WO2015063854A1 - 膨張弁 - Google Patents
膨張弁 Download PDFInfo
- Publication number
- WO2015063854A1 WO2015063854A1 PCT/JP2013/079226 JP2013079226W WO2015063854A1 WO 2015063854 A1 WO2015063854 A1 WO 2015063854A1 JP 2013079226 W JP2013079226 W JP 2013079226W WO 2015063854 A1 WO2015063854 A1 WO 2015063854A1
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- WIPO (PCT)
- Prior art keywords
- valve
- refrigerant
- mesh
- expansion valve
- pipe
- Prior art date
Links
- 239000006261 foam material Substances 0.000 claims abstract description 14
- 239000012530 fluid Substances 0.000 claims description 8
- 230000004323 axial length Effects 0.000 claims description 6
- 239000003507 refrigerant Substances 0.000 description 147
- 239000007788 liquid Substances 0.000 description 24
- 230000000694 effects Effects 0.000 description 17
- 239000012071 phase Substances 0.000 description 14
- 239000002826 coolant Substances 0.000 description 10
- 239000003570 air Substances 0.000 description 6
- 238000001816 cooling Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 239000000126 substance Substances 0.000 description 4
- 238000004581 coalescence Methods 0.000 description 3
- 239000007791 liquid phase Substances 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000007791 dehumidification Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005187 foaming Methods 0.000 description 1
- 230000000704 physical effect Effects 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000005514 two-phase flow Effects 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
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
-
- 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
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
-
- 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
-
- 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
-
- 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
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/067—Expansion valves having a pilot valve
-
- 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 that reduces refrigerant passing sound and improves comfort against noise.
- a flow noise is generated when the refrigerant passes through the valve chamber.
- the refrigerant flowing into the valve chamber equipped with the valve body has a two-phase flow state in which the gas-phase refrigerant is mixed into the liquid-phase refrigerant. If large bubbles are present in the gas-phase refrigerant, a collision noise is generated when passing through the valve chamber, which causes noise. In order to reduce such refrigerant passing sound, various ideas and proposals have been made conventionally.
- a throttling device dehumidification valve
- the valve body is made of a porous permeable material that communicates in the refrigerant flow direction, and is equipped with adjusting means for adjusting the permeation area of the porous permeable material.
- This throttle device is assumed to be used in an air conditioner as a dehumidifying valve, so even when the valve seat and the valve body are in contact with each other and the flow path is blocked (fully closed), it is made of a porous material.
- the refrigerant can pass through the configured valve body. Therefore, it is said that the collision sound generated when the two-phase refrigerant collides with the valve body can be reduced (see, for example, Patent Document 1).
- a hollow refrigerant rectifying cylinder having a plurality of holes is arranged on the inner wall in the axial direction of the valve chamber, and both ends thereof are fixed to a main body and a support plate that form the valve chamber, so that the horizontal direction (radial direction)
- An expansion valve has been proposed in which an inflowing refrigerant is allowed to pass through a refrigerant rectifying cylinder so that a collision sound caused by a collision with a valve body can be suppressed (see, for example, Patent Document 3).
- Japanese Patent No. 3428516 (Claim 1, FIG. 2) Japanese Patent No. 4925638 (Claim 1, FIG. 1) Japanese Patent No. 3380395 (FIG. 1)
- the present invention has been made to solve the above-described problems, and it is an object of the present invention to obtain an expansion valve that can effectively reduce refrigerant passage noise even when gas-liquid two-phase refrigerant is supplied. Objective.
- An expansion valve includes a main body having a valve seat in the axial direction of the valve chamber, a valve body that can move in the axial direction of the valve chamber and is disposed to face the valve seat, and the valve body with respect to the valve seat.
- the shaft portion facing the first pipe is formed of a member having a mesh structure or a foam material, and the member having a mesh structure or a foam material is larger than the diameter of the shaft portion of the valve body, It has a cylindrical shape smaller than the inner diameter of the valve chamber and is housed in the valve chamber.
- the periphery of the shaft portion facing the first pipe of the valve body is composed of a member having a mesh structure or a member made of a foam material.
- the refrigerant flows through the pipe (forward flow)
- the refrigerant comes into contact with a member having a mesh structure or a member made of a foam material, the flow velocity is reduced, and an impact sound generated when the refrigerant collides with the valve body is reduced.
- the member having a mesh structure or the foamed material has a cylindrical shape larger than the diameter of the shaft portion of the valve body and smaller than the inner diameter of the valve chamber, and is stored in the valve chamber, so that the passage of the refrigerant.
- the area is large, and the refrigerant noise reduction effect is also increased.
