at the time of full opening, the front end portion of the guide portion opens into the valve chamber, and the shape around the opening is complicated, and the flow of the fluid may be disturbed.
The refrigeration cycle system of the present invention includes a compressor, a condenser, an expansion valve, and an evaporator, and is characterized in that any one of the motor operated valves is used as the expansion valve.
The effects of the invention are as follows.
According to the electrically operated valve and the refrigeration cycle system of the present invention, the valve section can be prevented from being eccentric or inclined with respect to the valve port, thereby improving the sealing property and durability.
Drawings
Fig. 1 is a longitudinal sectional view showing an electric valve according to an embodiment of the present invention.
Fig. 2 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve in a closed state.
Fig. 3 is a cross-sectional view showing a main portion of the motor-operated valve, and is a cross-sectional view at a position indicated by line a-a in fig. 1 and 2.
Fig. 4 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve in an open state.
Fig. 5 is a longitudinal sectional view showing a modification of the motor-operated valve.
Fig. 6 is a diagram showing a refrigeration cycle system of the present invention.
In the figure:
1-valve body, 1A-valve chamber, 2-valve body, 2A-valve section, 2B-valve frame, 2D-compression spring, 3-drive section, 4-screw feed mechanism, 4A-support member, 5-guide member (guide section), 13-valve port, 17-guide surface (guide section), 22-base end section, 32-screw shaft (drive shaft), 32B-external screw section (second screw section), 41A-internal screw section (first screw section), 100-expansion valve (electric valve), 200-outdoor heat exchanger (condenser or evaporator), 300-indoor heat exchanger (evaporator or condenser), 400-flow path switching valve, 500-compressor.
Detailed Description
An electrically operated valve according to an embodiment of the present invention will be described with reference to fig. 1 to 4. As shown in fig. 1, the motor-operated valve 10 of the present embodiment includes a valve body 1, a valve body 2, a drive portion 3, a screw feed mechanism 4, and a guide member 5. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawing of fig. 1.
The valve body 1 is a member made of metal such as SUS or brass after cutting, and has a cylindrical valve chamber 1A formed therein, a first port 1B formed in a side surface thereof, a second port 1C formed in a bottom surface thereof, and a valve seat portion 1D formed above the second port 1C. A first joint pipe 11 communicating with the valve chamber 1A and allowing inflow or outflow of refrigerant is attached to the first port 1B of the valve body 1, and a second joint pipe 12 communicating with the valve chamber 1A and allowing outflow or inflow of refrigerant is attached to the second port 1C. A valve port 13 having a circular cross section is formed in the valve seat portion 1D. The valve body 1 is formed with a first tubular portion 14 that extends further upward in the axis L direction than the valve chamber 1A and houses a guide member 5 described below, and a second tubular portion 15 that extends upward of the first tubular portion 14 and has an inner diameter larger than the inner diameter of the first tubular portion 14. A case 16 constituting an outer shell of the driving portion 3 is fixed to an upper end edge of the second cylindrical portion 15.
As shown in fig. 2, the valve body 2 includes: a valve portion 2A having a needle-like portion 21 that is close to or away from the valve seat portion 1D to open and close the valve port 13; a cylindrical valve frame 2B that holds the proximal end portion 22 of the valve portion 2A; a spring seat 2C which is disposed in the valve frame 2B and abuts against a diameter-enlarged portion 32C at the front end of the screw shaft 32 described below; a compression spring 2D as a spring member interposed in a compressed state between the base end portion 22 of the valve portion 2A and the spring seat 2C; and a thrust washer 2E interposed between the diameter-enlarged portion 32c of the screw shaft 32 and the upper wall portion of the valve frame 2B. The valve portion 2A, the valve frame 2B, the spring seat 2C, the compression spring 2D, and the thrust washer 2E are disposed coaxially about the axis L, and the valve element 2 is driven by the driving portion 3 to advance and retreat in the direction of the axis L. The valve portion 2A has a projection 23 projecting upward (toward the driving portion 3) from the base end portion 22, and the projection 23 is inserted into the compression spring 2D. An insertion hole 24 through which the screw shaft 32 is inserted is formed in the upper wall portion of the valve frame 2B, and the diameter-enlarged portion 32c of the screw shaft 32 is engaged with the upper wall portion of the valve frame 2B via the thrust washer 2E. The thrust washer 2E can abut against the diameter-enlarged portion 32c of the screw shaft 32 and the upper wall portion of the valve frame 2B, and the frictional force between the abutting surfaces thereof becomes extremely small, whereby the rotation of the screw shaft 32 is hardly transmitted to the valve frame 2B.
