WO2011121747A1 - エジェクタ及び駆動流体発泡方法及び冷凍サイクル装置 - Google Patents
エジェクタ及び駆動流体発泡方法及び冷凍サイクル装置 Download PDFInfo
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- WO2011121747A1 WO2011121747A1 PCT/JP2010/055804 JP2010055804W WO2011121747A1 WO 2011121747 A1 WO2011121747 A1 WO 2011121747A1 JP 2010055804 W JP2010055804 W JP 2010055804W WO 2011121747 A1 WO2011121747 A1 WO 2011121747A1
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- flow path
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
- F04F5/46—Arrangements of nozzles
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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
- C09K5/02—Materials undergoing a change of physical state when used
- C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
- C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
-
- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
- C09K5/02—Materials undergoing a change of physical state when used
- C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
- C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
- C09K5/042—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising compounds containing carbon and hydrogen only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/14—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
- F04F5/16—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
- F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
- F04F5/54—Installations characterised by use of jet pumps, e.g. combinations of two or more jet pumps of different type
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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
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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
- C09K2205/10—Components
- C09K2205/106—Carbon dioxide
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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
- C09K2205/10—Components
- C09K2205/132—Components containing nitrogen
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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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0012—Ejectors with the cooled primary flow at high pressure
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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
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
Definitions
- This invention relates to an ejector that draws in a surrounding refrigerant by using the velocity energy of a two-phase refrigerant ejected from a nozzle at a high speed to circulate the refrigerant.
- a two-phase ejector may be used for the refrigeration cycle apparatus.
- the nozzle of the two-phase ejector has a tapered section where the cross-sectional area of the flow path decreases from the nozzle inlet along the flow direction, the throat where the cross-sectional area of the flow path is minimized, and the cross-sectional area of the flow path along the flow direction from the throat.
- the refrigerant flowing into the nozzle is depressurized while increasing in speed from the taper taper portion to the throat portion, and expands by foaming when the pressure reaches a pressure below the saturated liquid line. Further, expansion of the refrigerant is promoted at the divergent taper portion to further reduce the pressure, and the refrigerant is ejected from the nozzle as a high-speed gas-liquid two-phase refrigerant expanded under reduced pressure.
- the refrigerant flow rate passing through the nozzle is strongly influenced by the throat diameter.
- the practical throat diameter range is 0.5 to 2.0 mm.
- the angles of the tapered taper portion and the divergent taper portion should be moderate, for example, about 5 ° for the tapered taper portion and 3 ° or less for the divergent taper portion. .
- the taper taper portion is formed in a two-stage taper, and the taper length is shortened to facilitate workability at the time of manufacturing the nozzle (FIG. 5 of Patent Document 1). .
- Patent Document 1 the workability of the length of the divergent taper portion is not improved. There is still a problem that the cutting of the divergent taper portion is difficult because the diverging taper portion is very long with respect to the size of the throat diameter.
- An object of the present invention is to provide an ejector having a nozzle that can be easily cut into a divergent tapered portion.
- the ejector of the present invention is In an ejector provided with a nozzle part in which a flow path for reducing the driving fluid flowing in from the upstream side to flow out to the mixing part on the downstream side is formed,
- the flow path of the nozzle part is A decreasing flow path section in which the flow path cross-sectional area gradually decreases toward the downstream side,
- the same cross-sectional flow path part that continues for a predetermined length in substantially the same cross-sectional shape from the downstream end of the reduced flow path part, and And an enlarged flow path portion that is continuous from the downstream end portion of the same cross-section flow path portion, and that the flow channel cross-sectional area gradually increases toward the downstream side.
- FIG. 1 is a schematic diagram of a refrigeration cycle apparatus 1000 according to Embodiment 1.
- FIG. FIG. 3 is a schematic diagram of an ejector 103 according to Embodiment 1.
- FIG. 2 is a schematic diagram of a nozzle unit 201 of an ejector 103 according to Embodiment 1.
- FIG. 4 is a diagram showing a flow rate characteristic of the ejector 103 according to the first embodiment.
- FIG. 6 is a diagram for explaining a decrease in length of a divergent taper portion 201c of the ejector 103 according to the first embodiment.
- FIG. 3 is a schematic diagram of an ejector 103 with a needle valve in the first embodiment.
- FIG. 3 is a schematic diagram of another refrigeration cycle apparatus in the first embodiment.
