WO2006093149A1 - 膨張弁及び冷凍装置 - Google Patents
膨張弁及び冷凍装置 Download PDFInfo
- Publication number
- WO2006093149A1 WO2006093149A1 PCT/JP2006/303751 JP2006303751W WO2006093149A1 WO 2006093149 A1 WO2006093149 A1 WO 2006093149A1 JP 2006303751 W JP2006303751 W JP 2006303751W WO 2006093149 A1 WO2006093149 A1 WO 2006093149A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve body
- valve
- peripheral surface
- throttle
- hole
- Prior art date
Links
- 238000005057 refrigeration Methods 0.000 title claims description 15
- 230000002093 peripheral effect Effects 0.000 claims abstract description 229
- 239000003507 refrigerant Substances 0.000 claims description 284
- 238000005192 partition Methods 0.000 claims description 53
- 238000011144 upstream manufacturing Methods 0.000 claims description 23
- 238000003754 machining Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 description 24
- 239000007788 liquid Substances 0.000 description 12
- 238000000034 method Methods 0.000 description 10
- 230000002159 abnormal effect Effects 0.000 description 9
- 239000002826 coolant Substances 0.000 description 9
- 238000013461 design Methods 0.000 description 8
- 239000002893 slag Substances 0.000 description 8
- 238000007796 conventional method Methods 0.000 description 7
- 230000007257 malfunction Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 239000000126 substance Substances 0.000 description 4
- 230000005514 two-phase flow Effects 0.000 description 4
- 238000013467 fragmentation Methods 0.000 description 3
- 238000006062 fragmentation reaction Methods 0.000 description 3
- 230000001629 suppression Effects 0.000 description 3
- 102000029749 Microtubule Human genes 0.000 description 2
- 108091022875 Microtubule Proteins 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 210000004688 microtubule Anatomy 0.000 description 2
- 239000002808 molecular sieve Substances 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- URGAHOPLAPQHLN-UHFFFAOYSA-N sodium aluminosilicate Chemical compound [Na+].[Al+3].[O-][Si]([O-])=O.[O-][Si]([O-])=O URGAHOPLAPQHLN-UHFFFAOYSA-N 0.000 description 2
- 238000000638 solvent extraction Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 235000013399 edible fruits Nutrition 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007790 scraping Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
Classifications
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
- F16K47/06—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member with a throttle in the form of a helical channel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths
- F16K47/12—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths the throttling channel being of helical form
-
- 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
- F25B41/38—Expansion means; Dispositions thereof specially adapted for reversible cycles, e.g. bidirectional expansion restrictors
-
- 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
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/12—Sound
-
- 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
Definitions
- the present invention relates to an expansion valve and a refrigeration apparatus.
- a separate type air conditioner includes a refrigeration circuit shown in FIG. 23, for example.
- This refrigeration circuit includes a compressor 201, an outdoor coil 202, an expansion valve 203, and an indoor coil 204.
- the compressor 201 and the outdoor coil 202 are housed in the outdoor unit 205, and the expansion valve 203 and the indoor coil 204 are housed in the indoor unit 206.
- the expansion valve 203 for example, an electric expansion valve shown in FIG. 24 is used.
- the electric expansion valve includes a valve main body 210, and an inlet port 211 and an outlet port 212 are formed in the valve main body 210.
- a valve chamber 213 and a refrigerant flow passage 214 are formed in the valve main body 210, and the inlet port 211 and the outlet port 212 are communicated with each other through them.
- a partition wall 216 having a valve hole 217 is formed in the valve body 210.
- the valve body 215 force is stored with its tip directed toward the valve hole 217 of the partition wall 216.
- a tapered portion 218 is provided at the tip of the valve body 215, and a throttle portion 219 is formed between the tapered portion 218 and the valve hole 217.
- the valve body 215 is moved forward and backward with respect to the valve hole 217 by a drive unit such as a pulse motor (not shown), for example, and thereby the opening degree of the valve hole 217 (the throttle amount of the throttle unit 219) is adjusted.
- the high-pressure gas refrigerant compressed by the compressor 201 is first transported to the outdoor coil 202.
- the refrigerant is condensed and liquidized by heat exchange with the outside air.
- the liquefied refrigerant is introduced into the valve body 210 of the expansion valve 203 via the liquid pipe 207 and the inlet port 211.
- the refrigerant introduced into the valve main body 210 is sent out to the indoor coil 204 through the throttle 219 and the outlet port 212.
- the refrigerant sent to the indoor coil 204 evaporates and evaporates by exchanging heat with the indoor air, becomes low-pressure gas refrigerant, and returns to the compressor 201 again.
- bubbles may be generated in the liquid pipe 207 connecting the outdoor coil 202 and the expansion valve 203 depending on the installation conditions and operating conditions of the apparatus. Then, when the bubbles become large and a slag flow or a plug flow is generated in the refrigerant, the liquid refrigerant and the gas refrigerant alternately flow through the throttle portion 219. In this case, the flow rate fluctuation and pressure fluctuation of the refrigerant increased, and as a result, an abnormal noise was generated near the outlet of the expansion valve 203 due to the refrigerant flow. A similar problem exists during the heating operation of the heat pump air conditioner.
- Patent Document 1 discloses a configuration in which a porous body or an assembly of microtubules is provided near the outlet of the throttle portion
- Patent Document 2 discloses a configuration in which microtubules are bundled near the outlet of the throttle portion.
- -A configuration in which a cam pipe, a molecular sieve, or the like is provided is disclosed.
- a method of changing the shape of the flow path near the outlet of the throttle is disclosed.
- the inner diameter near the outlet of the orifice forming the valve hole is increased stepwise or continuously, or is tapered, and a groove is provided on the inner peripheral surface of the valve hole. It is disclosed in Reference 1. Furthermore, there is also known a method (conventional C method) in which the throttle part has a two-stage structure and an intermediate pressure is generated between the stages to disperse the flow energy of the refrigerant. Specifically, Patent Document 3 discloses a configuration in which an orifice having a two-stage structure is disposed in the throttle portion of the refrigerant flow path. Furthermore, Patent Document 4 discloses a method (conventional D method) in which the throttle portion has a one-stage structure and the throttle portion forms a plurality of refrigerant flow path forces.
- Patent Document 1 Japanese Patent Laid-Open No. 7-146032
- Patent Document 2 Japanese Patent Laid-Open No. 11-325658
- Patent Document 3 Japanese Patent Laid-Open No. 5-322381
- Patent Document 4 Japanese Patent Laid-Open No. 5-288286
- An object of the present invention is to provide an expansion valve capable of reducing abnormal noise generated when a gas-liquid two-phase refrigerant flow passing through a throttle portion without impairing reliability, and a refrigeration equipped with the expansion valve Is to provide a device.
- a valve body an inlet port and an outlet port formed in the valve body, and a valve formed in the valve body
- a refrigerant flow passage formed in the valve body, connecting the inlet port and the outlet port via the valve chamber, a valve body housed in the valve chamber, and the refrigerant flow passage.
- a first throttle portion formed, and a second throttle portion formed downstream of the first throttle portion of the refrigerant flow passage, wherein the valve body allows the refrigerant flow in the refrigerant flow passage to flow.
- the first valve hole is formed between the first valve hole and the outer peripheral surface of the rod-shaped member.
- a first valve body part that forms a throttle part and a second valve body part that forms the second throttle part are formed between the second valve hole, and the first throttle part is formed by the first valve.
- the opening degree can be changed by advancing and retracting the first valve body part with respect to the valve seat of the hole.
- a groove is formed on the inner peripheral surface of the valve hole, and at least one of the outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole is formed in a tapered shape by directing the tip of the valve body,
- the second throttle portion is a passage force formed between the groove and the outer peripheral surface of the second valve body portion facing the groove or the inner peripheral surface of the second valve hole.
- At least one of the outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole is directed toward the distal end portion of the valve body to form a tapered shape.
- the first throttle portion can be fully closed by moving the first valve body portion forward and backward with respect to the valve seat of the first valve hole. In this case, since the first throttle part can be fully closed, the necessary throttle amount can be sufficiently ensured until the first throttle part is fully closed.
- the outer peripheral surface of the second valve body part and the inner peripheral surface of the second valve hole may both be tapered toward the tip of the valve body.
- the opening of the second throttle portion is increased, the amount of change in the gap between the one surface having the groove and the other surface facing this surface is reduced.
- the passage constituting the second throttle portion which is related to the opening degree of the second throttle portion, can effectively act on the refrigerant. Therefore, even if the opening of the second throttle portion is increased, the effect of suppressing the flow rate fluctuation and pressure fluctuation of the refrigerant is sufficiently exerted.
- the taper angles of the outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole are the same.
- the cross-sectional area of the refrigerant passage which also has a helical groove force, does not change greatly depending on the valve opening, so the effect of subdividing the bubbles in the refrigerant is stably exhibited.
- the groove is formed on an outer peripheral surface of the second valve body portion. In that case, the groove can be easily processed.
- the valve body has the first valve body portion at a distal end portion and the second valve body portion at an intermediate portion.