The drive unit 3 includes a stepping motor 3A as an electric motor and a stopper mechanism 3B for restricting rotation of the stepping motor 3A. The stepping motor 3A includes: a magnetic rotor 31 magnetized in multipolar in the outer peripheral portion; a stator coil, not shown, disposed on the outer periphery of the case 16; and a screw shaft 32 as a drive shaft fixed to the magnetic rotor 31. The screw shaft 32 is fixed to the magnetic rotor 31 via a fixing member 32a, extends along the axis L, and has an upper end inserted into a guide 33 of the stopper mechanism 3B. An external thread portion 32b as a second thread portion is integrally formed at an intermediate portion of the screw shaft 32, and the external thread portion 32b is screwed with the internal thread portion 41a of the support member 4A. A diameter-enlarged portion 32c that engages with the valve frame 2B of the valve body 2 is formed at the distal end of the screw shaft 32.
The stopper mechanism 3B includes: a cylindrical guide 33 hanging down from the top of the housing 16; a guide wire body 34 fixed to the outer periphery of the guide 33; and a movable slider 35 which is guided by the guide wire 34 and can move up and down while rotating. The movable slider 35 is provided with a claw portion 35a protruding radially outward, and the movable slider 35 moves up and down while rotating along the guide wire 34 by rotating the magnetic rotor 31 and pressing the claw portion 35 a. An upper end stopper 33a defining the uppermost end position of the magnetic rotor 31 is formed on the guide 33, and a lower end stopper 34a defining the lowermost end position of the magnetic rotor 31 is formed on the guide wire body 34. The claw portion 35a of the movable slider 35 abuts on the upper end stopper 33a and the lower end stopper 34a to stop the rotation of the movable slider 35, thereby restricting the rotation of the magnetic rotor 31 and also stopping the raising or lowering of the valve element 2.
The screw feed mechanism 4 advances and retracts the valve body 2 by advancing and retracting the screw shaft 32 rotated by the stepping motor 3A in the direction of the axis L, and includes a support member 4A. The support member 4A includes a support member body 41 as a resin molded product and a metal fixing portion 42 insert-molded to the support member body 41, and the fixing portion 42 is welded and fixed to the upper end edge of the second tube portion 15 of the valve body 1. The support member body 41 is formed to have a female screw portion 41a as a first screw portion screwed to the male screw portion 32B of the screw shaft 32, and a cylindrical portion 41B provided closer to the valve port 13 than the female screw portion 41a and covering the outer peripheral surface of the valve frame 2B. Pressure equalizing holes 41c that penetrate in the radial direction and communicate the inside of the cylindrical portion 41b with the inside of the housing 16 (rotor chamber) are provided at a plurality of locations in the circumferential direction of the cylindrical portion 41 b. Pressure equalizing holes 42a that penetrate in the axial direction and communicate the inside of the second cylindrical portion 15 of the valve body 1 with the inside of the housing 16 (rotor chamber) are provided at a plurality of locations in the circumferential direction of the fixing portion 42. In the screw feeding mechanism 4, the male screw portion 32b of the screw shaft 32 is screwed to the female screw portion 41a of the support member 4A, and the magnetic rotor 31 and the screw shaft 32 are rotated by driving the screw shaft 32 to advance and retreat in the direction of the axis L, and the valve body 2 is also raised or lowered along the axis L along with this.
