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WO2011064813A1 - Accumulateur et dispositif de cycle de réfrigération - Google Patents

Accumulateur et dispositif de cycle de réfrigération Download PDF

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Publication number
WO2011064813A1
WO2011064813A1 PCT/JP2009/006331 JP2009006331W WO2011064813A1 WO 2011064813 A1 WO2011064813 A1 WO 2011064813A1 JP 2009006331 W JP2009006331 W JP 2009006331W WO 2011064813 A1 WO2011064813 A1 WO 2011064813A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
container
pipe
liquid
accumulator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2009/006331
Other languages
English (en)
Japanese (ja)
Inventor
鳩村傑
山下浩司
森本裕之
若本慎一
下地美保子
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2011542984A priority Critical patent/JP5425221B2/ja
Priority to PCT/JP2009/006331 priority patent/WO2011064813A1/fr
Publication of WO2011064813A1 publication Critical patent/WO2011064813A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2113—Temperatures of a suction accumulator

Definitions

  • the present invention relates to an accumulator used in a refrigeration cycle apparatus.
  • the present invention relates to an accumulator capable of returning oil even when a refrigerating machine oil incompatible with a refrigerant is used.
  • CO refrigerating machine oil used in the refrigeration cycle apparatus using two refrigerant the CO 2 refrigerant is a refrigerating machine oil incompatible.
  • refrigeration oil that is compatible with the CO 2 refrigerant in the entire operating temperature range used in the refrigeration cycle apparatus, such as chlorofluorocarbon refrigerant.
  • incompatible means that the refrigerant and the refrigerating machine oil do not completely dissolve, and that the incompatible is completely incompatible, and the amount that is slightly soluble but the amount that is soluble is difficult. Contains both soluble ones.
  • the hot gas is bypassed from the compressor discharge side, the hot gas is allowed to flow into the lower part of the accumulator, and the refrigerant and refrigeration oil staying in a separated state in the lower part of the accumulator are agitated and mixed to return oil from the accumulator.
  • Patent Document 1 proposes a method that enables this.
  • An accumulator performs gas-liquid separation in order to supply a gas-phase refrigerant to a compressor of a refrigeration cycle apparatus, and stores a liquid in the accumulator, and a refrigerator oil that circulates in a refrigerant circuit and a refrigerant circuit
  • a branch pipe for stirring the liquid and an outflow pipe having an oil return hole for allowing the refrigeration oil in the liquid staying in the container to flow out together with the refrigerant are provided.
  • the distribution joint and the branch pipe are connected to the inflow pipe, and the refrigerant is guided to the lower part of the container so as to stir the staying liquid.
  • the refrigeration oil can be conveyed to the compressor along with the refrigerant from the outflow pipe.
  • FIG. 2 is a diagram illustrating a configuration of an accumulator 6 according to Embodiment 1.
  • FIG. It is a figure showing the structure of the accumulator 6 which concerns on Embodiment 2.
  • FIG. It is a figure showing the structure of the accumulator 6 which concerns on Embodiment 3.
  • FIG. It is a figure showing the structure of the accumulator 6 which concerns on Embodiment 4.
  • FIG. 1 is a diagram illustrating a configuration of an air-conditioning apparatus serving as a refrigeration cycle apparatus according to Embodiment 1.
  • an air conditioner will be described as a representative refrigeration cycle apparatus.
  • the air conditioner according to the present embodiment connects an outdoor unit 100 and indoor units 200a and 200b with a gas pipe 51 and a liquid pipe 52, and constitutes a refrigerant circuit in which refrigerant circulates. Then, inside this refrigerant circuit, for example, carbon dioxide that becomes a supercritical state at a critical temperature (about 31 ° C.) or higher as refrigerant and PAG (polyalkylene glycol) oil that is incompatible with carbon dioxide as refrigerating machine oil are enclosed. is doing.
  • a critical temperature about 31 ° C.
  • PAG polyalkylene glycol
  • the outdoor unit 100 is basically installed outdoors and houses the compressor 1, the flow path switching valve 2, the heat source side heat exchanger 3, the accumulator 6, the blower 7, and the control device 8.