- the outer diameter of the second valve body is increased, design restrictions such as the total length of the grooves and the number of grooves are eased. As a result, the design for reducing the flow rate fluctuation and pressure fluctuation of the refrigerant becomes easy.
- an enlarged space portion is formed in a refrigerant flow passage extending from the first throttle portion to the second throttle portion.
- the vortex is likely to be generated in the refrigerant flow after passing through the first throttle portion. The generation of this vortex consumes the kinetic energy of the refrigerant flow, effectively mitigating refrigerant flow velocity fluctuations and pressure fluctuations.
- the first valve body portion includes a guide portion for deflecting the refrigerant flow that has passed through the first valve hole in the enlarged space portion.
- the kinetic energy of the refrigerant flow ejected from the first throttle part is easily consumed, and the flow rate fluctuation and pressure fluctuation of the refrigerant flowing in the second throttle part are more likely. Alleviated.
- the groove is a spiral groove
- the second throttle portion is an outer peripheral surface of the second valve body portion facing the spiral groove or the second valve hole. It is preferable to form a spiral passage formed between the peripheral surface and the peripheral surface. In this case, since the entire length of the passage constituting the second throttle portion is increased, the kinetic energy of the refrigerant can be effectively consumed, and the flow rate fluctuation and pressure fluctuation of the refrigerant are further alleviated.
- the first valve body portion is formed at a distal end portion of the valve body
- the second valve body portion is formed at an intermediate portion of the valve body
- the second valve body portion is formed.
- the inner peripheral surface of the second valve hole is formed in a tapered shape with a force directed toward the tip of the valve body, and the groove is a spiral groove.
- the downstream end of the second valve body part is preferably disposed in the second valve hole within a range from the minimum value to the maximum value of the opening of the second throttle part. In this case, it is possible to avoid unnecessarily disturbing the refrigerant flow rectified by the second throttle portion.
- a first valve body portion is formed at a distal end portion of the valve body
- a second valve body portion is formed at an intermediate portion of the valve body
- an outer periphery of the second valve body portion The surface and the inner peripheral surface of the second valve hole are tapered toward the tip of the valve body, the groove is a spiral groove, and the refrigerant extends from the first throttle part to the second throttle part.
- An enlarged space portion is formed in the passage near the inlet of the second valve hole, and the upstream end of the second valve body portion is within a range of a minimum value force and a maximum value of the opening degree of the second throttle portion. It is preferable to arrange in the expansion space.
- the spiral groove is preferably formed on the outer peripheral surface of the second valve body portion. In this case, the spiral groove can be easily processed.
- the second valve body portion and the second valve hole have the same taper angle. In that case, when the opening degree of the second throttle portion is increased, the amount of change in the gap between the one surface having the groove and the other surface facing this surface is reduced. Therefore, the spiral passage constituting the second throttle portion related to the opening degree of the second throttle portion can be effectively acted on the refrigerant.
- a taper angle of the first valve body portion is larger than a taper angle of the second valve hole.
- the throttle effect of the first throttle part can be changed more greatly than that of the second throttle part as the valve body is advanced and retracted.
- the taper angle of the second valve hole is preferably in the range of 5 degrees to 60 degrees. In this case, when the second throttle part is fully opened, the foreign matter trapped in the gap between the screw thread of the spiral groove and the inner peripheral surface of the second valve hole is removed.
- a gap between the first valve body part and the first valve hole formed in the vicinity of the outlet of the first throttle part is the second valve formed in the second throttle part. It is preferably smaller than the minimum value of the gap between the valve body and the second valve hole. In that case, the aperture effect of the first aperture
- the fruit can be made larger than the squeezing effect of the second squeezing part, and it can be reduced by suppressing clogging of foreign matter.
- a connecting portion is provided on the downstream side of the second valve body portion of the valve body, and the diameter of the connecting portion is larger than the diameter of the maximum outer peripheral portion of the second valve body portion. Is preferably small. In that case, it is possible to reduce the flow rate of the refrigerant flowing through the second throttle portion force pipe so that the refrigerant flow is not disturbed near the outlet port.
- a second different-diameter joint portion is formed between the connection portion and the second valve body portion, and the second different-diameter joint portion is the maximum outer circumference. It is preferable that the taper is formed in a tapered manner from the portion toward the connecting portion. In this case, it is possible to prevent the refrigerant rectified by the second throttle part from being disturbed, and thereby the generation of noise due to the refrigerant flow is further reduced.
- the second valve body portion force between the upstream end portion of the second valve body portion and the downstream end portion of the first valve body portion is the first valve body portion. It is preferable that a first different diameter joint portion having a taper shape is formed, and a taper angle of the first different diameter joint portion is larger than a taper angle of the first valve body portion. In this case, it becomes easy to form the first and second valve holes with appropriate diameters.
- the second valve body portion is formed by forming the spiral groove on the outer peripheral surface of the rod-shaped member, and then scraping the top of the screw thread of the spiral groove. It is preferably formed in a tapered shape toward the tip of the valve body. In that case, if the opening of the second throttle part is reduced, the cross-sectional area of the spiral passage is also reduced. Therefore, the opening degree of the second throttle portion is adjusted by the length of the spiral groove and the cross-sectional area of the spiral groove.
- the second valve body portion is formed by tapering the outer peripheral surface of the rod-shaped member toward the tip of the valve body, and then forming the spiral on the outer peripheral surface.
- the groove is formed by processing. In that case, it becomes easy to make the surface connecting the tops of the threads of the spiral groove into a tapered surface.
- the spiral groove preferably has a plurality of spiral groove forces.
- the refrigerant that is ejected by the first throttle force is dispersed in the plurality of spiral passages, and accordingly, the kinetic energy of the refrigerant flow can be dispersed. Also flows out from each spiral passage Since the flow velocity fluctuation and pressure fluctuation of the refrigerant are different, the refrigerant flowing out of each spiral passage collides with each other, and the flow velocity fluctuation and pressure fluctuation of the refrigerant are canceled, so that the generation of noise due to the refrigerant flow is effectively prevented. It is suppressed.
- the valve seat has a wall surface force of the first partition wall projecting around the first valve hole.
- the kinetic energy of the refrigerant flow ejected from the first throttle portion can be further consumed. Therefore, the flow velocity fluctuation and pressure fluctuation of the refrigerant flowing to the second throttle portion are further relaxed.
- the groove is a plurality of linear grooves extending in the advancing and retreating direction of the valve body, and the second throttle portion is opposed to the linear groove and the linear groove.
- the refrigerant ejected from the first throttle part is dispersed in each linear passage, and accordingly, the kinetic energy of the refrigerant flow can be dispersed.
- the refrigerant flowing out from each linear passage are different, the refrigerant flowing out from each linear passage force collides with each other, and the flow velocity fluctuation and pressure fluctuation of the refrigerant cancel each other. Generation of abnormal noise due to is effectively suppressed.
- the valve body forward and backward, the length of the overlapping portion between the groove and the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion can be changed. Accordingly, it is possible to simultaneously change the refrigerant flow resistance in the first throttle part and the refrigerant flow resistance in the second throttle part. Therefore, since the ratio of the refrigerant flow resistance is maintained in an appropriate range between the first throttle part and the second throttle part, it is possible to stabilize the generation of noise due to the refrigerant flow in the vicinity of the outlet of the expansion valve. Reduced.
- the linear grooves are preferably formed at equal intervals.
- a refrigeration apparatus includes the expansion valve. In that case, it is possible to realize a refrigeration apparatus that generates less noise due to the refrigerant flow.
- a valve body, a refrigerant flow passage formed in the valve body, a valve body housed in the valve body and made of a rod-shaped member, and the refrigerant flow A first throttle part formed in the passage, and a second throttle part formed upstream of the first throttle part of the refrigerant flow passage, and the valve body is formed in the refrigerant flow passage.
- a second valve hole is formed in the partition wall, an outer peripheral surface of the valve body is formed in a tapered shape, and the valve body includes a first valve body portion capable of contacting the valve seat of the first valve hole.
- a second valve body portion facing an inner peripheral surface of the second valve hole, and the first throttle portion has an opening degree by moving the first valve body portion forward and backward with respect to the first valve hole.
- the second throttle part may be a spiral groove formed on an outer peripheral surface of the second valve body part or an inner peripheral surface of the second valve hole, and an outer peripheral surface of the second valve body part or the second 2 A spiral passage formed between the inner peripheral surface of the valve hole, and at least one of the outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole is at the tip of the valve body. It is formed in a tapered shape due to the force.
- At least one of the outer peripheral surface of the second valve body and the inner peripheral surface of the second valve hole is a tapered surface. For this reason, when the opening of the first throttle part is reduced, the opening of the second throttle part is also reduced, and foreign objects are easily trapped.On the other hand, when the opening of the first throttle part is increased, the second throttle part is The opening is also increased, and the entrapped foreign matter is easily washed away by the refrigerant. Therefore, clogging of foreign matter is avoided, and problems such as malfunction of the valve body do not occur.