The guide member 5 is made of, for example, a metal such as SUS or brass, or a resin such as PPS (polyphenylene sulfide), is a member having a cylindrical shape as a whole, is provided on the valve port 13 side of the support member 4A (i.e., a gap is provided between the upper end of the guide member 5 and the lower end of the support member 4A), is inserted into the first cylindrical portion 14 of the valve body 1, and is caulked and fixed to the caulking portion 14A of the upper end of the first cylindrical portion 14. The guide member 5 has: an annular flange 51 caulked and fixed to the caulking portion 14 a; a press-fitting portion 52 continuous to the lower side of the collar portion 51 and press-fitted into the first tube portion 14; and a cylindrical portion 53 formed continuously to the lower side of the press-fitting portion 52 and having a smaller wall thickness than the press-fitting portion 52. The flange portion 51, the press-fitting portion 52, and the inner peripheral surface of the cylindrical portion 53 form a continuous cylindrical guide surface 5A having the same inner diameter, and the guide surface 5A faces the outer peripheral surface of the valve frame 2B with a slight gap therebetween, thereby constituting a guide portion for guiding the valve frame 2B in the direction of the axis L. As shown in fig. 3, two D-shaped cut portions 54 serving as communication passages for communicating the valve chamber 1A with the internal space of the second tube 15 are provided on the outer peripheral sides of the collar portion 51 and the press-fitting portion 52, and the valve chamber 1A and the internal space of the second tube 15 communicate with each other through the D-shaped cut portions 54.
As shown in fig. 2, the height dimension of the guide member 5, i.e., the length dimension L1 of the guide surface 5A in the axial direction, is formed to be larger than the outer diameter dimension L2 of the valve frame 2B (L1 > L2), and the length dimension L1 of the guide surface 5A is preferably 1.5 times or more the outer diameter dimension L2 of the valve frame 2B. A gap is formed between the guide surface 5A of the guide member 5 and the outer peripheral surface of the valve frame 2B, and a gap dimension S2 between the guide surface 5A and the outer peripheral surface of the valve frame 2B is set smaller than a gap dimension S1 between the inner peripheral surface of the cylindrical portion 41B of the support member 4A and the outer peripheral surface of the valve frame 2B. When the valve is closed as shown in fig. 2, a gap of a spacing dimension S3 is formed between the upper surface of the diameter-enlarged portion 32C of the screw shaft 32 and the lower surface of the thrust washer 2E, and when the valve is opened as shown in fig. 4, a gap of a spacing dimension S3 is formed between the front end surface of the diameter-enlarged portion 32C of the screw shaft 32 and the upper surface of the spring seat 2C. That is, when the valve is opened, the valve frame 2B is suspended and supported by the enlarged diameter portion 32c of the screw shaft 32 via the thrust washer 2E, and the biasing force of the compression spring 2D does not act on the valve element 2 from the screw shaft 32. In the valve opening state (fully open state) shown in fig. 4, the distal end portion of the valve frame 2B is provided to protrude further toward the valve port 13 than the distal end portion of the guide 5.
Next, the operation of the motor-operated valve 10 will be described. When the stepping motor 3A is driven to rotate the screw shaft 32 from the valve-opened state shown in fig. 4, the screw shaft 32 is lowered by the screw feeding mechanism 4, and the valve body 2 is also lowered along with this, and the needle-like portion 21 is inserted into the valve port 13. When the screw shaft 32 is further rotated and lowered, the valve body 2 comes into contact with the seat portion 1D, that is, the tapered surface 21a of the base end portion of the needle portion 21 is seated on the upper surface corner portion of the seat portion 1D, but at the moment of seating, the tip of the enlarged diameter portion 32C of the screw shaft 32 does not come into contact with the spring seat 2C, and the biasing force of the compression spring 2D is not applied to the valve body 2, and as a result, a frictional force of sliding rotation is not generated between the needle portion 21 and the seat portion 1D. When the screw shaft 32 is further rotated and lowered, as shown in fig. 2, the tip of the diameter-enlarged portion 32C of the screw shaft 32 abuts against the spring seat 2C to press down the spring seat 2C, and the biasing force of the compression spring 2D acts on the valve body 2, so that the needle-like portion 21 is pressed against the valve seat portion 1D to maintain the valve-closed state.