- FIG. 1 is a schematic diagram of a refrigeration cycle apparatus 1000 according to the first embodiment.
- a feature of the refrigeration cycle apparatus 1000 is an ejector 103.
- the ejector 103 is characterized in that the nozzle portion 201 includes a cylindrical flow passage portion 201b (sometimes referred to as a cylindrical flow passage) having a cylindrical flow passage.
- the present invention is characterized in that the inner diameter of the cylindrical flow path portion 201b corresponding to the throat portion is enlarged with respect to the conventional ejector.
- the length of the divergent taper portion can be shortened, and in addition to the fact that the inner diameter of the cylindrical flow path portion 201b is enlarged as compared with the conventional case, the workability by cutting can be improved.
- the compressor 101 In the refrigeration cycle apparatus 1000, the compressor 101, the condenser 102 (heat radiator), the ejector 103, and the gas-liquid separator 104 that separates the gas-liquid two-phase refrigerant flowing out from the ejector 103 into liquid refrigerant and gas refrigerant are refrigerant pipes. Connected sequentially. Further, in the refrigeration cycle apparatus 1000, the evaporator 105 is connected to the ejector 103 and the gas-liquid separator 104 by piping.
- the driving fluid inlet (103-1) is connected to the refrigerant outlet (102-1) of the condenser 102, and the suction fluid inlet (103-2) is connected to the refrigerant outlet (102-2) of the evaporator 105.
- 105-1) and an outflow port (103-3) through which the mixed fluid of the driving fluid and the suction fluid flows out is connected to the gas-liquid separator 104.
- a circuit including the compressor 101, the condenser 102, the ejector 103, and the gas-liquid separator 104 forms a first refrigerant circulation loop circuit, and a circuit including the gas-liquid separator 104, the evaporator 105, and the ejector 103 is the second circuit.
- a refrigerant circulation loop circuit is formed.
- the condenser 102 and the evaporator 105 are provided with fans 102-2 and 105-2, respectively.
- FIG. 2 shows a schematic diagram of the ejector 103.
- the ejector 103 includes a nozzle unit 201, a mixing unit 202, and a diffuser unit 203.
- the nozzle part 201 is formed with a flow path 20 that depressurizes the driving fluid flowing in from the upstream side and flows out to the mixing part 202 on the downstream side.
- the flow path 20 of the nozzle part 201 includes a tapered taper part 201a (reducing flow path part), a cylindrical flow path part 201b (same cross-sectional flow path part), and a divergent taper part 201c (enlarged flow path part).
- the cylindrical flow path part 201b corresponds to the throat part having the smallest cross-sectional area among the flow paths through which the coolant as the driving fluid passes.
- the nozzle unit 201 decompresses and expands the high-pressure refrigerant flowing out of the condenser 102, and ejects a high-speed two-phase fluid of a liquid refrigerant and a gas refrigerant.
- the refrigerant is sucked from the evaporator 105 by using the velocity energy of the high-speed two-phase fluid ejected from the nozzle unit 201 from the suction fluid inlet (103-2).
- the mixing unit 202 the pressure rises while mixing the refrigerant ejected from the nozzle unit 201 and the refrigerant sucked from the inflow port (103-2).
- the diffuser unit 203 the dynamic pressure of the mixed refrigerant is converted into a static pressure.
- FIG. 3 shows the nozzle part 201 of the first embodiment.
- the cylindrical flow path 201b has a cylindrical flow path shape having a diameter D2 and a length L2 (hereinafter sometimes referred to as a cylindrical flow path length L2).
- An arrow 11 indicates the direction in which the refrigerant flows. Therefore, the direction of the arrow is the downstream side.
- the taper taper part 201a the flow path cross-sectional area gradually decreases from the diameter D1 to the diameter D2.
- the taper angle is ⁇ 1.
- the length of the tapered portion 201a is “L1”.
- the cylindrical channel portion 201b has a cylindrical channel shape with a diameter D2 and a cylindrical channel length L2.
- the flow path sectional area of the divergent taper portion 201c gradually increases from the diameter D2 to the diameter D3.
- the taper angle is ⁇ 2.
- the length of the divergent taper portion 201c is “L3”.