- the first throttle portion can be fully closed by moving the first valve body portion back and forth with respect to the first valve hole. In that case, the first throttle can be fully closed Therefore, it is possible to secure a sufficient amount of aperture necessary for fully closing the first aperture.
- the outer peripheral surface of the second valve body part and the inner peripheral surface of the second valve hole may both be tapered toward the tip of the valve body.
- the opening of the second throttle portion is increased, the amount of change in the gap between the one surface having the groove and the other surface facing this surface is reduced.
- the passage constituting the second throttle portion which is related to the opening degree of the second throttle portion, can effectively act on the refrigerant. Therefore, even if the opening of the second throttle portion is increased, the effect of suppressing the flow rate fluctuation and pressure fluctuation of the refrigerant is sufficiently exerted.
- the taper angles of the outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole are the same. In that case, since the cross-sectional area of the spiral passage does not change greatly depending on the opening of the valve, the effect of subdividing the bubbles is stably exhibited.
- the spiral groove is formed on an outer peripheral surface of the second valve body portion. In that case, the groove can be easily processed.
- the valve body has the first valve body portion at a distal end portion and the second valve body portion at an intermediate portion.
- the outer diameter of the second valve body is increased, design restrictions such as the total length of the grooves and the number of grooves are eased. As a result, the flow rate fluctuation and pressure fluctuation of the refrigerant in the second throttle portion are further alleviated.
- an enlarged space portion is formed in the refrigerant passage from the second throttle portion to the first valve hole in the vicinity of the inlet of the first valve hole.
- a vortex is generated in the refrigerant flow after passing through the first throttle part in the enlarged space part.
- the kinetic energy of the refrigerant flow is consumed by the generation of vortices, and the flow velocity fluctuation and pressure fluctuation of the refrigerant are further alleviated.
- the valve body has the first valve body portion at a tip portion, the second valve body portion at an intermediate portion, an outer peripheral surface of the second valve body portion, and The inner peripheral surface of the second valve hole is tapered toward the tip of the valve body, and the upstream end of the second valve body is the minimum value force maximum value of the opening of the second throttle part. It is preferable that the second valve hole is disposed within a range of up to. In that case, avoiding unnecessarily disturbing the refrigerant flow rectified by the second throttle it can.
- a first valve body portion is formed at a distal end portion of the valve body
- a second valve body portion is formed at an intermediate portion of the valve body
- an outer periphery of the second valve body portion The surface and the inner peripheral surface of the second valve hole are tapered toward the tip of the valve body, and the inlet of the first valve hole is formed in the refrigerant passage from the second throttle part to the first valve hole.
- An enlarged space portion is formed in the vicinity, and the downstream end portion of the second valve body portion is disposed in the enlarged space portion within a range from the minimum value to the maximum value of the opening degree of the second throttle portion. It is preferable.
- the spiral groove is formed on an outer peripheral surface of the second valve body portion. In this case, the spiral groove can be easily processed.
- the second valve body portion and the second valve hole have the same taper angle. In that case, when the opening degree of the second throttle portion is increased, the amount of change in the gap between the one surface having the groove and the other surface facing this surface is reduced. Therefore, the spiral passage constituting the second throttle portion related to the opening degree of the second throttle portion can be effectively acted on the refrigerant.
- a taper angle of the first valve body portion is larger than a taper angle of the second valve hole.
- the throttle effect of the first throttle part can be changed more greatly than that of the second throttle part as the valve body is advanced and retracted.
- the taper angle of the tapered surface of the second valve hole is preferably in the range of 5 degrees to 60 degrees. In this case, when the second throttle part is fully opened, the foreign matter trapped in the gap between the screw thread of the spiral groove and the inner peripheral surface of the second valve hole is removed.
- a gap between the first valve body part and the first valve hole formed in the vicinity of the inlet of the first throttle part is the second valve formed in the second throttle part. It is preferably smaller than the minimum value of the gap between the valve body and the second valve hole. In that case, the squeezing effect of the first squeezing part can be made larger than that of the second squeezing part, and clogging of foreign matter can also be suppressed.
- a connecting portion is provided upstream of the second valve body portion of the valve body, and the diameter of the connecting portion is larger than the diameter of the maximum outer peripheral portion of the second valve body portion. It is also preferable that it is small. In that case, the second throttle force can also reduce the flow velocity of the refrigerant flowing in the pipe, and the refrigerant flow is not disturbed unnecessarily near the inlet port.
- a taper shape is formed between the connecting portion and the second valve body portion by applying a force from the maximum outer peripheral portion of the second valve body portion to the outer peripheral portion of the connecting portion. It is preferable that two different diameter joints are formed. In this case, the refrigerant rectified by the second throttle part is less likely to be disturbed, and the generation of noise due to the refrigerant flow is further reduced.
- the second valve body portion force between the downstream end portion of the second valve body portion and the upstream end portion of the first valve body portion is the first valve body portion. It is preferable that a first different diameter joint portion having a taper shape is formed, and a taper angle of the first different diameter joint portion is larger than a taper angle of the first valve body portion. In this case, it becomes easy to form the first and second valve holes with appropriate diameters.
- the spiral groove is threaded after the outer peripheral surface of the second valve body portion or the inner peripheral surface of the second valve hole is formed in parallel with the central axis of the valve body, It is preferable that the surface connecting the tops of the threads is formed so as to form a tapered surface by forming the top of the threads. In that case, if the opening of the second throttle part is reduced, the cross-sectional area of the spiral passage is also reduced. Therefore, the opening degree of the second throttle portion can be adjusted by the length of the spiral groove and the cross-sectional area of the spiral groove.
- the spiral groove is preferably formed by forming the outer peripheral surface of the valve body into a tapered shape and threading the processed surface. In that case, it becomes easy to make the surface connecting the tops of the threads of the spiral groove into a tapered surface.
- the valve seat is formed by projecting a periphery of the first valve hole from a wall surface portion of the first partition wall.
- the refrigerant that is ejected by the first throttle force is dispersed in the plurality of spiral passages, and accordingly, the kinetic energy of the refrigerant flow can be dispersed.
- the flow velocity fluctuation and pressure fluctuation of the refrigerant flowing out of each spiral passage force are different, the refrigerant flowing out of each helical passage collides with each other, and the flow velocity fluctuation and pressure fluctuation of the refrigerant cancel each other.
- the spiral groove preferably has a plurality of spiral groove forces. In that case, since the refrigerant flow is disturbed and the bubbles are further subdivided, the generation of noise due to the refrigerant flow is further reduced. In addition, if some of the spiral grooves are clogged with foreign substances, the refrigerant flows through the other spiral grooves, so the reliability against clogging of foreign substances can be improved.
- a refrigeration apparatus includes the expansion valve. In that case, it is possible to realize a refrigeration apparatus that generates less noise due to the refrigerant flow.
- FIG. 1 is a partial cross-sectional view of an expansion valve according to a first embodiment of the present invention.
- FIG. 2 is a partial cross-sectional view of an expansion valve according to a second embodiment of the present invention.
- FIG. 3 is a partial sectional view of an expansion valve according to a third embodiment of the present invention.
- FIG. 5 is a partial cross-sectional view of an expansion valve according to a fifth embodiment of the present invention.
- FIG. 6 is a partial sectional view of an expansion valve according to a sixth embodiment of the present invention.
- FIG. 7 is a partial sectional view of an expansion valve according to a seventh embodiment of the present invention.
- FIG. 8 is a partial sectional view of an expansion valve according to an eighth embodiment of the present invention.
- FIG. 9 is a partial sectional view of an expansion valve according to a ninth embodiment of the present invention.
- FIG. 10 is a partial sectional view of an expansion valve according to a tenth embodiment of the present invention.
- FIG. 11 is a partial sectional view of an expansion valve according to an eleventh embodiment of the present invention.
- FIG. 12 is a partial cross-sectional view of an expansion valve according to a twelfth embodiment of the present invention.
- FIG. 13 is a cross-sectional view taken along line 13-13 in FIG.
- FIG. 14 is a partial cross-sectional view of an expansion valve according to a thirteenth embodiment of the present invention.
- FIG. 15 is a sectional view taken along line 15-15 in FIG.
- FIG. 16 is a partial sectional view of an expansion valve according to a fourteenth embodiment of the present invention.
- FIG. 17 is a cross-sectional view taken along line 17-17 in FIG.
- FIG. 18 is a partial cross-sectional view of an expansion valve according to a fifteenth embodiment of the present invention.
- FIG. 19 is a partial sectional view of an expansion valve according to a sixteenth embodiment of the present invention.
- FIG. 20 is a partial sectional view showing a state in which the opening degree of the expansion valve according to the seventeenth embodiment of the present invention is minimum.
- FIG. 21 is a partial sectional view showing a state in which the opening degree of the expansion valve according to the seventeenth embodiment of the present invention is maximum.
- FIG. 22 is an enlarged partial sectional view of an expansion valve according to a seventeenth embodiment of the present invention.
- FIG. 23 is a block diagram showing a refrigerant circuit of a conventional separate type air conditioner.