- a mesh structure member or a member made of a foam material is provided around the shaft portion of the valve body and integrated with the valve body, the length to the throttle portion between the valve body and the valve seat ( The distance is shortened, and the reduced bubbles flow into the constricted portion before being combined and expanded, so that the refrigerant noise reduction effect is also increased.
- the refrigerant passes through a member having a mesh structure or a member made of a foam material, the bubble diameter can be reduced, and bubble vibration noise can be reduced. Moreover, the disturbance of the refrigerant can be suppressed, and the vortex noise can be reduced.
- the refrigerant that has been throttled and accelerated by passing between the valve body and the valve seat is a mesh structure member or foam material. Since it is decelerated by passing the member which becomes, the collision sound in a valve chamber wall surface can be reduced. Therefore, even when a two-phase refrigerant mixed with gas and liquid flows through the expansion valve, it is possible to reduce collision noise, intermittent noise, bubble vibration noise, and vortex noise caused by bubbles, and to reduce the noise of the expansion valve.
- FIG. 2 is a cross-sectional view showing a configuration of an expansion valve according to Embodiment 1 of the present invention, and a cross-sectional view taken along line AA. It is an expanded sectional view of the throttle part which shows the flow of the refrigerant of the expansion valve concerning Embodiment 1 of the present invention.
- FIG. 4 is a cross-sectional view showing a configuration of an expansion valve according to Embodiment 2 of the present invention, a cross-sectional view taken along line BB, and a perspective view of a second mesh member.
- Embodiment 1 FIG. The expansion valve according to the present invention will be described below with reference to the illustrated embodiment. In addition, this invention is not limited by the following embodiment.
- FIG. 1 is a refrigerant circuit diagram of an air-conditioning apparatus according to Embodiment 1 of the present invention.
- the air conditioner according to the embodiment of the present invention includes a compressor 1, a four-way valve 2, a condenser 3, a first expansion valve 4, a second expansion valve 5, and an evaporator 6 as refrigerant pipes as shown in FIG. Connected in series.
- the compressor 1, the four-way valve 2, the condenser 3, and the first expansion valve 4 are housed in a single box as an outdoor unit, and the second expansion valve 5 and the evaporator 6 are housed in a single box. Yes.
- FIG. 2 is a cross-sectional view showing the configuration of the expansion valve according to Embodiment 1 of the present invention and a cross-sectional view taken along the line AA. Since the first expansion valve 4 and the second expansion valve 5 have the same configuration, the first expansion valve 4 will be described as an example here.
- the first expansion valve 4 includes a main body 13 having a valve seat 12 in the axial direction of the valve chamber 11, and a valve body that can move in the axial direction of the valve chamber 11 and is opposed to the valve seat 12.
- valve drive means for advancing and retracting the valve body 14 by electromagnetic force to contact and separate from the valve seat 12, that is, a coil 15, and a first pipe 16 attached to the main body 13 in the horizontal direction (radial direction) And a second pipe 17 attached to the tip of the valve seat 12 and the main body 13 in the axial direction.
- the first pipe 16 and the second pipe 17 are made of, for example, a copper pipe and are brazed to the main body 13.
- the main body 13 is manufactured by cutting a brass casting.
- valve body 14 and the valve seat 12 are brought into contact with and separated from each other by the electromagnetic force of the coil 15, and the flow passage cross-sectional area between the valve seat 12 and the valve body 14 communicating from the first pipe 16 to the second pipe 17 is increased. Change.
- the valve element 14 and the valve seat 12 are in contact with each other and the valve element 14 is at the lowermost position so that the flow path is completely closed, the valve element 14 is at the uppermost part of the valve chamber 11.
- the case where the flow path width between the valve body 14 is maximum is defined as fully open.
- the valve body 14 is configured with a mesh structure member (hereinafter referred to as “mesh member”) 18 in part, that is, around the shaft portion 14a facing the first pipe 16.
- the mesh member 18 has a cylindrical shape that is larger than the diameter of the shaft portion 14 a of the valve body 14 and smaller than the inner diameter of the valve chamber 11, and is accommodated in the valve chamber 11.
- valve body 14 (particularly the tip portion thereof) in contact with the valve seat 12 is constituted by a non-mesh member that does not allow the refrigerant to pass therethrough.
- the mesh structure of the mesh member 18 is formed by, for example, crossing a plurality of steel wires and including a plurality of lattices (mesh).