  • the compressor 1 compresses the gas refrigerant.
  • the flow path switching valve 2 such as a four-way valve is a refrigerant flow path switching unit that switches the direction in which the refrigerant flows in accordance with the operation mode of the indoor units 200a and 200b.
  • the heat source side heat exchanger 3 functions as a radiator or an evaporator depending on the operation mode, and performs heat exchange between outdoor air (hereinafter referred to as outside air) and the refrigerant.
  • the accumulator 6 can store surplus refrigerant or the like to adjust the amount of refrigerant circulating in the refrigerant circuit according to the operation mode.
  • the blower 7 forcibly sends outside air to the outer surface of the heat source side heat exchanger 3 to promote heat exchange between the outside air and the refrigerant.
  • the control device 8 controls the refrigerant circuit in cooperation with a control device (not shown) that controls the operation of the indoor units 200a and 200b, such as driving the compressor 1 and the blower 7, switching the flow path switching valve 2, and the like. I do. Although it is housed in the outdoor unit 100 here, it may be provided outside.
  • the indoor units 200a and 200b accommodate electronic expansion valves 4a and 4b, load-side heat exchangers 5a and 5b, and blowers 9a and 9b, respectively.
  • the electronic expansion valves 4a and 4b serve as decompression means, and adjust the amount of refrigerant flowing through the load-side heat exchangers 5a and 5b by changing the opening, respectively, and adjust the refrigerant pressure and temperature in the load-side heat exchangers 5a and 5b.
  • the load side heat exchangers 5a and 5b have one end connected to the gas pipe 51 and the other end connected to the liquid pipe 52 via the electronic expansion valves 4a and 4b.
  • the load-side heat exchangers 5a and 5b also function as radiators or evaporators depending on the operation mode, and exchange heat between the air in the air-conditioning target space and the refrigerant. If the heat source side heat exchanger 3 functions as a radiator, the load side heat exchangers 5a, 5b function as an evaporator, and if the heat source side heat exchanger 3 functions as an evaporator, the load side heat exchanger 5a, 5b functions as a radiator.
  • the blowers 9a and 9b promote heat exchange between the air in the air-conditioning target space and the refrigerant in the load-side heat exchangers 5a and 5b, and send air related to heat exchange with the refrigerant into the air-conditioning target space.
  • two indoor units 200a and 200b are provided, but one or three or more indoor units 200 may be connected by piping.
  • FIG. 2 is a diagram showing a two-layer separation curve of carbon dioxide and PAG oil. From FIG. 2, it can be seen that when the oil content is about 40% or less, carbon dioxide and PAG oil are separated into two layers in all temperature ranges. Since the oil content in the refrigerant circuit as in the present embodiment is about 10% to 20%, the carbon dioxide and the PAG oil are separated into two layers in the entire temperature region where the temperature of the refrigerant in the refrigerant circuit is reached.
  • FIG. 3 is a graph showing the relationship between the temperature, the density of the carbon dioxide liquid, and the density of the PAG oil. From FIG. 3, when the temperature of the liquid carbon dioxide (hereinafter referred to as carbon dioxide liquid) and the PAG oil is about ⁇ 15 ° C. or less, the density of the carbon dioxide liquid becomes higher than the density of the PAG oil. For this reason, the carbon dioxide liquid becomes heavier than the PAG oil, and the PAG oil stays on top of the carbon dioxide liquid. Conversely, at a temperature higher than about ⁇ 15 ° C., the PAG oil stays below the carbon dioxide solution.
  • FIG. 4 is a diagram for illustrating the structure of a normal accumulator 60.
  • a normal accumulator 60 will be described for comparison with the accumulator 6 of the present embodiment.
  • the arrows represent the flow of refrigerant and refrigerating machine oil (hereinafter the same).
  • the accumulator 60 the container A to be sealed, an inflow pipe B for allowing a mixture of refrigerant (liquid refrigerant and gas refrigerant) and refrigerating machine oil to flow into the container A, and a mixture of refrigerant and refrigerating machine oil to flow out of the container A. It is composed of a U-shaped outflow pipe C.
  • the outflow pipe C has an oil return hole (oil return hole) D for returning the refrigeration oil at the lower part.