- the angle ⁇ 1 of the taper taper portion 201a and the angle ⁇ 3 of the divergent taper portion are designed so that ⁇ 1 is around 5 ° and ⁇ 3 is 1.5 ° or less in order to reduce eddy loss due to sudden reduction or expansion. The Therefore, the taper taper portion length “L1” and the divergent taper portion 201c length “L3” are determined from the diameter D1 of the nozzle inlet, the diameter D2 of the cylindrical flow passage 201b that is the throat, and the diameter D3 of the nozzle outlet.
- the cylindrical flow path length L2 is very short compared to the total length of the nozzle.
- stainless steel metal, copper and copper alloy, aluminum or the like can be used as the material of the nozzle portion 201 in the ejector 103.
- FIG. 4 shows a Mollier diagram in the refrigeration cycle apparatus 1000 shown in FIG.
- the operation of the refrigeration cycle apparatus 1000 will be described with reference to FIGS.
- the high-temperature and high-pressure gas refrigerant (state A) delivered from the compressor 101 dissipates heat in the condenser 102 and is liquefied (state B) and flows into the ejector 103 (drive fluid).
- the driving fluid flows in from the inflow port (103-1)
- the driving fluid expands while being reduced in pressure at the nozzle unit 201, and becomes an ultra-high-speed gas-liquid two-phase refrigerant and flows out of the nozzle unit 201 (state C).
- the refrigerant is drawn from the suction fluid inlet (103-2) based on the kinetic energy of the driving flow flowing out from the nozzle unit 201 (suction fluid), and the mixed fluid of the driving fluid and the suction fluid flows into the mixing unit 202 ( State D).
- the mixing unit 202 the driving fluid and the suction fluid are mixed while exchanging their mutual momentum, whereby the pressure is recovered.
- the pressure is recovered by converting the dynamic pressure into the static pressure due to the enlargement of the cross-sectional area of the flow path (state E).
- the gas-liquid two-phase refrigerant that has flowed out of the ejector 103 is separated into a gas refrigerant and a liquid refrigerant by the gas-liquid separator 104.
- the gas refrigerant flows into the compressor 101 (state F), and the liquid refrigerant flows into the evaporator 105 (state G).
- the liquid refrigerant absorbs heat from the surroundings in the evaporator 105 and evaporates (state H), and is sucked from the suction fluid inlet (103-2) of the ejector 103 by the drawing action of the driving fluid.
- a refrigerant circulation loop to the evaporator 105 (a refrigerant circulation circuit of the evaporator 105, the ejector 103, and the gas-liquid separator 104) is formed.
- the refrigeration cycle apparatus using the ejector can increase the suction pressure of the compressor as compared with the conventional refrigeration cycle apparatus, so that the operation efficiency can be improved.
- FIG. 5 shows the pressure inside the nozzle, the average speed of the refrigerant, and the void ratio when the nozzle part 201 does not have the cylindrical flow path part 201b.
- the memory on the vertical axis is the void ratio.
- the horizontal axis in FIG. 5 indicates the distance from the nozzle inlet (driving fluid inlet (103-1)).
- a vertical broken line represents the position of the throat.
- the “void ratio” is an area ratio occupied by the gas refrigerant when the cross-sectional area of the flow path is 1.
- a void ratio of 0 is a state in which no gas refrigerant exists
- a void ratio of 1 is a state in which the flow path is covered with the gas refrigerant.
- the refrigerant flowing into the nozzle 201 is depressurized by the tapered taper portion 201a and the divergent taper portion 201c, and the refrigerant starts to foam below the saturation pressure.
- the gas ratio (void ratio) in the flow path increases due to foaming, the refrigerant speed increases rapidly. Foaming continues toward the downstream of the divergent taper portion 201c, the pressure decreases, and the speed increases. Thereby, a high-speed two-phase refrigerant is ejected from the nozzle.
- FIG. 6 shows the flow rate characteristics of the nozzle when the throat portion is formed as the cylindrical flow path portion 201b.
- the horizontal axis represents the ratio between the cylindrical channel length L2 of the cylindrical channel 201b and the diameter D2 of the cylindrical channel 201b.
- the diameter D2 of the cylindrical flow path 201b is assumed to be 2 mm or less.
- a solid line indicates the nozzle portion 201 having the cylindrical flow path 201b, and a broken line indicates a nozzle without the cylindrical flow path 201b.
- the pressure in the cylindrical flow path 201b decreases along the flow direction due to friction loss.
- the pressure reaches the foaming start pressure in the cylindrical flow path 201b (position L2 ′)
- the liquid refrigerant foams the speed rapidly increases due to expansion, and the pressure rapidly decreases.