- the audible limit frequency 20 kHz which is a high frequency range of a general audible range
- the bubble diameter at the audible limit Can be calculated. If the lattice length of the mesh is set to be equal to or less than the audible limit bubble diameter, the bubble vibration sound can be out of the audible range, and the refrigerant sound can be effectively suppressed. Accordingly, here, the mesh length of the mesh member 18 is set to be equal to or less than the audible limit bubble diameter.
- f frequency of the bubble
- R represents the radius of the bubble
- gamma is the specific heat ratio
- [rho w is medium density
- sigma is the surface tension.
- At least the outer shape of the mesh member 18 has a maximum valve chamber diameter, and the axial length of the mesh member 18 is a projection of the cross section of the first pipe 16 regardless of whether the valve element 14 is fully open or fully closed.
- the length is such that a part of the mesh member 18 can exist on the surface. In this way, by allowing the mesh member 18 to always exist on the projection plane of the cross section of the first pipe 16, in the forward flow in which the refrigerant flows from the first pipe 16 to the second pipe 17, Regardless, since the refrigerant flowing into the valve chamber 11 passes through the mesh member 18, the collision noise between the valve body 14 and the refrigerant can be effectively suppressed.
- the refrigerant circuit according to the first embodiment is a two-stage expansion circuit including a first expansion valve 4 and a second expansion valve 5.
- the refrigerant circulates in the order of the compressor 1, the four-way valve 2, the condenser 3, the first expansion valve 4, the second expansion valve 5, and the evaporator 6.
- the low-pressure gas refrigerant is pressurized to become a high-temperature and high-pressure gas refrigerant.
- the gaseous refrigerant passes through the four-way valve 2 and radiates heat to the ambient air in the condenser 3.
- the gas refrigerant is condensed by the heat radiation to the air, and becomes a liquid refrigerant whose temperature is lowered.
- the liquid refrigerant is decompressed by the first expansion valve 4 and becomes a low-pressure two-phase refrigerant.
- the liquid phase of the two-phase refrigerant is further expanded by the second expansion valve 5 and becomes a two-phase refrigerant having increased dryness.
- the evaporator 6 the refrigerant receives heat from the air and the liquid part evaporates.
- the gaseous refrigerant whose temperature has increased due to heat received from the air flows into the compressor 1 again.
- Refrigerant sounds can be broadly classified into sound sources such as bubble vibration sounds, collision sounds, vortex sounds, and jet sounds.
- the main purpose of the expansion valve according to the first embodiment is to suppress the influence of these sound sources and reduce refrigerant noise. *
- FIG. 3 is an enlarged cross-sectional view of the throttle portion showing the flow of the refrigerant of the expansion valve according to the first embodiment of the present invention, where (a) shows the forward flow and (b) shows the reverse flow.
- the symbols A1 to A5 in the figure indicate locations where the sound source reduction effect can be obtained, and correspond to the explanations of the following items (A1) to (A5).
- the flow of the refrigerant from the first pipe 16 (FIG. 2) to the second pipe 17 is forward flow
- the flow from the second pipe 17 to the first pipe 16 is reverse flow.
- the mesh member 18 has a mesh lattice length set to be equal to or smaller than the audible limit of the bubble diameter. For this reason, the bubble diameter is reduced by passing the refrigerant from the radial direction to the valve body axis direction, the generated bubble vibration sound is shifted outside the audible range, and the refrigerant sound in the audible range is reduced. Moreover, the mesh member 18 makes a gas-liquid uniform by letting a refrigerant pass, and reduces eddy noise. Since the outer diameter of the cylindrical mesh member 18 is substantially equal to the inner diameter of the valve chamber 11, the fluid passage area can be increased, and the effect of reducing the refrigerant noise and vortex noise is further increased.
- the axial length of the mesh member 18 is a length that can always exist on the projection plane of the cross section of the first pipe 16 regardless of whether the valve body 14 is in a fully open state or a fully closed state.
- the passing distance is long, and the effect of reducing the vortex noise is increased.
- valve body 14 which is one of the non-mesh members does not pass the refrigerant, it does not flow directly from the first pipe 16 to the second pipe 17 via the mesh member 18. Therefore, flow rate adjustment is easy.
- coolant sound in an audible range can be reduced.
- the outer diameter of the mesh member 18 is substantially equal to the inner diameter of the valve chamber 11, the fluid passage area can be increased, and the effect of reducing the refrigerant sound and vortex noise is further increased.
- the axial length of the mesh member 18 is a length that can always exist on the projection plane of the cross section of the first pipe 16 regardless of whether the valve body 14 is in a fully open state or a fully closed state. The passing distance is long, and the effect of reducing vortex noise is increased.