- FIG. 24 is a partial sectional view schematically showing an expansion valve of a refrigerant circuit.
- the expansion valve includes a valve body 1, and the valve body 1 is formed with an inlet port la and an outlet port lb.
- the valve body 1 has a substantially cylindrical shape, in which a valve chamber 2 and a refrigerant flow passage 3 are formed.
- the inlet port la and the outlet port lb communicate with each other via the valve chamber 2 and the refrigerant flow passage 3.
- a valve body 4 is accommodated in the valve chamber 2, a valve body 4 is accommodated.
- a first throttle portion 5 is provided on the upstream side of the refrigerant flow passage 3, and a second throttle portion 6 is provided on the downstream side.
- a liquid pipe 7 that connects the outdoor coil and the expansion valve is connected to the inlet port la, and a pipe 8 that connects the expansion valve and the indoor coil is connected to the outlet port lb.
- the inlet port la is provided at the lower part of the valve body 1
- the outlet port lb is provided on the side wall of the valve body 1
- the refrigerant flows along the arrow direction indicated by the solid line in FIG. Flowing inside.
- a first partition wall 10 is formed at a position corresponding to the first throttle portion 5, and a second partition wall 11 is formed at a position corresponding to the second throttle portion 6.
- the first and second partition walls 10 and 11 both extend along the direction intersecting the refrigerant flow.
- a first valve hole 12 is formed in the first partition wall 10, and a second valve hole 13 having a larger diameter than the first valve hole 12 is formed in the second partition wall 11.
- the refrigerant flow passage 3 is tapered from the second partition wall 11 (second valve hole 13) toward the first partition wall 10 (first valve hole 12).
- the valve body 4 has a substantially cylindrical connecting portion 14 in the upper part, a second valve body part 16 in the middle part, and a lower part in the lower part.
- a conical first valve body 15 is provided.
- the valve body 4 is arranged coaxially with the valve body 1 and is supported so as to be movable in the vertical direction.
- the valve body 4 is drivingly connected to a pulse motor (not shown) via a connecting portion 14.
- the first valve body portion 15 has a tapered shape by directing force at the tip thereof.
- a groove is formed in a spiral shape.
- the spiral groove 17 is formed by threading the outer peripheral surface of the second valve body portion 16 after forming the second valve body portion 16 in a conical shape.
- the outer peripheral surface of the second valve body portion 16 where the screw thread of the spiral groove 17 is located is a taper surface.
- the taper angle of the outer peripheral surface of the second valve body portion 16 is smaller than the taper angle of the outer peripheral surface of the first valve body portion 15.
- the second throttle portion 6 is formed from the outer peripheral surface of the second valve body portion 16, the inner peripheral surface of the second valve hole 13, and the spiral passage 18.
- the spiral passage 18 is a space surrounded by the spiral groove 17 of the second valve body portion 16 and the inner peripheral surface of the second valve hole 13.
- the taper angle of the outer peripheral surface of the second valve body part 16 is the same as the taper angle of the inner peripheral surface of the second valve hole 13. In this case, the outer peripheral surface of the second valve body portion 16 and the inner peripheral surface of the second valve hole 13 are parallel to each other.
- the speed of the refrigerant flowing from the second throttle portion 6 to the pipe is reduced, and the kinetic energy of the refrigerant flow is reduced. Therefore, the speed fluctuation and pressure fluctuation of the refrigerant are suppressed to be small, and the generation of noise due to the refrigerant flow is further reduced in the vicinity of the outlet of the expansion valve.
- the second throttle portion 6 includes a spiral passage 18. In this case, since the entire length of the second throttle portion 6 becomes long, the kinetic energy of the refrigerant flow can be effectively lost. Therefore, the flow rate fluctuation and pressure fluctuation of the refrigerant are further reduced, and the generation of noise due to the refrigerant flow is further reduced near the outlet of the expansion valve.
- Both the outer peripheral surface of the second valve body portion 16 and the inner peripheral surface of the second valve hole 13 are tapered toward the tip of the valve body 4. In this case, when the opening degree of the first throttle portion 5 is reduced, the gap between the second valve body portion 16 and the second valve hole 13 is also minimized, and foreign matter is easily trapped in the gap.
- the spiral groove 17 constituting the spiral passage 18 is formed on the outer peripheral surface of the second valve body portion 16. In that case, the spiral groove 17 can be easily processed.
- the spiral groove 17 is formed by forming the tip of the rod-like member in a tapered shape and threading the tapered surface. In this case, the taper surface can be easily processed.
- the valve body 4 has a first valve body portion 15 at the tip portion and a second valve body portion 16 at the intermediate portion. Thereby, the outer diameter of the second valve body portion 16 can be increased, and design restrictions such as the length, width, and depth of the spiral groove 17 are eased. Therefore, the design of the spiral groove 17 constituting the second throttle portion 6 is facilitated.
- the refrigerant flow passage 3 is partitioned by the first and second partition walls 10 and 11, and with respect to the first and second valve holes 12 and 13 of the first and second partition walls 10 and 11.
- One valve body 4 is driven.
- a first throttle portion 5 is formed between the first valve hole 12 and the first valve body portion 15, and a first passage including a spiral passage 18 is provided between the second valve hole 13 and the second valve body portion 16. 2
- the throttle part 6 is formed. In this case, the configuration of the expansion valve having a two-stage throttle portion is simplified.
- the expansion valve includes a valve main body 21, and the valve main body 21 is formed with an inlet port 21a and an outlet port 21b.
- the valve body 21 has a substantially cylindrical shape, and a valve chamber 22 and a refrigerant flow passage 23 are formed therein.
- the inlet port 21 a and the outlet port 21 b are communicated with each other via the valve chamber 22 and the refrigerant flow passage 23.
- a valve body 24 is accommodated in the valve chamber 22.
- a first throttle portion 25 is provided on the upstream side of the refrigerant flow passage 23, and a second throttle portion 26 is provided on the downstream side.
- a liquid pipe 27 that connects the outdoor coil and the expansion valve is connected to the inlet port 21a, and a pipe 28 that connects the expansion valve and the indoor coil is connected to the outlet port 21b.
- an inlet port 21a is provided on the side wall of the valve body 21, and an outlet port 21b is provided on the lower portion of the valve body 21.
- the coolant flows along the arrow direction indicated by the solid line in FIG. It flows in 21.
- a first partition wall 30 is formed at a position corresponding to the first throttle portion 25, and a second partition wall 31 is formed at a position corresponding to the second throttle portion 26.
- the first and second partition walls 30 and 31 both extend along the direction intersecting the refrigerant flow.
- a second valve hole 33 is formed in the second partition wall 31, and a first valve hole 32 having a larger diameter than the second valve hole 33 is formed in the first partition wall 30.
- the inner peripheral surface of the second valve hole 33 forms a taper shape toward the outlet port 21b!
- the valve body 24 includes a connecting part 34 at the upper part, a first valve body part 35 at the intermediate part, and a second valve body part 36 at the lower part.
- the valve body 24 is arranged coaxially with the valve body 21 and is supported so as to be movable in the vertical direction.
- the valve body 24 is drivingly connected to a pulse motor (not shown) via a connecting portion 34.
- the first valve body portion 35 has a tapered shape with a force directed to the tip thereof.
- a groove is formed in a spiral shape.
- the spiral groove 37 is formed by threading the tapered surface of the second valve body portion 36 after forming the second valve body portion 36 in a conical shape.
- the taper angle of the outer peripheral surface of the second valve body portion 36 is smaller than the taper angle of the outer peripheral surface of the first valve body portion 35.
- the outer peripheral surface of the second valve body 36 and the second valve hole 3 The second throttle portion 26 is formed from the inner peripheral surface of 3 and the spiral passage 38.
- the spiral passage 38 is a space surrounded by the spiral groove 37 of the second valve body portion 36 and the inner peripheral surface of the second valve hole 33.
- the taper angle of the outer peripheral surface of the second valve body 36 is the same as the taper angle of the inner peripheral surface of the second valve hole 33.
- the outer peripheral surface of the second valve body portion 36 and the inner peripheral surface of the second valve hole 33 are parallel to each other.
- the speed of the refrigerant flowing from the second throttle 26 to the pipe is reduced, and the kinetic energy of the refrigerant flow is reduced. Therefore, the speed fluctuation and pressure fluctuation of the refrigerant are suppressed to be small, and the generation of noise due to the refrigerant flow is reduced near the outlet of the expansion valve.
- the second throttle portion 26 includes a spiral passage 38.
- the entire length of the second throttle portion 26 becomes long, the kinetic energy of the refrigerant flow can be effectively lost. Therefore, the flow rate fluctuation and pressure fluctuation of the refrigerant are further reduced, and the generation of noise due to the refrigerant flow is further reduced near the outlet of the expansion valve.
- Both the outer peripheral surface of the second valve body portion 36 and the inner peripheral surface of the second valve hole 33 are tapered toward the tip of the valve body 24.