- the pressure at the inlet of the divergent taper portion 201c is lower than that of the nozzle without the cylindrical channel 201b due to friction loss of the cylindrical channel 201b.
- the pressure drop in the divergent taper portion 201c in the presence of the cylindrical channel 201b is reduced, and as a result, the length L3 of the divergent taper portion 201c is shorter than that of the nozzle without the cylindrical channel 201b.
- the friction loss ⁇ P in the cylindrical channel 201b can be predicted by the following equation (1). From this, ⁇ P is calculated using L2 ′ as a parameter. That is, the foaming start position L2 ′ can be predicted from the equation (1) with respect to the difference ⁇ P between the inlet pressure PIN of the cylindrical flow path portion 201b and the foaming start pressure PST .
- the foaming start pressure may be a pressure at which the refrigerant superheat degree (refrigerant temperature and saturation: temperature difference) is 5K.
- the cylindrical flow path length L2 may be determined based on the foaming start position L2 ′.
- the flow rate of the refrigerant passing through the nozzle unit 201 can be controlled by adjusting the position where the refrigerant starts to be foamed by the length of the cylindrical flow path length L2.
- FIG. 8 is a view showing a case where the nozzle unit 201 is used in the ejector 103 having the movable needle valve 205.
- the ejector 103 may be realized as an ejector in which a movable needle valve 25 for controlling the flow rate of the refrigerant is inserted.
- FIG. 9 is a diagram showing a configuration of another refrigeration cycle apparatus in the first embodiment. Even if the ejector 103 is mounted on a refrigerant circuit (refrigeration cycle apparatus) as shown in FIG. 9, the same effect as in FIG. 1 can be obtained.
- the compressor 101, the condenser 102 (heat radiator), the expansion mechanism 106, the first evaporator 105a, the ejector 103, and the second evaporator 105b are sequentially connected by refrigerant piping.
- the ejector 103 has a driving fluid inlet (103-1) connected to the branch pipe 21 branched from the middle of the pipe connecting the condenser 102 and the expansion mechanism 106, and a suction fluid inlet (103-2).
- the refrigerant outlet (105b-2) of the second evaporator 105b is connected to the refrigerant outlet (105a-2) of the first evaporator 105a, and the outlet (103-3) through which the mixed fluid of the driving fluid and the suction fluid flows out. 1) is connected.
- the expansion mechanism 106 and the refrigerant inlet (105a-1) of the first evaporator 105a are connected, and the refrigerant outlet (105b-2) of the second evaporator 105b and the inlet of the compressor 101 are connected. And are connected.
- the refrigerant flowing out of the condenser 102 is divided into the first evaporator 105a and the ejector 103.
- the refrigerant that has flowed out of the first evaporator 105 a is sucked and pressurized by the ejector 103.
- the refrigerant that has flowed out of the ejector 103 flows to the second evaporator 105 b and the suction port of the compressor 101.
- the cross-sectional shape is a circle. It is not limited to an ellipse or other shapes. It is sufficient that the cross-sectional shape does not change along the flow path direction.
- FIG. 3 only the tapered taper portion exists on the upstream side of the cylindrical flow channel 201b, but it may be a two-step tapered portion, or “another cylindrical flow channel + taper taper portion” as shown in FIG. But you can. That is, the flow path immediately before the cylindrical flow path 201b may be a tapered tapered portion.
- the ejector 103 according to Embodiment 1 starts foaming in the cylindrical channel by providing a cylindrical channel in the throat of the nozzle.
- the length L3 of the divergent taper portion can be shortened as compared with a nozzle without a cylindrical flow path. Therefore, when manufacturing by cutting, the divergent taper portion 201c is easily processed.
- the ejector 103 according to Embodiment 1 has a cylindrical flow path in the throat portion of the nozzle, and the diameter D2 of the throat portion is enlarged. Therefore, the ejector 103 can flow the same flow rate of refrigerant as a nozzle without a cylindrical flow path, and when manufactured by cutting, the workability with a cutting tool is improved by increasing the diameter D2, and the manufacturing time is increased. Can be reduced.
- Ejector 103 of Embodiment 1 has improved machinability by expanding the throat diameter D2 and adding a cylindrical flow path. Therefore, dimensional accuracy can be improved by finishing the cylindrical flow path part 201b and the divergent taper part 201c with a reamer, for example.