- the expansion valve according to Embodiment 1 of the present invention even when the two-phase refrigerant flows, the bubble vibration sound, the collision sound, the vortex sound, and the shunt sound that are the sound sources of the refrigerant sound can be suppressed, and the expansion valve The noise can be reduced.
- the natural frequency of the isomorphic high density substance and the low density substance is higher in the low density substance. Therefore, when the natural vibration is excited by fluid pressure fluctuation or other factors, high frequency sound is generated.
- the non-mesh member and the valve body are preferably made of highly dense substances. The same applies to other embodiments described below.
- FIG. 4 is a cross-sectional view showing a configuration of an expansion valve according to Embodiment 2 of the present invention, a cross-sectional view taken along line BB, and a perspective view of a second mesh member.
- the expansion valve according to Embodiment 2 of the present invention has a second mesh structure member (hereinafter referred to as a second mesh member) 20 at the end on the main body 13 side in the second pipe 17 as shown in FIG. Is provided.
- a second mesh structure member hereinafter referred to as a second mesh member
- the second mesh member 20 is provided with a frustoconical mesh member 22 inside a cylindrical non-mesh structure member 21, so that fluid can pass through the frustoconical mesh member 22, and
- the upper surface of the frustoconical mesh member 22 having a reduced diameter is configured to face the valve seat side.
- the lattice length of the mesh is set to be equal to or less than the audible limit bubble diameter, similarly to the cylindrical mesh member 18 of the first embodiment.
- the axial length of the second mesh member 20 corresponds to, for example, the distance from the valve seat 12 to the wall surface of the second pipe 17 in the state where the fluid velocity is maximum. It is set to length. For this reason, a refrigerant
- the diameter of the upper surface of the truncated cone-shaped mesh member 22 of the second mesh member 20 is equal to the orifice diameter of the valve seat 12, and the diameter of the lower surface is equal to the inner diameter of the second pipe 17. It is configured. For this reason, a refrigerant
- the outer periphery of the second mesh member 20 is composed of a cylindrical non-mesh structure member 21. Therefore, removal from the second piping 17 is easy.
- refrigerant sounds can be roughly classified into sound sources such as bubble vibration sounds, collision sounds, vortex sounds, and jet sounds.
- the expansion valve of the second embodiment also has the main purpose of suppressing the influence of these sound sources and reducing refrigerant noise.
- FIG. 5 is an enlarged cross-sectional view of the throttle part showing the refrigerant flow of the expansion valve according to the second embodiment of the present invention, where (a) shows the forward flow and (b) shows the reverse flow.
- the symbols B1 to B9 in the figure indicate locations where the sound source reduction effect can be obtained, and correspond to the explanations of the following items (B1) to (B9).
- the flow of the refrigerant from the first pipe 16 (FIG. 4) to the second pipe 17 is forward flow
- the flow from the second pipe 17 to the first pipe 16 is reverse flow.
- the valve element 14 has an intermediate opening degree that is fully open and fully closed in the forward flow, and the refrigerant flows from the first pipe 16 (FIG. 4) to the second pipe 17.
- the flow of the refrigerant at the locations B1 to B3 is the same as the flow of the refrigerant at the locations A1 to A3 described in the first embodiment, and the description of the above items (A1) to (A3) can be applied. Therefore, explanation is omitted.
- the frustoconical mesh member 22 of the second mesh member 20 reduces the bubble diameter by passing the refrigerant, and shifts the generated bubble vibration sound out of the audible range. For this reason, the refrigerant
- the refrigerant throttled and accelerated by the valve body 14 spreads in a divergent shape in the second pipe 17, but an orifice is formed between the second pipe 17 and the valve seat 12 as shown in FIG. 5. As a result, a reverse flow is generated on the throttle side, and a dead water area is generated.
- the second mesh member 20 is provided with the frustoconical mesh member 22 inside the cylindrical non-mesh structure member 21, so that the flow of the refrigerant is smooth.
- the length of the second mesh member 20 in the axial direction is a length corresponding to the distance from the valve seat 12 to the wall surface of the second pipe 17 in the state where the fluid velocity is maximum. Therefore, the refrigerant passes through the second mesh member 20 even under the maximum flow velocity. For this reason, refrigerant noise can be reduced.
- the valve element 14 has an intermediate opening degree of full opening and full closing in the reverse flow, and the refrigerant flows from the second pipe 17 to the first pipe 16.
- coolant in the location of B8 and B9 is the same as that of the refrigerant
- the second mesh member 20 arranged in the valve body axis direction allows the refrigerant to pass through, thereby reducing the bubble diameter and shifting the bubble vibration sound outside the audible range.