The motor-operated valve of the present embodiment is not limited to the motor-operated valve 10 shown in fig. 1 to 4, and may have a structure shown in fig. 5. The electric valve 10A shown in fig. 5 is different from the electric valve 10 in that: the guide portion is constituted by a guide surface 17 formed integrally with the valve main body 1. The guide surface 17 vertically penetrates the valve main body 1 so as to communicate the valve chamber 1A with the inside of the second cylindrical portion 15, and is formed as a cylindrical surface centered on the axis L. The clearance dimension S2 between the guide surface 17 and the outer peripheral surface of the valve frame 2B is set smaller than the clearance dimension S1 between the inner peripheral surface of the cylindrical portion 41B of the support member 4A and the outer peripheral surface of the valve frame 2B. The length L1 of the guide surface 17 in the direction of the axis L is set to be larger than the outer diameter L2 of the valve frame 2B. Further, one or more communication holes 18 are provided around the guide surface 17 to serve as communication passages for communicating the valve chamber 1A with the inside of the second cylindrical portion 15.
According to the present embodiment described above, the guide member 5 is provided on the valve port 13 side of the screw feeding mechanism 4 with respect to the support member 4A, and the valve frame 2B is guided in the direction of the axis L by the guide member 5, whereby the accuracy of guiding the valve frame 2B with respect to the axis L can be improved, and the eccentricity and inclination of the needle portion 21 with respect to the valve port 13 can be suppressed. Therefore, by seating the needle portion 21 on the valve seat portion 1D without decentering or inclining with respect to the valve port 13, occurrence of valve leakage at the time of closing the valve can be suppressed, and local deformation and abrasion of the contact portion between the needle portion 21 and the valve seat portion 1D can be suppressed to improve durability.
The guide member 5, which is separate from the valve body 1, is fixed to the valve body 1, and the valve frame 2B is guided by the guide surface 5A of the guide member 5, so that a member different from the valve body 1 in material and molding method can be selected as the guide member 5. On the other hand, as shown in fig. 5, if the valve frame 2B is guided by the guide surface 17 formed integrally with the valve main body 1, the number of components can be reduced, and the positional accuracy of the valve port 13 and the guide surface 17 can be improved, thereby improving the guide accuracy of the valve frame 2B.
Further, the clearance dimension S2 between the guide surface 5A of the guide member 5 or the guide surface 17 of the valve body 1 and the outer peripheral surface of the valve holder 2B is smaller than the clearance dimension S1 between the inner peripheral surface of the cylindrical portion 41B of the support member 4A and the outer peripheral surface of the valve holder 2B (S1 > S2), so that even when the cylindrical portion 41B of the support member 4A is eccentric or inclined with respect to the axis, the cylindrical portion 41B is less likely to interfere with the valve holder 2B, and the accuracy of guiding the valve body 2 can be prevented from being impaired.
Further, the length L1 of the portion where the valve frame 2B is guided by the guide surface 5A of the guide member 5 or the guide surface 17 of the valve body 1 is larger than the outer diameter L2 of the valve frame 2B (L1 > L2), whereby the guide length of the valve frame 2B can be secured, and the inclination of the valve frame 2B can be suppressed.
Further, the valve body 2B of the valve body 2 located at the fully open position projects further toward the valve port 13 than the tip end portions of the guide surfaces 5A and 17, and the flow of the fluid in the valve chamber 1A can be stabilized.
Further, at the time of valve opening, since the biasing force of the compression spring 2D does not act on the valve body 2 from the screw shaft 32 and the biasing force of the compression spring 2D does not act on the valve body 2 at the moment of seating, a frictional force of sliding rotation is not generated between the needle portion 21 and the seat portion 1D, and local deformation and abrasion of the contact portion between the needle portion 21 and the seat portion 1D can be suppressed, and further durability can be improved.
Further, a communication path (D-shaped cut portion 54, communication hole 18 in the modified example) is provided to communicate the valve chamber 1A with the interior of the second cylindrical portion 15, the valve chamber 1A is communicated with the interior space of the second cylindrical portion 15 of the valve main body 1 via the communication path (D-shaped cut portion 54, communication hole 18), and a gap is provided between the upper end portion of the guide portion (the upper end portion of the guide member 5, the upper end portion of the guide surface 17 in the modified example) and the lower end portion of the support member 4A, so that the pressure in the interior spaces (rotor chambers) of the valve chamber 1A and the housing 16 can be easily equalized. That is, the second cylindrical portion 15 of the valve body 1 communicates with the rotor chamber via the clearance between the guide portion (the guide member 5, the upper end portion of the guide surface 17 in the modification) and the support member 4A, the inside of the cylindrical portion 41b of the support member body 41, and the pressure equalizing hole 41c, and communicates with the rotor chamber via the pressure equalizing hole 42a of the fixing portion 42 of the support member 4A, and pressure equalization between the valve chamber 1A and the rotor chamber is realized via these two paths.