- the ejector 103 of the first embodiment has a cylindrical flow path length L2 that is very short compared to the total length of the nozzle. For this reason, the friction loss in the cylindrical flow path is very small compared to the pressure drop due to expansion, so that power conversion efficiency equivalent to that of a nozzle without the cylindrical flow path can be obtained.
- the total length of the nozzle is increased and the material cost is increased.
- the cylindrical flow path length L2 is short as described above, the increase in material cost is slight. Since the machinability is improved by expanding the throat diameter and shortening the divergent taper length, the cost reduction effect by improving the machinability is far greater than the increase in material cost.
- the refrigerant to be used may be a chlorofluorocarbon refrigerant or other refrigerant.
- the refrigerant to be used may be a natural refrigerant such as ammonia, carbon dioxide, hydrocarbon (eg, propane, isobutane), a low GWP refrigerant such as HFO1234yf, and a mixed refrigerant thereof.
- the refrigeration cycle apparatus of Embodiment 1 is not limited to an air conditioner, and may be realized as a refrigerator, chiller, or water heater.
- the diameter of the throat portion of the nozzle portion of the ejector is 0.5 to 2 mm, and the length of the divergent taper portion that expands the refrigerant is 20 mm or more, so that a narrow hole is deeply inserted.
- foaming is promoted by utilizing a pressure drop of the refrigerant due to friction of the cylindrical channel.
- the diameter of the cylindrical flow path is increased from the conventional throat diameter.
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Abstract
Description
(2)また、放電加工による製造ではコスト高となる。
(3)また、鋳造ではノズル内面の仕上げ精度が悪化するため、鋳造はノズルの量産製造には不向きである。
上流側から流入した駆動流体を減圧させて下流側の混合部に流出する流路が形成されたノズル部を備えたエジェクタにおいて、
前記ノズル部の前記流路は、
前記下流側に向かうに従って流路断面積が次第に減少する減少流路部と、
前記減少流路部の前記下流側の端部から略同一の断面形状で所定の長さ連続する同一断面流路部と、
前記同一断面流路部の前記下流側の端部から連続する共に、前記下流側に向かうに従って流路断面積が次第に拡大する拡大流路部と
を備えたことを特徴とする。
以下図1~図9を参照して実施の形態1の冷凍サイクル装置を説明する。
図1は、実施形態1の冷凍サイクル装置1000の模式図である。冷凍サイクル装置1000の特徴は、エジェクタ103である。後述する図3に示すように、エジェクタ103が、ノズル部201に流路が円筒形状の円筒流路部201b(円筒状流路という場合もある)を備えた点が特徴である。また、従来のエジェクタに対して、喉部に相当する円筒流路部201bの内径を拡大した点が特徴である。円筒流路部201bを備えることで末広テーパー部長さを短縮できるので、円筒流路部201bの内径を従来に比べて拡大したことと併せて、切削加工による加工性を向上できる。