- the refrigerant coolant sound in an audible range can be reduced.
- the 2nd mesh member 20 makes a gas-liquid uniform by allowing a refrigerant to pass through, and reduces eddy noise.
- the refrigerant is gradually decompressed and immediately passes through the cylindrical mesh member 18 in the next valve chamber 11 even when foaming occurs due to the decompression. The sound reduction effect can be increased.
- FIG. FIG. 6 is a cross-sectional view showing a configuration of an expansion valve according to Embodiment 3 of the present invention, a cross-sectional view taken along the line CC, and a plan view of a second mesh member.
- the expansion valve according to Embodiment 3 of the present invention has a lattice length in which members of a second mesh structure (hereinafter referred to as second mesh members) 30 are arranged at intervals in the axial direction as shown in FIG. Are constituted by a plurality of types of mesh members 31, 32, 33.
- the second mesh member 30 is arranged so that the mesh length of the mesh members 31, 32, and 33 having different lattice lengths becomes shorter as the mesh member 31 approaches the main body 13.
- the minimum lattice length is set to be equal to or smaller than the audible limit bubble diameter described above.
- bubble vibration noise can be effectively reduced by setting the minimum lattice length to be equal to or smaller than the audible limit bubble diameter.
- refrigerant sounds can be roughly classified into sound sources such as bubble vibration sounds, collision sounds, vortex sounds, and jet sounds.
- the expansion valve of the third embodiment also has the main purpose of suppressing the influence of these sound sources and reducing refrigerant noise.
- FIG. 7 is an enlarged cross-sectional view of the throttle portion showing the flow of the refrigerant of the expansion valve according to the third embodiment of the present invention, where (a) shows the forward flow and (b) shows the reverse flow.
- the symbols C1 to C8 in the figure indicate locations where the sound source reduction effect can be obtained, and correspond to the description of the following items (C1) to (C8). Also here, the flow of the refrigerant from the first pipe 16 (FIG. 6) to the second pipe 17 is forward flow, and the flow from the second pipe 17 to the first pipe 16 is reverse flow.
- the second mesh member 30, particularly the mesh member 33 having the minimum lattice length allows the refrigerant to pass through, thereby reducing the bubble diameter and shifting the generated bubble vibration sound out of the audible range. For this reason, the refrigerant
- the valve element 14 has an intermediate opening degree between full open and full close, and the refrigerant flows from the second pipe 17 to the first pipe 16 (FIG. 6).
- the flow of the refrigerant at the locations C7 and C8 is the same as the flow of the refrigerant at the locations A4 and A5 described in the first embodiment, and the description of the items (A4) and (A5) can be applied. Therefore, explanation is omitted.
- the plurality of types of mesh members 31, 32, 33 arranged at intervals in the valve body axis direction reduce the bubble diameter by allowing the refrigerant to pass therethrough, and shift the bubble vibration sound outside the audible range.
- the refrigerant coolant sound in an audible range can be reduced.
- the plurality of types of mesh members 31, 32, and 33 allow the gas and liquid to become uniform and reduce eddy noise by allowing the refrigerant to pass therethrough. Since the bubble diameter is gradually reduced every time the refrigerant passes through the plurality of types of mesh members 31, 32, 33, the turbulent flow of the refrigerant can be further suppressed, and vortex noise can be reduced.
- the shaft portion 14a facing the first pipe 16 of the valve body 14 has been described with the mesh member 18 as an example.
- the present invention is not limited to this.
- a member made of a foam material may be integrally provided around the shaft portion 14a of the valve body 14. Even in this case, the effect of reducing the refrigerant passing sound can be obtained.