- the opening degree of the first throttle portion 25 is reduced, the gap between the second valve body portion 36 and the second valve hole 33 is also reduced, so that foreign matters are easily trapped in the gap.
- this gap also increases, so that foreign matters can be easily washed away by the cooling medium. In this way, clogging of foreign matter in the gap can be suppressed, and malfunction of the valve body 24 can be avoided.
- the spiral groove 37 is formed on the outer peripheral surface of the second valve body portion 36.
- the spiral groove 37 is formed by forming the tip of a rod-like member in a tapered shape and threading the tapered surface. In this way, the taper surface can be easily processed.
- the refrigerant flow passage 23 is partitioned by the first and second partition walls 30 and 31, and the first valve hole 32 and the second valve hole 33 of the first and second partition walls 30 and 31.
- One valve element 4 is driven.
- the first throttle 25 is formed between the first valve hole 32 and the first valve body 35
- the spiral passage 38 is formed between the second valve hole 33 and the second valve body 36.
- a second throttle part 26 including is formed. In this case, the configuration of the expansion valve including the two-stage throttle portion is simplified.
- an enlarged space portion 41 is formed between the first valve hole 12 and the second throttle portion 6.
- the inner diameter of the refrigerant flow passage 3 is partially enlarged. According to this configuration, in the enlarged space portion 41, vortices are generated in the coolant flow that has passed through the first throttle portion 5, so that the kinetic energy of the coolant flow can be effectively lost. Therefore, the speed fluctuation and pressure fluctuation of the refrigerant flow are further reduced, and the generation of noise due to the refrigerant flow is further reduced near the outlet of the expansion valve.
- a first taper portion 15 a is formed at the tip of the first valve body portion 15. Further, in the first valve body portion 15, a second tapered portion 15b is formed on the proximal end side with respect to the first tapered portion 15a. The taper angle of the first taper portion 15a is smaller than the taper angle of the second taper portion 15b.
- a tapered surface portion composed of both tapered portions 15a and 15b is configured as a guide portion. According to this configuration, the guide portion deflects the refrigerant flow that has passed through the first valve hole 12 in the enlarged space portion 41 (broken arrows shown in FIG. 4).
- a valve seat 43 is provided around the first valve hole 12 so that the wall surface of the first partition wall 10 protrudes upward.
- a vortex formation space 44 is formed between the valve seat 43 and the wall surface of the refrigerant flow passage 3.
- the outer peripheral surface of the second valve body portion 46 is a smooth tapered surface, while the spiral groove 48 is formed on the inner peripheral surface of the second valve hole 47.
- a space surrounded by the spiral groove 48 and the outer peripheral surface of the second valve body portion 46 is formed as the spiral passage 49.
- the outer peripheral surface of the second valve body portion 36 is a smooth tapered surface, while the spiral groove 53 is formed on the inner peripheral surface of the second valve hole 52.
- a space surrounded by the spiral groove 53 and the outer peripheral surface of the second valve body portion 51 is formed as the spiral passage 54. According to this configuration, the same operational effects as those of the second embodiment are exhibited.
- a spiral groove 57 is formed in the second valve body portion 56.
- the spiral groove 17 first forms the outer peripheral surface of the second valve body portion 56 in parallel with the center line of the valve body 4. Then, after threading the outer peripheral surface of the second valve body portion 56, the top of the thread of the spiral groove 57 so that the outer peripheral surface of the second valve body portion 56 tapers toward the tip of the valve body 4. Sharpen.
- the outer peripheral surface of the second valve body portion 56 is a surface connecting the tops of the threads of the spiral groove 57 and is a tapered surface.
- a spiral passage 57 is formed between the spiral groove 55 and the second valve hole 13, and the cross-sectional area thereof becomes smaller toward the tip of the valve body 4.
- the opening degree of the second throttle portion 6 when the opening degree of the second throttle portion 6 is reduced, the cross-sectional area of the spiral passage 57 is also reduced.
- the opening degree (throttle amount) of the second throttle portion 6 is adjusted by the length of the spiral groove 55 and the cross-sectional area of the spiral groove 55.
- a spiral groove 61 is formed in the second valve body portion 62.
- the outer peripheral surface of the second valve body portion 62 is formed in parallel with the center line of the valve body 24. Then, after threading the outer peripheral surface of the second valve body part 62, the outer peripheral surface of the second valve body part 62 becomes the valve body.
- the top of the screw thread of the spiral groove 61 is cut so as to taper toward the tip of 24.
- the outer peripheral surface of the second valve body portion 62 is a surface connecting the tops of the threads of the spiral groove 61 and is a taper surface.
- a spiral passage 63 is formed between the spiral groove 61 and the inner peripheral surface of the second valve hole 33, and its cross-sectional area becomes smaller toward the tip of the valve body 24. According to this configuration, when the opening of the second throttle portion 26 is reduced, the cross-sectional area of the spiral passage 63 is also reduced accordingly. In this case, the opening degree (aperture amount) of the second throttle portion 26 is adjusted by the length of the spiral groove 61 and the cross-sectional area of the spiral groove 61.
- the inner peripheral surface of the second valve hole 65 is formed in parallel with the center line of the valve body 4.
- a spiral passage 66 is formed between the outer peripheral surface of the second valve body portion 16 and the inner peripheral surface of the second valve hole 65.
- the outer peripheral surface of the second valve body portion 68 is formed in parallel with the center line of the valve body 4.
- a spiral groove 67 is formed on the outer peripheral surface of the second valve body portion 68.
- the spiral groove 67 is formed by threading the outer peripheral surface of the second valve body portion 68 after forming the outer peripheral surface of the second valve body portion 68 in parallel with the center line of the valve body 4.
- a spiral passage 69 is formed between the spiral groove 67 and the inner peripheral surface of the second valve hole 13. According to this configuration, the size of the gap between the second valve body portion 68 and the inner peripheral surface of the second valve hole 13 is changed according to the opening degree of the first and second throttle portions 5 and 6.
- the second valve body portion 71 is formed in a tapered shape from the intermediate portion of the valve body 4 toward the tip.
- Four linear grooves 72 extending along the axis of the valve body 4 are formed at equal intervals on the inner peripheral surface of the second valve hole 13.
- Each of the linear grooves 72 has a triangular shape with the same shape and the same dimensions.
- the inner diameter of the second valve hole 13 is set to a dimension that allows the second valve body portion 71 and the second valve hole 13 to slide when the throttle amount of the second throttle portion 6 is maximum. Thereby, a plurality of refrigerant passages constituting the second throttle portion 6 are independently formed between the linear groove 72 and the second valve body portion 71.
- the first throttle 5 and the second throttle 6 on the downstream side reduce the amount of pressure reduction of the first throttle 5. This reduces the ejection energy of the refrigerant ejected from the first throttle 5. Further, the refrigerant ejected from the first throttle portion 5 is dispersed in the plurality of linear passages 73, and accordingly, the kinetic energy of the refrigerant flow is also dispersed. Since the refrigerant that has passed through each linear passage 73 becomes a turbulent flow, the flow velocity fluctuation and pressure fluctuation of the refrigerant are further alleviated. Further, the flow rate fluctuation and pressure fluctuation of the refrigerant flowing out from each linear passage 73 are different.
- the cooling medium can be evenly distributed in the linear passages 73, and the kinetic energy of the refrigerant flow can be further effectively improved. Can be dispersed.
- first valve body portion 15 is formed at the distal end portion of the valve body 4 and the second valve body portion 71 is formed at the intermediate portion, the outer diameter of the second valve body portion 71 and The inner diameter of each second valve hole 13 can be increased. This relaxes design constraints such as the length, width, or depth of the linear groove 72. Therefore, the design for reducing the flow rate fluctuation and pressure fluctuation of the refrigerant passing through the second throttle portion 6 becomes easy.
- the refrigerant flow passage 3 is partitioned by the first and second partition walls 10 and 11, and with respect to the first and second valve holes 12 and 13 of the first and second partition walls 10 and 11.
- One valve body 4 is driven.
- the first throttle part 5 is formed between the first valve hole 12 and the first valve body part
- the second throttle part 6 is formed between the second valve hole 13 and the second valve body part 16. It is formed.
- the structure of the tension valve is simplified.
- the second valve body portion 75 is formed in a tapered shape by directing the tip of the valve body 24.
- On the inner peripheral surface of the second valve hole 33 four linear grooves 76 extending along the axis of the valve body 24 are formed at equal intervals.
- Each of the linear grooves 76 has a substantially triangular cross section having the same shape and the same dimensions.
- the inner diameter of the second valve hole 33 is set to a dimension that allows the second valve body part 75 and the second valve hole 33 to slide when the throttle amount of the second throttle part 26 is maximum. Accordingly, a plurality of refrigerant passages constituting the second throttle portion 26 are formed independently between the linear groove 76 and the second valve body portion 75.
- the flow rate fluctuation and pressure fluctuation of the refrigerant flowing out from each linear passage 77 are different. Therefore, the refrigerant flowing out from each linear passage 77 collides with each other, so that the flow velocity fluctuation and pressure fluctuation of the refrigerant are effectively reduced. Therefore, the kinetic energy, speed fluctuation, and pressure fluctuation of the refrigerant flow flowing from the second throttle 26 to the pipe are further reduced, and the generation of noise due to the refrigerant flow is further reduced near the outlet of the expansion valve.