  • the discharge port E is an opening portion of a pipe for discharging the inflowing refrigerant, and is here an opening portion of one end of the inflow tube B.
  • the intake port F is an opening part of the one end of the outflow pipe C for taking in the refrigerant to flow out.
  • the vertical relationship of the positions is defined as, for example, an upper side and a lower side with respect to the vertical direction.
  • the discharge port E opened at one end of the inflow pipe B is more than the intake port F opened at one end of the outflow pipe C. Is also located on the lower side. Further, in order to carry the liquid refrigerant and the refrigerating machine oil while swirling to the lower part of the container A, the discharge port E in the inflow pipe B faces the inner wall of the container A in the vertical direction or faces downward. ing.
  • the gap between the outlet E in the inlet pipe B and the inner wall of the container A is equal to or larger than a certain value (for example, 2 of the inner diameter of the inlet pipe B). (Distance more than double).
  • the distance between the oil return hole D and the bottom of the container A is made as short as possible in order to reduce the amount of refrigerating machine oil staying at the bottom of the container A (for example, a distance that can be managed in production).
  • the gas refrigerant staying in the upper part of the container A flows out of the container A from the outflow pipe C.
  • the liquid refrigerant and the refrigerating machine oil staying in the lower part of the container A are generated by the dynamic pressure of the gas refrigerant generated between the intake port F of the outflow pipe C and the oil return hole D and the height of the liquid level in the container A. Due to the difference, the oil is sucked from the oil return hole D and flows out of the container A together with the gas refrigerant.
  • the amount of liquid in the accumulator 60 will be described.
  • the refrigerant whose amount is optimized is compressed to high temperature and high pressure by the compressor 1, passes through the flow path switching valve 2, is radiated by the heat source side heat exchanger 3, and exits the liquid pipe 52.
  • the gas refrigerant that has been decompressed by the electronic expansion valves 4a and 4b and obtained the set superheat degree (for example, 1 to 5 ° C.) at the outlets of the load side heat exchangers 5a and 5b passes through the gas pipe 51 to the accumulator 60. It flows in and is sucked into the compressor 1 again.
  • the liquid refrigerant and the high-concentration refrigerating machine oil each form a layer in the accumulator 60 and stay in the lower part in the container A.
  • the refrigerating machine oil is heavier than the refrigerant.
  • the refrigerating machine oil is located below the refrigerant, and as shown in FIG. 4 (a), the refrigerating machine oil is sucked from the oil return hole D installed in the lower part of the accumulator 60, Oil is returned to the compressor 1.
  • the gas refrigerant in the heating operation, is compressed to high temperature and high pressure by the compressor 1, passes through the flow path switching valve 2, exits the gas pipe 51, and then radiates heat in the load side heat exchangers 5 a and 5 b. Then, after the pressure is reduced by the electronic expansion valves 4 a and 4 b, the gas or the two-phase refrigerant evaporated at the outlet of the heat source side heat exchanger flows into the accumulator 60 through the liquid pipe 52. At this time, the surplus refrigerant (liquid refrigerant) and the refrigerating machine oil each form a layer and stay in the container A separated.
  • the refrigerating machine oil becomes heavier than the refrigerant.
  • the oil is returned to the compressor 1 through the oil return hole D provided in.
  • the refrigerating machine oil becomes lighter than the liquid refrigerant, so that the refrigerating machine oil stays on top of the liquid refrigerant.
  • the refrigerating machine oil if liquid refrigerant is present at the position of the oil return hole D provided in the lower part of the accumulator 60 (outflow pipe C), the refrigeration oil is returned to the compressor 1 from the oil return hole D. It becomes difficult to oil.
  • FIG. 5 is a diagram illustrating the structure of the accumulator 6 according to the first embodiment.
  • the liquid refrigerant staying in the lower part in the container A and the refrigerating machine oil that is incompatible with the refrigerant are prevented from forming a layer, and the density of the refrigerant is higher than the density of the refrigerating machine oil. Even in large environments, it is possible to return oil.
  • the container A, the inflow pipe B, the outflow pipe C, the oil return hole D, the discharge port E, and the intake port F are the same as the accumulator of FIG.