Abstract
Description
また、膨張弁として用いる場合には、弁体にて流路を完全に塞ぐことができるようにする必要があり、絞り部と弁体を通過する冷媒流れ両方を考慮して設計する必要があり、そのまま適用することはできない。
また、網目構造の部材または発泡材料でなる部材は、弁体の軸部の直径よりも大きく、弁室の内径よりも小さい円筒形状を有し、弁室内に収納されているので、冷媒の通過面積が大きく、冷媒音低減効果も大きくなる。
また、網目構造の部材または発泡材料でなる部材を、弁体の軸部の周りに設けて、弁体と一体化しているので、弁体と弁座との間の絞り部までの長さ(距離)が短かくなり、縮小された気泡が合体し拡大する前に絞り部に流入するため、冷媒音低減効果も大きくなる。
また、網目構造の部材または発泡材料でなる部材を冷媒が通過することで、気泡径を縮小させることができ、気泡振動音を低減できる。また、冷媒の乱れが抑制でき、渦音を低減できる。
また、第二の配管から第一の配管に冷媒が流れる場合(逆方向流れ)、弁体と弁座の間を通過することによって絞られ増速した冷媒が、網目構造の部材または発泡材料でなる部材を通過することで減速されるため、弁室壁面での衝突音を低減できる。
したがって、膨張弁に気液が混在する二相冷媒が流れた場合においても、気泡による衝突音、間欠音、気泡振動音、渦音を低減でき膨張弁を低騒音化することができる。
以下に、図示実施形態により本発明に係る膨張弁について説明する。なお、以下の実施形態により本発明が限定されるものではない。
本発明の実施形態に係る空気調和装置は、図1のように圧縮機1、四方弁2、凝縮器3、第一の膨張弁4、第二の膨張弁5、蒸発器6が冷媒配管にて直列に接続される。例えば冷房運転において、圧縮機1、四方弁2、凝縮器3、第一の膨張弁4は室外機、第二の膨張弁5、蒸発器6は室内機としてそれぞれ1つの箱体に収納されている。
第一の膨張弁4は、図2のように弁室11の軸方向に弁座12を有する本体13と、弁室11の軸方向に移動でき弁座12と対向して配置される弁体14と、弁体14を電磁力によって進退させ、弁座12に対して当接、離反させる弁駆動手段すなわちコイル15と、本体13に水平方向(径方向)に取り付けられる第一の配管16と、弁座12の先かつ本体13に軸方向に取り付けられる第二の配管17とを備える。第一の配管16と第二の配管17は、例えば銅管からなり、本体13とろう付けされている。本体13は真鍮製の鋳造品を切削加工して製造される。
冷房運転において、冷媒は圧縮機1、四方弁2、凝縮器3、第一の膨張弁4、第二の膨張弁5、蒸発器6の順に循環する。圧縮機1において、低圧の気体冷媒は昇圧され、高温高圧の気体冷媒となる。気体冷媒は、四方弁2を通過し凝縮器3において周囲空気に放熱する。空気への放熱により気体冷媒は凝縮し、温度が低下した液冷媒となる。液冷媒は、第一の膨張弁4で減圧されて低圧の二相冷媒となる。二相冷媒は、第二の膨張弁5によって更に液部が膨張し、乾き度の増加した二相冷媒となる。蒸発器6において、冷媒は空気から受熱し液部が蒸発する。空気からの受熱により温度が上昇した気体冷媒は、圧縮機1に再び流入する。
図3(a)のように正方向流れにおいて、弁体14は全開と全閉の中間開度とされ、冷媒は第一の配管16(図2)から第二の配管17に流れる。
(A1)膨張弁、例えば第一の膨張弁4は、第一の配管16の投影面の一部に網目部材18が存在するため、流体はまず網目部材18に接触し、流速が低下して、弁体14に衝突する。このため、弁体14に冷媒が衝突する際に生じる衝撃音を低減できる。
また、網目部材18は、冷媒を通過させることで、気液を均一化し、渦音を低減させる。円筒形状の網目部材18の外径は、弁室11の内径と略等しくしているため、流体の通過面積を大きくとれ、前記冷媒音及び渦音の低減効果は更に大きくなる。
また、網目部材18の軸方向長さは、弁体14が全開、全閉のいずれの状態にある場合でも常に第一の配管16の断面の投影面に存在できる長さとしてあるため、流体の通過距離が長く、前記渦音の低減効果は大きくなる。
また、非網目部材の1つである弁体14は冷媒を通さないため、第一の配管16から網目部材18を介して直接第二の配管17に流れることはない。そのため、流量調節が容易である。
図3(b)のように逆方向流れにおいて、弁体14は全開と全閉の中間開度とされ、冷媒は第二の配管17から第一の配管16(図2)に流れる。
(A4)非網目部材の1つである弁体14と弁座12との間を通過することにより絞られ増速した冷媒が、網目部材18を通過することで減速される。このため、弁室11の壁面での衝突音を低減できる。