- the refrigerant flow passage 23 is partitioned by the first and second partition walls 30 and 31, and is connected to the first and second valve holes 31, 33 of the first and second partition walls 30, 31.
- One valve body 24 is driven.
- the second throttle portion 26 is formed between the first valve hole 32 and the first valve body portion 35. In this case, the configuration of the expansion valve having a two-stage throttle portion is simplified.
- linear grooves 82 are formed at equal intervals on the outer peripheral surface of the second valve body portion 81.
- the inner peripheral surface of the second valve hole 83 is a smooth tapered surface having no groove.
- Four linear passages 84 are formed independently between the linear groove 82 and the inner peripheral surface of the second valve hole 83. According to this configuration, the linear groove 82 can be processed more easily than in the twelfth embodiment. [0133] (Fifteenth embodiment)
- the outer peripheral surface of the second valve body 85 is formed in parallel with the central axis of the valve body 24.
- the second valve hole 33 is formed in a tapered shape by directing the tip of the valve body 24.
- a plurality of linear grooves 76 are formed on the inner peripheral surface of the second valve hole 33.
- a plurality of linear passages 86 are independently formed between the outer peripheral surface of the second valve body 85 and the inner peripheral surface of the second valve hole 33.
- the size of the gap between the outer peripheral surface of the second valve body portion 85 and the inner peripheral surface of the second valve hole 33 is changed by opening and closing the valve body 24 and opening and closing the second throttle portion 26. . That is, by increasing the degree of opening of the second restrictor 26, foreign matter trapped in the gap between the outer peripheral surface of the second valve body 85 and the inner peripheral surface of the second valve hole 13 is easily caused by the refrigerant flow. Can be washed away.
- the inner peripheral surface of the second valve hole 91 is formed in parallel with the central axis of the valve body 4.
- a plurality of linear grooves 92 having a triangular cross section are formed on the inner peripheral surface of the second valve hole 91.
- a plurality of linear passages 93 are independently formed between the outer peripheral surface of the second valve body 71 and the inner peripheral surface of the second valve hole 91.
- the size of the gap between the outer peripheral surface of the second valve body portion 16 and the inner peripheral surface of the second valve hole 91 is changed by opening and closing the valve body 4 and opening and closing the second throttle portion 6. . That is, by increasing the opening degree of the second throttle portion 6, the foreign matter trapped in the gap can be easily washed and flowed by the refrigerant flow.
- the taper angle ⁇ 1 of the second valve body portion 16 and the taper of the second valve hole 13 The angle oc 2 is the same.
- the taper angle oc2 of the second valve hole 13 is preferably approximately 5 degrees to approximately 60 degrees.
- the lower limit of 5 degrees for the taper angle ⁇ 2 is the lower limit of the taper angle a2 that can remove foreign matter trapped in the gap between the thread of the spiral groove 17 and the inner peripheral surface of the second valve hole 13. is there.
- the upper limit value of the taper angle ⁇ 2 of 60 degrees is a value of the taper angle ⁇ 2 based on the length required for forming the spiral groove 17.
- the taper angle a 1 and the taper angle ex 2 are each about 25 degrees.
- the downstream end of the second valve body 16 is within the range from the minimum value (state shown in Fig. 20) to the maximum value (state shown in Fig. 21) of the opening of the second throttle portion 6. Arranged in the valve hole 13. That is, the position XI of the downstream end portion of the second valve body portion 16 is always lower than the position Y1 of the downstream end portion of the second valve hole 13 related to the opening degree of the second throttle portion 6.
- the downstream end of the second valve body portion 16 is connected to the connecting portion 14 via the second different diameter joint portion 96.
- the diameter d2 of the connecting portion 14 is smaller than the diameter dl of the maximum outer peripheral portion of the second valve body portion 16.
- the maximum outer peripheral portion of the second valve body portion 16 is continuously connected to the connecting portion 14 via the second different diameter joint portion 96.
- the second different diameter joint 96 is tapered from the second valve body 16 to the connecting part 14! RU
- the upstream end of the second valve body 16 extends from the minimum value (state shown in Fig. 20) to the maximum value (state shown in Fig. 21). 41. That is, the position X2 of the upstream end portion of the second valve body portion 16 is within the range of the minimum value force maximum value of the opening degree of the second throttle portion 6, and the position Y2 of the upstream end portion of the second valve hole 13 Is always below.
- the first valve body portion 15 is formed in a tapered shape toward the tip of the valve body 4.
- 81 of the first valve body portion 15 is larger than the taper angle ⁇ 2 of the second valve hole 13.
- a first different diameter joint portion 95 is provided between the second valve body portion 16 and the first valve body portion 15.
- the first different-diameter joint portion 95 is formed in a tapered shape by directing force from the second valve body portion 16 to the first valve body portion 15.
- the taper angle ⁇ 2 of the first different diameter joint portion 95 is larger than the taper angle ⁇ 1 of the first valve body portion 15.
- the gap S1 between the first valve body 15 and the first valve hole 12 is smaller than the minimum gap S2 between the second valve body 16 and the second valve hole 13.
- the gap S 1 between the first valve body 15 and the first valve hole 12 indicates the shortest distance between the first valve body 15 and the outlet side corner of the first valve hole 12.
- the second valve body 16 and the second valve hole 13 The minimum gap S2 indicates the shortest distance between the second valve body portion 16 and the second valve hole 13.
- the taper angle a 1 of the second valve body part 16 is the same as the taper angle a 2 of the second valve hole 13.
- the upstream end portion of the second valve body portion 16 is arranged in the enlarged space portion 41 within the range from the minimum value to the maximum value of the opening degree of the second throttle portion 6.
- the refrigerant can be smoothly circulated from the enlarged space portion 41 to the second throttle portion 6. Thereby, the generation of noise due to the refrigerant flow is further reduced.
- the spiral passage 18 constituting the second throttle portion 6 can be effectively acted on the refrigerant regardless of the opening degree of the second throttle portion 6.
- the taper angle ⁇ 2 of the second valve hole 13 is preferably in the range of approximately 5 degrees to approximately 60 degrees. In this case, it is possible to easily remove the foreign matter caught in the gap between the screw thread of the spiral groove 17 and the inner peripheral surface of the second valve hole 13. In addition, a sufficient length of the spiral groove 17 can be secured.
- the gap S1 between the first valve body portion 15 and the first valve hole 12 is smaller than the minimum gap S2 between the outer peripheral surface of the second valve body portion 16 and the second valve hole 13. For this reason, the aperture effect of the first aperture section 5 can be changed significantly more than that of the second aperture section 6, and clogging of foreign matters due to the second aperture section 6 can also be suppressed. Therefore, for example, the first diaphragm unit 5 and the second diaphragm unit 6 have different functions, such as the first diaphragm unit 5 as the main diaphragm unit and the second diaphragm unit 6 as the noise suppression unit. The optimal design of the expansion valve can be realized.
- the diameter d2 of the connecting portion 14 is smaller than the diameter dl of the maximum outer peripheral portion of the second valve body portion 16. Therefore, the flow rate of the refrigerant flowing from the second throttle 6 to the pipe can be reduced. As a result, the refrigerant flow is not unnecessarily disturbed near the outlet port lb, and the generation of noise due to the refrigerant flow can be reduced.
- a second different diameter joint portion 96 is formed between the connecting portion 14 and the second valve body portion 16.
- the disturbance generated in the refrigerant flow in the valve body 1 can be further suppressed. Therefore, the generation of noise due to the refrigerant flow is further reduced.
- a first different diameter joint portion 95 is formed between the upstream end portion of the second valve body portion 16 and the downstream end portion of the first valve body portion 15. Further, the taper angle 2 of the first different diameter joint portion 95 is larger than the taper angle
- the outlet port lb is provided at the lower part of the valve body 1, and the inlet port la is provided on the side wall of the valve body 1, thereby allowing the refrigerant to flow along the arrow direction indicated by the broken line in FIG. May be washed away.
- the inlet port 21a is provided at the lower part of the valve body 21, and the outlet port 21b is provided on the side wall of the valve body 21, thereby allowing the refrigerant to flow in the direction indicated by the broken line in FIG. You may flow along.
- the outlet port lb is provided in the lower part of the valve body 1, and the inlet port la is provided in the side wall of the valve body 1, thereby allowing the refrigerant to flow in the direction indicated by the broken line in FIG. It may flow along.
- the inlet port la is provided in the lower part of the valve body 1, and the outlet port lb is provided in the side wall of the valve body 1, thereby allowing the refrigerant to flow in the direction indicated by the broken line in FIG. It may flow along.