Next, a refrigeration cycle system of the present invention will be described with reference to fig. 6. Fig. 6 is a diagram showing a refrigeration cycle system according to an embodiment. In the drawings, reference numeral 100 denotes an expansion valve using the motor-operated valves 10 and 10A of the above embodiments, 200 denotes an outdoor heat exchanger mounted in an outdoor unit, 300 denotes an indoor heat exchanger mounted in an indoor unit, 400 denotes a flow path switching valve constituting a four-way valve, and 500 denotes a compressor. The expansion valve 100, the outdoor heat exchanger 200, the indoor heat exchanger 300, the flow path switching valve 400, and the compressor 500 are connected by pipes as shown in the drawing, and thereby a heat pump type refrigeration cycle is configured. Note that the illustration of the reservoir, the pressure sensor, the temperature sensor, and the like is omitted.
The flow path of the refrigeration cycle is switched by the flow path switching valve 400 to two types, i.e., a flow path during the cooling operation and a flow path during the heating operation. In the cooling operation, as shown by solid arrows in the figure, the refrigerant compressed by the compressor 500 flows from the flow path switching valve 400 into the outdoor heat exchanger 200, the outdoor heat exchanger 200 functions as a condenser, the liquid refrigerant flowing out of the outdoor heat exchanger 200 flows to the indoor heat exchanger 300 side via the expansion valve 100, and the indoor heat exchanger 300 functions as an evaporator.
On the other hand, during the heating operation, as indicated by the broken-line arrows in the figure, the refrigerant compressed by the compressor 500 circulates from the flow path switching valve 400 to the indoor heat exchanger 300, the expansion valve 100, the outdoor heat exchanger 200, the flow path switching valve 400, and the compressor 500 in this order, and the indoor heat exchanger 300 functions as a condenser and the outdoor heat exchanger 200 functions as an evaporator. The expansion valve 100 performs decompression and expansion of the liquid refrigerant flowing from the outdoor heat exchanger 200 during the cooling operation or the liquid refrigerant flowing from the indoor heat exchanger 300 during the heating operation, and controls the flow rate of the refrigerant.
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 described below are also included in the present invention. For example, in the above-described embodiment, the electrically operated valves 10 and 10A used in an air conditioner such as a home air conditioner are exemplified, but the electrically operated valve of the present invention is not limited to the home air conditioner, and may be a commercial air conditioner, and may be applied to various refrigerators and the like without being limited to the air conditioner.
In the above embodiment, the driving unit 3 is configured to include the stepping motor 3A and the stopper mechanism 3B, but is not limited to such a configuration, and the valve body may be driven in the axial direction via the drive shaft as the driving unit. In the above embodiment, the screw feeding mechanism 4 is configured by screwing the male screw portion 32b of the screw shaft 32 of the driving portion 3 and the female screw portion 41a of the support member 4A, but the present invention is not limited to this, and the screw feeding mechanism may be configured by forming a female screw (second screw portion) on one side of the driving shaft, forming a male screw (first screw portion) on one side of the support member, and screwing the male screw and the female screw.
In the above-described embodiment, the tip end portion of the valve portion 2A of the valve body 2 is formed as the needle-like portion 21 having a tapered shape, and the needle-like portion 21 is inserted into the valve port 13 and seated thereon. In the above embodiment, the valve portion 2A and the valve frame 2B are formed separately and fixed, but the present invention is not limited thereto, and the valve portion 2A and the valve frame 2B may be connected to be rotatable relative to each other. In the above embodiment, the compression spring 2D is directly in contact with the base end portion 22 of the valve portion 2A, but a member for reducing the frictional force similar to the thrust washer 2E may be interposed between the base end portion 22 of the valve portion 2A and the compression spring 2D. In the case of a structure in which the valve portion 2A and the valve frame 2B are connected to each other so as to be rotatable relative to each other, the distal end portion of the screw shaft 32 and the valve frame 2B may be fixed so as not to be rotatable relative to each other.