(A5)網目部材18は、冷媒を弁体14の軸方向から径方向に通過させることで、気泡径を縮小させ、発生する気泡振動音を可聴域外にシフトさせる。このため、可聴域内の冷媒音を削減できる。網目部材18の外径は、弁室11の内径と略等しくしているため、流体の通過面積を大きくとれ、冷媒音及び渦音の低減効果は更に大きくなる。また、網目部材18の軸方向長さは、弁体14が全開、全閉のいずれの状態にある場合でも常に第一の配管16の断面の投影面に存在できる長さとしてあるため、流体の通過距離が長く、渦音の低減効果が大きくなる。
図4は本発明の実施形態2に係る膨張弁の構成を示す断面図、B-B線断面図、及び第二の網目部材の斜視図である。図中、前述の実施形態1と同じ機能部分には同じ符号を付してある。
本発明の実施形態2に係る膨張弁は、図4のように第二の配管17内の本体13側の端部に、第二の網目構造の部材(以下、第二の網目部材という)20を設けたものである。
図5(a)のように正方向流れにおいて弁体14は全開と全閉の中間開度とされ、冷媒は第一の配管16(図4)から第二の配管17に流れる。なお、B1~B3の箇所における冷媒の流れは、前述の実施形態1で説明したA1~A3の箇所における冷媒の流れと同様であり、前述の(A1)~(A3)項の説明を適用できるため説明を省略する。
(B4)非網目部材の1つである弁体14により絞られ増速した冷媒が、第二の網目部材20を通過することで、円錐台状の網目部材22によって減速されられるため、第二の配管17の壁面での衝突音を低減できる。
また、円錐台状の網目部材22は、冷媒を通過させることで、気液が均一化され、渦音を低減できる。弁体14によって絞られ増速した冷媒は、第二の配管17で末広がり状に広がるが、図5に示すように、第二の配管17と弁座12との間にオリフィスが形成されていると、絞り側に逆流する流れが発生し、死水域が発生する。死水域では渦が形成されるため、冷媒流れが乱れ、渦音を生じさせる。
本実施形態2に係る膨張弁は、第二の網目部材20が円筒状の非網目構造の部材21の内部に円錐台状の網目部材22を備えたものであるので、冷媒の流れがスムースになり、死水域の発生が抑制され、冷媒の乱れた流れが抑制でき、更に渦音を低減できる。
また、第二の網目部材20の軸方向長さを、流体の速度が最大の状態で、絞られた冷媒が弁座12から第二の配管17の壁面に衝突するまでの距離に相当する長さに設定してあるので、最大流速下においても、冷媒が第二の網目部材20を通過する。このため、冷媒音を低減できる。
図5(b)のように逆方向流れにおいて弁体14は全開と全閉の中間開度とされ、冷媒は第二の配管17から第一の配管16に流れる。なお、B8,B9の箇所における冷媒の流れは、前述の実施形態1で説明したA4,A5の箇所における冷媒の流れと同様であり、前述の(A4),(A5)項の説明を適用できるため説明を省略する。
(B6)弁体軸方向に配置された第二の網目部材20は、冷媒を通過させることで、気泡径を縮小させ、気泡振動音を可聴域外にシフトさせる。このため、可聴域内の冷媒音を削減できる。
また、第二の網目部材20は、冷媒を通過させることで、気液を均一化し、渦音を低減させる。冷媒は、第二の網目部材20を通過することで、緩やかに減圧され、減圧に伴い発泡が生じた際にも直ちに次の弁室11内の円筒形状の網目部材18を通過するため、冷媒音低減効果を大きくすることができる。
図6は本発明の実施形態3に係る膨張弁の構成を示す断面図、C-C線断面図、及び第二の網目部材の平面図である。図中、前述の実施形態1と同じ機能部分には同じ符号を付してある。
本発明の実施形態3に係る膨張弁は、図6のように第二の網目構造の部材(以下、第二の網目部材という)30を、軸方向に間隔を置いて配置された格子長さの異なる複数種の網目部材31,32,33で構成したものである。
図7(a)のように正方向流れにおいて弁体14は全開と全閉の中間開度とされ、冷媒は第一の配管16(図6)から第二の配管17に流れる。なお、C1~C3の箇所における冷媒の流れは、前述の実施形態1で説明したA1~A3の箇所における冷媒の流れと同様であり、前述の(A1)~(A3)項の説明を適用できるため説明を省略する。
(C4)非網目部材の1つである弁体14により絞られ増速した冷媒が、複数の第二の網目部材30を通過することで減速されるため、第二の配管17の壁面での衝突音を低減できる。第二の網目部材30、特に最小の格子長さを有する網目部材33は、冷媒を通過させることで、気泡径を縮小させ、発生する気泡振動音を可聴域外にシフトさせる。このため、可聴域内の冷媒音を削減できる。また、各第二の網目部材30を通過させることで、気液が均一化され、渦音を低減できる。
逆方向流れにおいて弁体14は全開と全閉の中間開度とされ、冷媒は第二の配管17から第一の配管16(図6)に流れる。なお、C7,C8の箇所における冷媒の流れは、前述の実施形態1で説明したA4,A5の箇所における冷媒の流れと同様であり、前述の(A4),(A5)項の説明を適用できるため説明を省略する。