- all of the second throttle portions have spiral passage forces, and the passage lengths thereof are sufficiently secured, so that pressure fluctuations in the gas-liquid two-phase flow can be suppressed. Further, while the refrigerant flows while swirling along the spiral path, the bubbles in the refrigerant are subdivided. Such bubble fragmentation occurs when the refrigerant flow rate is low with a low refrigeration load, that is, in the second throttle section. This is also sufficient when the gap between the spiral groove with a small opening and the inner peripheral surface of the second valve hole is small.
- the first throttle portion can be fully closed, it is possible to sufficiently secure the throttle amount necessary to fully close the first throttle portion. In addition, it is possible to prevent clogging of foreign substances as compared with the conventional method A.
- the outer peripheral surface of the second valve body part and the inner peripheral surface of the second valve hole are both tapered toward the tip of the valve body. In this case, even if the opening of the second throttle portion is increased, the amount of change in the gap between the spiral groove and the inner peripheral surface of the second valve hole can be minimized. Therefore, it becomes easy to maintain the shape of the spiral passage related to the opening of the second throttle portion, and the effect of subdividing the bubbles by the spiral passage is sufficiently exhibited.
- the outer peripheral surface of the second valve body and the inner peripheral surface of the second valve hole both have the same taper angle. For this reason, it becomes easier to maintain the shape of the spiral passage related to the opening of the second throttle portion, and the effect of subdividing the bubbles by the spiral passage is stably exhibited.
- valve body has a first valve body portion at a tip portion and a second valve body portion at an intermediate portion.
- the spiral groove is formed in the outer peripheral surface of the 2nd valve body part. In this case, if the outer diameter of the second valve body is increased, the length of the spiral passage is sufficiently secured.
- the inlet port la is provided in the lower part of the valve body 1, and the outlet port lb is provided in the side wall of the valve body 1, thereby allowing the refrigerant to flow along the arrow direction indicated by the broken line in FIG. May be flown.
- the refrigerant flow that has passed through the second throttle 6 in the enlarged space 41 is Being disturbed, the bubbles in the refrigerant are further subdivided. Thereby, generation
- the outlet port lb is provided at the lower part of the valve body 1, and the inlet port la is provided on the side wall of the valve body 1, so that the refrigerant flows along the arrow direction indicated by the broken line in FIG. May be flown.
- a swirling flow is generated in the refrigerant flow from the second throttle portion 6 toward the first valve hole 12, and the bubbles in the refrigerant are further subdivided. Thereby, generation
- the outlet port lb is provided at the lower part of the valve body 1, and the inlet port la is provided on the side wall of the valve body 1, so that the refrigerant flows along the arrow direction indicated by the broken line in FIG. May be washed away.
- the inlet port la is provided at the lower part of the valve body 1, and the outlet port lb is provided on the side wall of the valve body 1, thereby allowing the refrigerant to flow in the direction indicated by the broken line in FIG. It may flow along.
- the outlet port lb is provided at the lower part of the valve body 1, and the inlet port la is provided on the side wall of the valve body 1, so that the refrigerant flows in the direction indicated by the broken line in FIG. It may be washed away.
- the outlet port lb is provided at the lower part of the valve body 1, and the inlet port la is provided on the side wall of the valve body 1, thereby allowing the refrigerant to flow in the direction indicated by the broken line in FIG. You can also shoot it.
- an outlet port lb is provided at the bottom of the valve body 1, and the valve body 1 side
- the refrigerant may flow along the arrow direction indicated by the broken lines in FIGS.
- the upstream end portion of the second valve body portion 16 is disposed in the second valve hole 13 within the range from the minimum value to the maximum value of the opening degree of the second throttle portion 6. In this case, it is possible to prevent the refrigerant flow from being disturbed by the second valve body portion 16 before the bubbles in the refrigerant are subdivided by the spiral passage 18.
- the downstream end of the second valve body portion 16 is disposed in the enlarged space portion 41 within the range in which the minimum value force of the opening degree of the second throttle portion 6 is also up to the maximum value.
- the refrigerant can be smoothly circulated from the spiral passage 18 to the enlarged space portion 41.
- the gas-liquid two-phase flow becomes a turbulent flow in the enlarged space portion 41, and the bubbles in the refrigerant are subdivided. Therefore, the generation of noise due to the refrigerant flow can be further reduced.
- the outer peripheral surface of the second valve body portion 16 and the inner peripheral surface of the second valve hole 9 are both tapered toward the tip of the valve body 4, and the taper angles thereof are the same. is there. In this case, since the spiral passage 18 does not change greatly depending on the opening degree of the second valve body portion 16, the bubbles in the refrigerant can be stably subdivided.
- the gap S1 between the first valve body 15 and the first valve hole 12 is related to the opening of the first throttle part 5 and the second throttle part 6, and the second valve body part 16 and the second valve It is smaller than the minimum gap S2 with the hole 13.
- the aperture effect of the first aperture section 5 is greater than that of the second aperture section 6, and it is possible to suppress clogging of foreign matter caused by the second aperture section 6.
- the diameter d2 of the connecting portion 14 is smaller than the diameter dl of the maximum outer peripheral portion of the second valve body portion 16. In this case, since the refrigerant flow flowing into the valve body 1 is not hindered by the connecting portion 12, the generation of noise due to the refrigerant flow is further effectively reduced.
- the expansion valve may be used in a multi-type air conditioner in which a plurality of indoor units are connected to a single outdoor unit.
- a multi-type air conditioner in which a plurality of indoor units are connected to a single outdoor unit.
- the expansion valve of the present invention is used in a multi-type air conditioner, the generation of abnormal noise due to the refrigerant flow can be more effectively reduced.
- the first throttle parts 5 and 25 may be used within a range not fully closed. Further, the first throttle portions 5 and 25 may be configured not to be fully closed.
- the enlarged space portion 41 shown in the third embodiment may be formed.
- the flow rate fluctuation and pressure fluctuation of the refrigerant are alleviated, so that the generation of noise due to the refrigerant flow is more effectively reduced in the vicinity of the outlet of the expansion valve.
- the enlarged space portion 41 shown in the third embodiment is formed, and the guide portion shown in the fourth embodiment is the first valve body portion 15 May be provided.
- the generation of vortices is promoted in the enlarged space portion 41, the generation of noise due to the refrigerant flow is more effectively reduced near the outlet of the expansion valve.
- the valve seat 43 shown in the fifth embodiment is formed, and the vortex forming space 44 for swirling the refrigerant is formed. May be. In these cases, since the generation of vortices is promoted in the vortex formation space 44, the generation of noise due to the refrigerant flow can be effectively reduced near the outlet of the expansion valve.
- the inner peripheral surfaces of 7 and 52 may be surfaces parallel to the central axes of the valve bodies 4 and 24.
- the inner peripheral surfaces of the second valve holes 13, 33, 83 are surfaces parallel to the central axes of the valve bodies 4, 24. It may be.
- the threaded surfaces of the spiral grooves 17, 37, 55, 61 are the centers of the valve bodies 4, 24. It may be a plane parallel to the line.
- the inner peripheral surfaces of the second valve holes 47, 52 are formed parallel to the center line of the valve body 24, and the spiral grooves 48, 53 are formed in the second valve holes 47, It may be formed on the inner peripheral surface of 52.
- the outer peripheral surface of the second valve body portion 16 is formed in parallel with the center line of the valve body 4, and the second valve body portion 16
- the outer peripheral surface of the second valve body part 16 is directed toward the tip of the valve body 14 by cutting the outer peripheral surface of the second valve body part 16 by cutting the top of the thread of the spiral groove 17. You may form in a taper shape. In these cases, the opening degree of the second throttle portion 6 is adjusted by the length and cross-sectional area of the spiral groove 17.
- the inner peripheral surfaces of the second valve holes 47, 52 are formed parallel to the center line of the valve body 24, and the inner peripheral surfaces of the second valve holes 47, 52 are spiraled. Grooves 48, 53 are formed, then spiral grooves 4
- the tops of the 8 and 53 threads may be shaved. In these cases, the length of spiral grooves 48 and 53 The opening degree of the second throttle parts 6 and 26 is adjusted according to the cross-sectional area.
- a plurality of spiral grooves 17, 37, 48, 53, 55, 61, 67 of the second throttle portions 6, 26 are provided and formed in parallel. Also good. In these cases, the flow rate and pressure fluctuations of the refrigerant are more effective by colliding with the refrigerant channels 18, 38, 49, 54, 57, 63, 66, and 69, which flow out from each other. Reduced to
- the cross-sectional shape of the linear grooves 72, 76, 82, 92 may be any shape such as a circle, an oval, an ellipse, or a U-shape.
- the cross-sectional areas of the linear grooves 72, 76, 82, 92 may be changed, and the cross-sectional areas of the respective linear passages 73, 77, 84, 86, 93 may be changed.
- the total number of the linear grooves 72, 76, 82, 92 may be changed to change the total cross-sectional area of each of the linear grooves 72, 76, 82, 92.
- a plurality of linear grooves may be provided independently in the second valve body portions 75, 85 and 71, respectively.
- the inner peripheral surface of the second valve hole 33 may be a surface parallel to the central axis of the valve body 24.