Further, in the above-described embodiment, the guide member 5 and the guide surface 17 are provided to the valve port 13 of the valve body 1 so as to sandwich the valve chamber 1A (that is, the valve chamber 1A is provided between the lower end of the guide member 5 and the lower end of the guide surface 17 and the valve port 13), but the present invention is not limited to this, and a tubular guide portion continuous to the valve port may be provided to guide the valve holder by the guide portion. In this case, the cylindrical guide portion continuous with the valve port may be provided with a communication hole on a side surface thereof to communicate the first port with the inside of the guide portion, and the inner space of the cylindrical guide portion may function as a valve chamber. In this case, the cylindrical guide portion may be formed integrally with the valve body, or may be formed separately from the valve body and fixed to the valve body. In addition, when the valve main body and the valve seat member are formed separately, a cylindrical guide portion may be integrally provided in the valve seat member.
While the embodiments of the present invention have been described in detail with reference to the drawings, the specific configurations are not limited to the embodiments, and design changes and the like that do not depart from the scope of the present invention are also included in the present invention.
Claims (6)
1. An electrically operated valve comprising: a valve body having a valve port; a valve element for opening and closing the valve port; a driving part for driving the driving shaft to rotate; and a screw feeding mechanism for advancing and retreating the drive shaft in the axial direction in accordance with the rotation of the drive shaft,
the above-mentioned electric valve is characterized in that,
the valve body is configured to include:
a valve section that moves closer to or away from the valve port in accordance with the forward and backward movement of the drive shaft;
a cylindrical valve frame provided over a distal end portion of the drive shaft and a proximal end portion of the valve portion; and
a spring member which is provided in the valve frame and biases the valve portion in a valve closing direction,
the screw feeding mechanism includes:
a support member fixed to the valve main body;
a first screw portion provided in the support member and screwed to the drive shaft; and
a second screw part provided on the drive shaft and screwed with the first screw part,
the valve body is provided with a guide portion that is located closer to the valve port than the support member and that guides the valve frame in the axial direction.
2. Electrically operated valve according to claim 1,
the guide portion is formed of a cylindrical guide member fixed to the valve body, or a guide surface formed integrally with the valve body.
3. Electrically operated valve according to claim 1 or 2,
the support member has a cylindrical portion provided closer to the valve port than the first screw portion and covering an outer peripheral surface of the valve holder,
a gap dimension S2 between the inner circumferential surface of the guide portion and the outer circumferential surface of the valve holder is smaller than a gap dimension S1 between the inner circumferential surface of the cylindrical portion and the outer circumferential surface of the valve holder.
4. An electrically operated valve according to any one of claims 1 to 3,
a length L1 of a portion of the guide portion that guides the valve frame in the axial direction is larger than an outer diameter L2 of the valve frame.
5. Electrically operated valve according to any of claims 1 to 4,
when the valve element is in the fully open position, the tip end portion of the valve frame is arranged to protrude further toward the valve port than the tip end portion of the guide portion.
6. A refrigeration cycle system comprises a compressor, a condenser, an expansion valve and an evaporator, and is characterized in that,
an electrically operated valve as claimed in any one of claims 1 to 5 is used as the expansion valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020137902A JP7453091B2 (en) | 2020-08-18 | 2020-08-18 | Electric valve and refrigeration cycle system |
| JP2020-137902 | 2020-08-18 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN114076206A true CN114076206A (en) | 2022-02-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110861987.6A Pending CN114076206A (en) | 2020-08-18 | 2021-07-29 | Electric valve and refrigeration cycle system |
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| Country | Link |
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| JP (1) | JP7453091B2 (en) |
| CN (1) | CN114076206A (en) |
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| Publication number | Publication date |
|---|---|
| JP7453091B2 (en) | 2024-03-19 |
| JP2022034213A (en) | 2022-03-03 |
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