(C5)弁体軸方向に間隔を置いて配置された複数種の網目部材31,32,33は、冷媒をこれらを通過させることで、気泡径を縮小させ、気泡振動音を可聴域外にシフトさせる。このため、可聴域内の冷媒音を削減できる。
また、複数種の網目部材31,32,33は、冷媒を通過させることで、気液が均一化し、渦音を低減させる。冷媒は、複数種の網目部材31,32,33を通過する毎に徐々に気泡径が縮小されるため、冷媒の乱れた流れを更に抑制でき、渦音を低減できる。
Claims (10)
- 弁室の軸方向に弁座を有する本体と、
前記弁室の軸方向に移動でき前記弁座と対向して配置される弁体と、
前記弁体を前記弁座に対して当接、離反させる弁駆動手段と、
前記本体の前記弁室に径方向から接続される第一の配管と、
前記本体の前記弁室に軸方向から取り付けられる第二の配管とを備え、
前記弁体は、少なくとも前記第一の配管に対向する軸部の周りが、網目構造の部材または発泡材料でなる部材で構成され、
前記網目構造の部材または発泡材料でなる部材は、前記弁体の前記軸部の直径よりも大きく、前記弁室の内径よりも小さい円筒形状を有し、前記弁室内に収納されていることを特徴とする膨張弁。 - 前記網目構造の部材または発泡材料でなる部材の軸方向長さは、前記弁体が全開、全閉のいずれの状態にある場合でも、前記第一の配管の断面の投影面に当該網目構造の部材または発泡材料でなる部材の一部が存在する長さに設定されていることを特徴とする請求項1記載の膨張弁。
- 前記弁体の前記軸部の周りの前記部材は、網目構造の部材であり、その格子長さは、可聴域の高い周波数帯域である可聴限界の振動数を有する気泡径よりも小さく設定されていることを特徴とする請求項1又は2記載の膨張弁。
- 第二の配管内の本体側の端部に、第二の網目構造の部材を設けたことを特徴とする請求項1~3のいずれかに記載の膨張弁。
- 第二の網目構造の部材は、円筒状の非網目構造の部材の内部に円錐台状の網目部材を備えたものであり、流体が円錐台状の網目部材を通過できるように、また前記円錐台状の網目部材の縮径された上面が弁座側を向くように構成されていることを特徴とする請求項4記載の膨張弁。
- 第二の網目構造の部材の軸方向長さは、流体の速度が最大の状態で、絞られた冷媒が弁座から第二の配管壁面に衝突するまでの距離に相当する長さに設定されていることを特徴とする請求項4又は5記載の膨張弁。
- 前記円錐台状の網目部材は、その格子長さが、可聴域の高い周波数帯域である可聴限界の振動数を有する気泡径よりも小さく設定されていることを特徴とする請求項5又は6記載の膨張弁。
- 第二の網目構造の部材は、軸方向に間隔を置いて配置された格子長さの異なる複数種の網目部材で構成されていることを特徴とする請求項4記載の膨張弁。
- 前記格子長さの異なる複数種の網目部材は、本体に近づくほど格子長さが短くなるように配置されていることを特徴とする請求項8記載の膨張弁。
- 前記格子長さの異なる複数種の網目部材のうち最小の格子長さを有する網目部材は、その格子長さが、可聴限界の気泡径以下に設定されていることを特徴とする請求項8又は9記載の膨張弁。
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JP2017026101A (ja) * | 2015-07-27 | 2017-02-02 | 日本ドレッサー株式会社 | 弁装置 |
JP2020153479A (ja) * | 2019-03-22 | 2020-09-24 | 株式会社鷺宮製作所 | 温度膨張弁、および、温度膨張弁を用いた冷凍サイクルシステム |
JP7262261B2 (ja) | 2019-03-22 | 2023-04-21 | 株式会社鷺宮製作所 | 温度膨張弁、および、温度膨張弁を用いた冷凍サイクルシステム |
CN112443668A (zh) * | 2019-08-29 | 2021-03-05 | 浙江三花汽车零部件有限公司 | 一种膨胀阀 |
JP7466485B2 (ja) | 2021-03-24 | 2024-04-12 | 株式会社鷺宮製作所 | 電動弁 |
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EP3064868A1 (en) | 2016-09-07 |
EP3064868B1 (en) | 2021-01-20 |
JPWO2015063854A1 (ja) | 2017-03-09 |
EP3064868A4 (en) | 2017-05-31 |
JP6012882B2 (ja) | 2016-10-25 |
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