  • the discharge port E is located at the opening of one end of the inflow branch pipe H.
  • the distribution joint G such as a Y-shaped joint or a T-shaped joint is a joint for distributing the mixture of the refrigerant and the refrigerating machine oil flowing in from the inflow pipe B to the inflow branch pipe H and the branch pipe I.
  • the inflow branch pipe H performs gas-liquid separation into a mixture of gas refrigerant, liquid refrigerant, and refrigerating machine oil (will play the same role as the inflow pipe B in FIG. 4).
  • the branch pipe I is a pipe for directly feeding the mixture of the refrigerant and the refrigerating machine oil distributed by the distribution joint G in order to stir the liquid refrigerant and the refrigerating machine oil staying in the lower part in the container A into the lower part of the container A. is there.
  • the agitation discharge port J is an opening portion of a pipe for discharging a mixture of the refrigerant and the refrigerating machine oil for stirring the liquid refrigerant and the refrigerating machine oil, and is here an opening part of one end of the branch pipe I. .
  • the stirring outlet J is directed to face the inner wall of the bottom of the container A.
  • the inner sectional area of the inflow branch pipe H is made larger than the inner sectional area of the branch pipe I.
  • Use a suitable pipe diameter For this reason, the mixture of the refrigerant and the refrigerating machine oil can be prevented from flowing excessively to the branch pipe I side, and can be prevented from flowing to the inflow branch pipe H side to reduce the gas-liquid separation efficiency.
  • by maintaining an inner cross-sectional area equal to or greater than that of the inlet side of the inflow pipe B it is possible to suppress an increase in pressure loss.
  • the outlet E of the inflow branch pipe H is located at the upper part of the accumulator 6 (upper half part in the vertical direction), because the time required for turning becomes longer, so that the gas-liquid separation efficiency becomes higher.
  • the discharge port E may be provided below the accumulator 6.
  • the branch pipe I is a thin pipe, and there is a risk of breaking due to vibration or the like. Therefore, for example, the branch pipe I is installed close to a portion of the outflow pipe C facing the vertical direction, and is fixed to the outflow pipe C with a fixture. And the intensity
  • the distribution joint G, the inflow branch pipe H, and the branch pipe I are connected to the inflow pipe B in the accumulator 6, and the refrigerant flowing from the inflow pipe B and the refrigeration Since the liquid refrigerant staying in the lower part in the container A and the refrigerating machine oil incompatible with the refrigerant are stirred by feeding the mixture with the machine oil so that the refrigerating machine oil is not retained in the upper part in the container A, the refrigerant, etc. Regardless of the temperature, the refrigeration oil can be transported to the oil return hole D and returned to the compressor 1.
  • the refrigerant ejected from the agitation outlet J is mixed with liquid refrigerant and gas refrigerant.
  • the liquid refrigerant in the container A and the gas refrigerant sent in are mixed.
  • Mixing and lowering the density of the refrigerant, which is a mixture of liquid and gas makes it easier for the refrigerating machine oil to stay in the lower part of the container A, and has the effect of making it easier to return the refrigerating machine oil from the oil return hole D. Regardless of the temperature of the refrigerant or the like, the refrigeration oil can be transported to the oil return hole D and returned to the compressor 1.
  • FIG. FIG. 6 is a diagram illustrating the structure of the accumulator 6 according to the second embodiment.
  • the same reference numerals as those in FIG. 5 perform the same functions as those described in the first embodiment.
  • a distribution joint K, a branch pipe L, and a branch branch pipe M are further connected to the branch pipe I by piping.
  • the distribution joint K is a joint for distributing the mixture of the refrigerant and the refrigerating machine oil flowing in from the branch pipe I to the branch pipe L and the branch branch pipe M, similarly to the distribution joint G.
  • the branch pipe L has a discharge port N at one end. When the amount of liquid refrigerant and refrigerating machine oil staying is large and the discharge port N is located below the liquid level, a mixture of refrigerant and refrigerating machine oil that stirs the liquid refrigerant and refrigerating machine oil is fed and stirred. It becomes the piping of. Further, when the discharge port N is located below the liquid level, similarly to the inflow branch pipe H, gas-liquid separation is performed into a mixture of gas refrigerant, liquid refrigerant, and refrigeration oil.