冷凍サイクル装置1000では、圧縮機101、凝縮器102(放熱器)、エジェクタ103及びエジェクタ103から流出した気液二相の冷媒を液冷媒とガス冷媒に分離する気液分離器104が冷媒配管で順次接続されている。さらに、冷凍サイクル装置1000では、蒸発器105がエジェクタ103と気液分離器104とに配管で接続されている。エジェクタ103は、駆動流体の流入口(103-1)が凝縮器102の冷媒流出口(102-1)と接続し、吸引流体の流入口(103-2)が蒸発器105の冷媒流出口(105-1)と接続し、駆動流体と吸引流体との混合流体を流出する流出口(103-3)が気液分離器104と接続されている。圧縮機101、凝縮器102、エジェクタ103及び気液分離器104からなる回路が第一の冷媒循環ループ回路を形成し、気液分離器104、蒸発器105、エジェクタ103からなる回路が第二の冷媒循環ループ回路を形成している。なお凝縮器102、蒸発器105はそれぞれファン102-2、105-2を備えている、
図2は、エジェクタ103の概略図を示す。エジェクタ103は、ノズル部201、混合部202、ディフューザー部203で構成される。ノズル部201は、上流側から流入した駆動流体を減圧させて下流側の混合部202に流出する流路20が形成されている。ノズル部201の流路20は、先細テーパー部201a(減少流路部)、円筒流路部201b(同一断面流路部)、末広テーパー部201c(拡大流路部)を備える。円筒流路部201bは駆動流体である冷媒が通過する流路のうちで最も断面積が小さい喉部に相当する。
図3は、実施の形態1のノズル部201を示す。円筒流路201bは、直径D2、長さL2(以下、円筒状流路長L2という場合がある)の円筒状の流路形状である。矢印11は冷媒の流れる方向を示している。従って矢印の方向が下流側である。
(1)先細テーパー部201aは、流路断面積が直径D1から直径D2に次第に減少する。テーパー角度はθ1である。先細テーパー部201aの長さは「L1」である。
(2)円筒流路部201bは、直径D2、円筒状流路長L2の円筒状の流路形状である。
(3)末広テーパー部201cは、流路断面積が直径D2から直径D3に次第に増加する。テーパー角度はθ2である。末広テーパー部201cの長さは「L3」である。
(4)先細テーパー部201aの角度θ1と末広テーパー部の角度θ3とは、急縮小、急拡大による渦損失を低減するために、θ1は5°前後、θ3は1.5°以下で設計される。よって、先細テーパー部長さ「L1」と末広テーパー部201cの長さ「L3」とは、ノズル流入口の径D1、喉部である円筒流路部201bの径D2及びノズル流出口の径D3から幾何学的に決まる。なお円筒状流路長L2はノズル全長と比べて非常に短い。
(5)なおエジェクタ103におけるノズル部201の材質は、ステンレス系金属、銅および銅合金、アルミなどを採用することができる。
次に冷凍サイクル装置1000の動作について説明する。
図4は、図1に示した冷凍サイクル装置1000におけるモリエル線図を示す。
図2、図4を参照して冷凍サイクル装置1000の動作を説明する。圧縮機101から送出された高温高圧のガス冷媒(状態A)は、凝縮器102で放熱して液化(状態B)し、エジェクタ103へ流入する(駆動流体)。駆動流体は、流入口(103-1)から流入するとノズル部201で減圧しながら膨張し、超高速の気液二相冷媒になってノズル部201から流出する(状態C)。ノズル部201から流出する駆動流の運動エネルギーに基づき吸引流体の流入口(103-2)から冷媒が引き込まれ(吸引流体)、駆動流体と吸引流体との混合流体が混合部202へ流入する(状態D)。混合部202では、駆動流体と吸引流体とが互いの運動量を交換し合いながら混じり合うことで、圧力が回復する。更に、ディフューザー部203においても流路断面積の拡大により、動圧が静圧に変換することで圧力が回復する(状態E)。エジェクタ103を流出した気液二相冷媒は、気液分離器104にてガス冷媒と液冷媒とに分離される。気液分離器104では、ガス冷媒は圧縮機101へ流入し(状態F)、液冷媒は蒸発器105へ(状態G)流入する。液冷媒は蒸発器105にて周囲から吸熱して蒸発し(状態H)、エジェクタ103の吸引流体の流入口(103-2)から駆動流体の引き込み作用により吸引される。この一連の動作により、蒸発器105への冷媒循環ループ(蒸発器105、エジェクタ103、気液分離器104の冷媒の循環回路)が形成される。
次にエジェクタ103のノズル部201の動作について説明する。