- the outer peripheral surface of the second valve body portion 71 may be a surface parallel to the central axis of the valve body 4.
- the second valve body parts 16, 36, 46, 51, 56, 62 and the inner peripheral surfaces of the second valve holes 13, 33, 47, 52 The taper angle may be varied.
- the taper angles of the outer peripheral surface of the second valve body portions 71, 75, 81 and the inner peripheral surface of the second valve holes 13, 33, 83 may be different from each other. .
- the spiral groove 17 may be formed on the inner peripheral surface of the second valve hole 13.
- the expansion valve and the refrigeration apparatus of the present invention may be applied to an air conditioner such as an integral type, a separate type, or a multi-type, or a refrigerant circuit other than the air conditioner (for example, a refrigerant circuit such as a refrigerator Road).
- an air conditioner such as an integral type, a separate type, or a multi-type, or a refrigerant circuit other than the air conditioner (for example, a refrigerant circuit such as a refrigerator Road).
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Details Of Valves (AREA)
- Lift Valve (AREA)
- Temperature-Responsive Valves (AREA)
- Electrically Driven Valve-Operating Means (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/883,238 US7832653B2 (en) | 2005-02-28 | 2006-02-28 | Expansion valve having a grooved valve member and refrigeration device including the same |
AU2006219331A AU2006219331C1 (en) | 2005-02-28 | 2006-02-28 | Expansion valve and refrigeration device |
EP06714881A EP1857748A4 (en) | 2005-02-28 | 2006-02-28 | EXPANSION VALVE AND REFRIGERATION DEVICE |
Applications Claiming Priority (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005054979 | 2005-02-28 | ||
JP2005-054979 | 2005-02-28 | ||
JP2005104397 | 2005-03-31 | ||
JP2005-104397 | 2005-03-31 | ||
JP2005362501A JP3824019B1 (ja) | 2005-02-28 | 2005-12-15 | 膨張弁及び冷凍装置 |
JP2005-362501 | 2005-12-15 | ||
JP2005362502A JP3826951B1 (ja) | 2005-03-31 | 2005-12-15 | 膨張弁及び冷凍装置 |
JP2005-362502 | 2005-12-15 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006093149A1 true WO2006093149A1 (ja) | 2006-09-08 |
Family
ID=36941178
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/303751 WO2006093149A1 (ja) | 2005-02-28 | 2006-02-28 | 膨張弁及び冷凍装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7832653B2 (ja) |
EP (1) | EP1857748A4 (ja) |
KR (1) | KR100877032B1 (ja) |
AU (1) | AU2006219331C1 (ja) |
WO (1) | WO2006093149A1 (ja) |
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JPWO2017077769A1 (ja) * | 2015-11-06 | 2018-06-21 | 株式会社日立製作所 | 弁構造並びにこれを有する油圧機器及び流体機械並びに機械 |
JP2019027566A (ja) * | 2017-08-03 | 2019-02-21 | 株式会社栗本鐵工所 | スリーブ弁 |
JP2021055711A (ja) * | 2019-09-27 | 2021-04-08 | 株式会社鷺宮製作所 | 電動弁及び冷凍サイクルシステム |
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CN109682022B (zh) * | 2018-12-26 | 2021-03-19 | 青岛海信日立空调系统有限公司 | 一种膨胀阀控制方法及装置、空调系统 |
WO2020255192A1 (ja) * | 2019-06-17 | 2020-12-24 | 三菱電機株式会社 | 冷凍サイクル装置 |
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Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH10205927A (ja) * | 1997-01-17 | 1998-08-04 | Denso Corp | 電動式膨張弁 |
JPH11325658A (ja) * | 1998-05-08 | 1999-11-26 | Matsushita Seiko Co Ltd | 膨張弁 |
JP2002071241A (ja) * | 2000-08-30 | 2002-03-08 | Mitsubishi Heavy Ind Ltd | 空調装置及びその冷媒制御用絞り弁 |
JP2002122367A (ja) * | 2000-10-17 | 2002-04-26 | Denso Corp | 制御弁 |
JP2002195698A (ja) * | 2000-10-17 | 2002-07-10 | Denso Corp | ヒートポンプ用制御弁 |
JP2005069644A (ja) * | 2003-08-27 | 2005-03-17 | Daikin Ind Ltd | 多段電動膨張弁及び冷凍装置 |
JP2005351605A (ja) * | 2004-06-14 | 2005-12-22 | Daikin Ind Ltd | 膨張弁及び冷凍装置 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1112050A (en) * | 1912-10-11 | 1914-09-29 | Franz Max Berberich | Device for mixing and rendering liquids homogeneous. |
US4044991A (en) * | 1975-10-06 | 1977-08-30 | Consolidated Controls Corporation | High energy loss fluid flow control device |
JPH05288286A (ja) | 1992-04-07 | 1993-11-02 | Hitachi Ltd | 膨張弁 |
JPH05322381A (ja) | 1992-05-25 | 1993-12-07 | Mitsubishi Heavy Ind Ltd | 膨張弁装置 |
JPH07146032A (ja) | 1993-11-26 | 1995-06-06 | Matsushita Seiko Co Ltd | 膨張弁 |
JPH08334280A (ja) * | 1995-04-07 | 1996-12-17 | Fuji Koki Seisakusho:Kk | 膨張弁及び冷凍システム |
DE10139534A1 (de) * | 2001-08-10 | 2003-02-20 | Bosch Rexroth Ag | Schließkörper, insbesondere Ventilkegel für ein Stetigdruckventil |
US6981689B2 (en) * | 2004-04-08 | 2006-01-03 | Gueorgui Milev Mihaylov | Hybrid flow metering valve |
-
2006
- 2006-02-28 US US11/883,238 patent/US7832653B2/en not_active Expired - Fee Related
- 2006-02-28 KR KR1020077017206A patent/KR100877032B1/ko not_active IP Right Cessation
- 2006-02-28 AU AU2006219331A patent/AU2006219331C1/en not_active Ceased
- 2006-02-28 EP EP06714881A patent/EP1857748A4/en not_active Withdrawn
- 2006-02-28 WO PCT/JP2006/303751 patent/WO2006093149A1/ja active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH10205927A (ja) * | 1997-01-17 | 1998-08-04 | Denso Corp | 電動式膨張弁 |
JPH11325658A (ja) * | 1998-05-08 | 1999-11-26 | Matsushita Seiko Co Ltd | 膨張弁 |
JP2002071241A (ja) * | 2000-08-30 | 2002-03-08 | Mitsubishi Heavy Ind Ltd | 空調装置及びその冷媒制御用絞り弁 |
JP2002122367A (ja) * | 2000-10-17 | 2002-04-26 | Denso Corp | 制御弁 |
JP2002195698A (ja) * | 2000-10-17 | 2002-07-10 | Denso Corp | ヒートポンプ用制御弁 |
JP2005069644A (ja) * | 2003-08-27 | 2005-03-17 | Daikin Ind Ltd | 多段電動膨張弁及び冷凍装置 |
JP2005351605A (ja) * | 2004-06-14 | 2005-12-22 | Daikin Ind Ltd | 膨張弁及び冷凍装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1857748A4 * |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8152136B2 (en) * | 2007-11-26 | 2012-04-10 | The Hong Kong Polytechnic University | Polymer microvalve with actuators and devices |
JP2015072119A (ja) * | 2015-01-07 | 2015-04-16 | 三菱電機株式会社 | 電子膨張弁 |
JPWO2017077769A1 (ja) * | 2015-11-06 | 2018-06-21 | 株式会社日立製作所 | 弁構造並びにこれを有する油圧機器及び流体機械並びに機械 |
JP2019027566A (ja) * | 2017-08-03 | 2019-02-21 | 株式会社栗本鐵工所 | スリーブ弁 |
JP2021055711A (ja) * | 2019-09-27 | 2021-04-08 | 株式会社鷺宮製作所 | 電動弁及び冷凍サイクルシステム |
JP7145134B2 (ja) | 2019-09-27 | 2022-09-30 | 株式会社鷺宮製作所 | 電動弁及び冷凍サイクルシステム |
JP2022176224A (ja) * | 2019-09-27 | 2022-11-25 | 株式会社鷺宮製作所 | 電動弁及び冷凍サイクルシステム |
JP7383774B2 (ja) | 2019-09-27 | 2023-11-20 | 株式会社鷺宮製作所 | 電動弁及び冷凍サイクルシステム |
WO2024078720A1 (de) | 2022-10-13 | 2024-04-18 | Pierburg Gmbh | Expansionsventil |
Also Published As
Publication number | Publication date |
---|---|
KR100877032B1 (ko) | 2009-01-07 |
AU2006219331C1 (en) | 2009-05-28 |
AU2006219331A1 (en) | 2006-09-08 |
US20080282717A1 (en) | 2008-11-20 |
AU2006219331B2 (en) | 2009-01-08 |
EP1857748A1 (en) | 2007-11-21 |
US7832653B2 (en) | 2010-11-16 |
KR20070099001A (ko) | 2007-10-08 |
EP1857748A4 (en) | 2013-03-13 |
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