  • the branch branch pipe M is a pipe that feeds a mixture of refrigerant and refrigerating machine oil and stirs the liquid refrigerant and refrigerating machine oil staying in the container A.
  • a stirring outlet J is provided at one end of the branch branch pipe M.
  • the sum of the inner sectional areas of the lowermost branch pipe L and branch branch pipe M and the inner sectional area of the branch pipe I are made equal.
  • the sum of the inner cross-sectional areas of the inflow branch pipe H and the branch pipe I is made equal to the inner cross-sectional area of the inflow pipe B.
  • the inner sectional area of the branch pipe L is larger than the inner sectional area of the branch branch pipe J
  • the inner sectional area of the inflow branch pipe H is larger than the inner sectional area of the branch pipe I.
  • the inner cross-sectional area of the inflow branch pipe H > A in / 2
  • the inner cross-sectional area of the branch pipe I ⁇ A in / 2.
  • the inner sectional area of the branch pipe L > A in / 4
  • the inner sectional area of the branch pipe J ⁇ A in / 4.
  • the refrigerant that has been distributed by the distribution joint G and passed through the branch pipe I is further distributed to the branch pipe L and the branch branch pipe M by the distribution joint K.
  • the mixture is stirred by the mixture of the refrigerant and the refrigerating machine oil that has passed through the branch branch pipe M.
  • FIG. 7 is a diagram showing the structure of the accumulator 6 according to the third embodiment.
  • the liquid suction hole O is a hole having a certain interval (for example, an interval of 20 mm) between one end J and the other end of the branch pipe I. In the present embodiment, three holes are formed, but a smaller or larger number of liquid suction holes O may be provided.
  • the inner cross-sectional area of the branch pipe I is made smaller than the inner cross-sectional area of the inflow pipe B, so that the pipe is contracted (for example, the inner cross-sectional area A in of the inflow pipe B Cross-sectional area ⁇ A in / 4).
  • the pipe is contracted (for example, the inner cross-sectional area A in of the inflow pipe B Cross-sectional area ⁇ A in / 4).
  • the inner sectional area of the inflow branch pipe H is made larger than the inner sectional area of the branch pipe I.
  • the inner cross-sectional area ⁇ A in the inlet branch pipe H the pipe such that the inner cross-sectional area ⁇ A in / 4 of the branch pipe I make the diameter.
  • the liquid suction hole O is inserted into the branch pipe I for feeding the mixture of the refrigerant and the refrigerating machine oil into the liquid refrigerant and the refrigerating machine oil staying in the container A. Since, for example, even when the refrigeration oil is located above the liquid refrigerant, the refrigeration oil can be sucked from the liquid suction hole O and sent to the lower part in the container A, so that the oil return hole D The oil return from can be promoted.
  • FIG. FIG. 8 is a diagram illustrating the structure of the accumulator 6 according to the fourth embodiment.
  • the same reference numerals as those in FIG. 5 perform the same functions as those described in the first embodiment.
  • the distribution joint G of the present embodiment is different from the above-described embodiment in that it is connected to the inflow pipe B, the inflow branch pipe H, and the branch pipe I outside the container A.
  • the solenoid valve P performs an opening / closing operation for allowing or not allowing refrigerant or the like to pass through the branch pipe I.
  • the temperature detector Q detects the temperature of the refrigerant or the like flowing out from the outflow pipe C.
  • the control device 8 described above causes the solenoid valve P to perform an operation based on the temperature related to the detection of the temperature detector Q.
  • the temperature detector Q may be installed at a position where the temperature of the refrigerant flowing into the accumulator can be detected, for example, the inflow pipe B.
  • the magnitude relationship between the density of the refrigerant and the density of the refrigerating machine oil changes at about ⁇ 15 ° C., which is a low temperature environment. Therefore, for example, when the control device 8 determines that the temperature related to detection by the temperature detector Q is lower than a temperature (for example, ⁇ 14 ° C.) just before reaching ⁇ 15 ° C., the control device 8 opens the solenoid valve P, and the refrigerant In addition, the mixture of the refrigerating machine oil is allowed to pass through the branch pipe I, and the liquid refrigerant and the refrigerating machine oil that are staying are agitated.