図5は、ノズル部201に円筒流路部201bがない場合の、ノズル内部の圧力、冷媒の平均速度、ボイド率を示す。縦軸のメモリはボイド率である。円筒流路部201bがない場合とは、図7の最下部に示すような、先細テーパー部201aからすぐに末広テーパー部201cに移行する形状の場合(L2=0)である。図5の横軸は、ノズル入口(駆動流体の流入口(103-1))からの距離を示している。また、縦の破線は、喉部の位置を表している。ここで「ボイド率」とは、流路断面積を1としたときのガス冷媒の占める面積比である。ボイド率0はガス冷媒が存在しない状態であり、ボイド率1は流路がガス冷媒で覆われている状態である。図5に示すように、ノズル201へ流入した冷媒は、先細テーパー部201a、末広テーパー部201cで減圧し、冷媒は、飽和圧力以下となって発泡し始める。発泡により流路内のガス比率(ボイド率)が増すことで冷媒速度が急上昇する。末広テーパー部201cの下流に向かって発泡は継続し、圧力が低下し、速度は上昇する。これにより、高速の二相冷媒がノズルから噴出する。
図6は喉部が円筒流路部201bとして形成された場合のノズルの流量特性である。横軸は、円筒流路部201bの円筒状流路長L2と円筒流路部201bの直径D2との比を表す。縦軸は、喉部直径がD2、かつ、円筒流路部が無い場合(L2=0)における流量を1とした場合の流量比を示す。円筒流路部201bの円筒状流路長L2を長くすると流量は低下する。これは、円筒状流路201bでの摩擦損失により圧力が低下することで冷媒の飽和温度が下がり、円筒状流路201b内で冷媒が発泡開始するためである。ガス冷媒の比体積は液冷媒の比体積に比べて非常に大きいため、気液二相流体のように液体中にガスを含むような流体は流れにくい。図6に示すように、喉部径D2を1.1倍、1.2倍とした場合もL2/D2に対する流量特性は同じ傾向を示す。また、喉部径D2を拡大した場合、流量は増大する。この特性より、円筒状流路201bを設け、かつ喉部径D2を拡大すると、円筒流路が無い(L2=0)のノズルと同一流量を流すことができる。図6に示す例では、喉部径D2が1.1倍の場合には「L2/D2」が1程度となる円筒状流路長L2を選び、喉部径D2が1.2倍の場合には「L2/D2」が5程度となる円筒状流路長L2を選ぶことで、円筒流路部201bの無い場合(L=0)と同一流量の冷媒を流すことができる。
なお、本実施の形態1のエジェクタ103は、円筒状流路201bの直径D2を2mm以下と想定している。
図7は、円筒状流路201bを有するノズル部201と、円筒状流路201bの無いノズル(L2=0)との、冷媒の圧力分布と速度分布との概略図である。実線が円筒状流路201bを有するノズル部201を示し、破線が円筒状流路201bの無いノズルを示す。円筒流路部201b内の圧力は、摩擦損失により流れ方向に沿って低下する。円筒流路部201b内で圧力が発泡開始圧に達すると(L2’の位置)、液体状態の冷媒は発泡し、膨張により速度が急上昇、圧力が急低化する。末広テーパー部201cの流入口における圧力は、円筒状流路201bの摩擦損失により、円筒状流路201bの無いノズルと比べて低くなる。これにより、円筒状流路201bのある場合の末広テーパー部201cにおける圧力降下は小さくなり、結果として、末広テーパー部201cの長さL3は、円筒状流路201bの無いノズルと比べて短くなる。
ρ:密度、
u:速度
である。
発泡開始圧は、文献によると、冷媒過熱度(冷媒温度と飽和:温度の差)が5Kとなる圧力を用いればよい。円筒状流路長L2は、この発泡開始位置L2’に基づいて決定するとよい。
Claims (8)
- 上流側から流入した駆動流体を減圧させて下流側の混合部に流出する流路が形成されたノズル部を備えたエジェクタにおいて、
前記ノズル部の前記流路は、
前記下流側に向かうに従って流路断面積が次第に減少する減少流路部と、
前記減少流路部の前記下流側の端部から略同一の断面形状で所定の長さ連続する同一断面流路部と、
前記同一断面流路部の前記下流側の端部から連続する共に、前記下流側に向かうに従って流路断面積が次第に拡大する拡大流路部と
を備えたことを特徴とするエジェクタ。 - 前記減少流路部は、
液体状態の前記駆動流体を流入し、前記駆動流体を液体状態で減圧させながら液体状態で前記同一断面流路部に流出し、
前記同一断面流路部は、
前記所定の長さの途中で、液体状態の前記駆動流体に発泡を開始させることを特徴とする請求項1記載のエジェクタ。 - 前記減少流路部と、前記同一断面流路部と、前記拡大流路部とは、
いずれも、前記流路の断面形状が略円形状であることを特徴とする請求項1または2のいずれかに記載のエジェクタ。 - 前記同一断面流路部は、
前記略同一の断面形状が円であると共に、前記円の直径が2mm以下であることを特徴とする請求項1~3のいずれかに記載のエジェクタ。 - 前記エジェクタは、
前記流路に配置されることにより、前記駆動流体の流量を調節するニードル弁を備えたことを特徴とする請求項1~4のいずれかに記載のエジェクタ。 - 上流側から流入した液体状態の駆動流体を下流側の混合部に流出する流路が形成されたノズル部を備えたエジェクタに使用される方法であって、前記混合部に流出する前記駆動流体を発泡させる発泡方法において、
前記ノズル部の前記流路は、
前記下流側に向かうに従って流路断面積が次第に減少する減少流路部と、
前記減少流路部の前記下流側の端部から略同一の断面形状で所定の長さ連続する同一断面流路部と、
前記同一断面流路部の前記下流側の端部から連続する共に、前記下流側に向かうに従って流路断面積が次第に拡大する拡大流路部と
を備え、
前記液体状態の駆動流体を、前記同一断面流路部の前記所定の長さの途中で発泡させることを特徴とする駆動流体発泡方法。 - 圧縮機、放熱器、エジェクタ、気液分離器が冷媒配管で順次接続され、さらに、蒸発器がエジェクタと気液分離器とに接続され、
前記エジェクタは、
駆動流体の流入口が前記放熱器の冷媒流出口と接続し、
吸引流体の流入口が前記蒸発器の冷媒流出口と接続し、
駆動流体と吸引流体との混合流体を流出する流出口が前記気液分離器と接続した冷凍サイクル装置において、
前記エジェクタは、
上流側である前記駆動流体の流入口から流入した駆動流体を減圧させて下流側の混合部に流出する流路が形成されたノズル部を備え、
前記ノズル部の前記流路は、
前記下流側に向かうに従って流路断面積が次第に減少する減少流路部と、
前記減少流路部の前記下流側の端部から略同一の断面形状で所定の長さ連続する同一断面流路部と、
前記同一断面流路部の前記下流側の端部から連続する共に、前記下流側に向かうに従って流路断面積が次第に拡大する拡大流路部と
を備えたことを特徴とする冷凍サイクル装置。 - 圧縮機、放熱器、膨張機構、第1蒸発器、エジェクタ、第2蒸発器が冷媒配管で順次接続され、
前記エジェクタは、
駆動流体の流入口が前記放熱器と前記膨張機構とを接続する配管の途中から分岐した分岐配管と接続し、
吸引流体の流入口が前記第1蒸発器の冷媒流出口と接続し、
駆動流体と吸引流体との混合流体を流出する流出口が前記第2蒸発器の冷媒流入口と接続し、
前記エジェクタは、
上流側である前記駆動流体の流入口から流入した駆動流体を減圧させて下流側の混合部に流出する流路が形成されたノズル部を備え、
前記ノズル部の前記流路は、
前記下流側に向かうに従って流路断面積が次第に減少する減少流路部と、
前記減少流路部の前記下流側の端部から略同一の断面形状で所定の長さ連続する同一断面流路部と、
前記同一断面流路部の前記下流側の端部から連続する共に、前記下流側に向かうに従って流路断面積が次第に拡大する拡大流路部と
を備えたことを特徴とする冷凍サイクル装置。
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2010
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- 2010-03-31 US US13/583,937 patent/US20130000348A1/en not_active Abandoned
- 2010-03-31 CN CN201080065781.2A patent/CN102822535B/zh active Active
- 2010-03-31 EP EP10848925.3A patent/EP2554852B1/en active Active
- 2010-03-31 JP JP2012507971A patent/JP5575225B2/ja not_active Expired - Fee Related
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JP2003139098A (ja) | 2001-10-30 | 2003-05-14 | Nippon Soken Inc | エジェクタ |
JP2003185275A (ja) * | 2001-12-19 | 2003-07-03 | Denso Corp | エジェクタ方式の減圧装置 |
JP2004239145A (ja) * | 2003-02-05 | 2004-08-26 | Denso Corp | エジェクタ |
JP2006017444A (ja) * | 2004-06-01 | 2006-01-19 | Denso Corp | エジェクタサイクルおよびその制御方法 |
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CN104160159A (zh) * | 2012-03-07 | 2014-11-19 | 株式会社电装 | 喷射器 |
WO2014162688A1 (ja) * | 2013-04-03 | 2014-10-09 | 株式会社デンソー | エジェクタ |
JP2014202391A (ja) * | 2013-04-03 | 2014-10-27 | 株式会社デンソー | エジェクタ |
Also Published As
Publication number | Publication date |
---|---|
EP2554852A1 (en) | 2013-02-06 |
CN102822535B (zh) | 2015-10-21 |
EP2554852B1 (en) | 2018-05-16 |
CN102822535A (zh) | 2012-12-12 |
JP5575225B2 (ja) | 2014-08-20 |
EP2554852A4 (en) | 2016-11-16 |
US20130000348A1 (en) | 2013-01-03 |
JPWO2011121747A1 (ja) | 2013-07-04 |
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