  • a temperature for example, ⁇ 14 ° C.
  • the control device 8 closes the solenoid valve P so that the mixture of refrigerant and refrigerating machine oil does not pass through the branch pipe I. To do.
  • the mixture of the refrigerant and the refrigerating machine oil all flows to the inflow branch pipe H side, the gas-liquid separation efficiency can be made equal to that of a normal accumulator.
  • the inner cross-sectional area of the inflow branch pipe H is made equal to the inner cross-sectional area of the inlet pipe B. Further, the inner sectional area of the branch pipe I is made smaller than that of the inflow branch pipe H.
  • the tube diameter such that the inner cross-sectional area ⁇ A in the branch pipe I To do.
  • the temperature detector Q for detecting the temperature of the refrigerant and the like, and the refrigerant to the branch pipe I based on the temperature related to the detection of the temperature detector Q.
  • the refrigerating machine oil is located below the liquid refrigerant and the oil return hole is not required to stir.
  • the solenoid valve P can be closed. For this reason, the oil return which does not contain a liquid refrigerant can be performed, and the efficiency of oil return can be improved.
  • the circuit configuration is not complicated by installing the solenoid valve P in the accumulator 6 body.
  • Embodiment 5 FIG.
  • the refrigerant in the refrigerant circuit is carbon dioxide and the refrigerating machine oil is PAG oil has been described as an example, but a combination of other refrigerants and refrigerating machine oil may be used.
  • the refrigerant may be a refrigerant such as a mixed refrigerant composed of carbon dioxide and an ether such as dimethyl ether or hydrofluoroether.
  • the refrigerant is not limited to a supercritical state, but is a refrigerant that does not contain chlorine, such as an alternative refrigerant such as HFC410A and HFC407C, which is a refrigerant that performs heat exchange in a normal two-phase state, and a conventional Freon-based refrigerant such as R22 and R134a.
  • Natural refrigerants such as refrigerants and hydrocarbons may be used.
  • the refrigerating machine oil may be a refrigerating machine oil that is incompatible with each of these refrigerants.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
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  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un accumulateur et analogue qui peut assurer le retour d'huile sans complication d'architecture de circuit ou consommation d'énergie. L'accumulateur selon l'invention (6) effectue une séparation vapeur/liquide et accumule le liquide pour alimenter un fluide frigorigène dans une phase vapeur à un compresseur (1) dans un dispositif de cycle de réfrigération. L'accumulateur est équipé: d'un récipient (A) pour accumuler le liquide ; d'une conduite de débit entrant (B) à travers laquelle un fluide frigorigène, qui circule dans un circuit de réfrigération, s'écoule dans le récipient (A) ; d'un couplage de distribution (G) pour distribuer, dans une pluralité de directions, le fluide frigorigène qui s'est écoulé dans la conduite de débit entrant (B) ; d'une conduite de branchement (I) qui transporte le fluide réfrigérant vers la partie inférieure du récipient (A) de sorte que le fluide frigorigène agite le liquide accumulé dans le récipient (A) ; et d'une conduite de débit sortant (C) qui comporte un orifice de retour d'huile (D) hors duquel le fluide frigorigène s'écoule conjointement avec l'huile frigorigène dans le liquide accumulé dans le récipient (A).
PCT/JP2009/006331 2009-11-25 2009-11-25 Accumulateur et dispositif de cycle de réfrigération Ceased WO2011064813A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2011542984A JP5425221B2 (ja) 2009-11-25 2009-11-25 アキュムレータ及び冷凍サイクル装置
PCT/JP2009/006331 WO2011064813A1 (fr) 2009-11-25 2009-11-25 Accumulateur et dispositif de cycle de réfrigération

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Application Number Priority Date Filing Date Title
PCT/JP2009/006331 WO2011064813A1 (fr) 2009-11-25 2009-11-25 Accumulateur et dispositif de cycle de réfrigération

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WO2011064813A1 true WO2011064813A1 (fr) 2011-06-03

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013245836A (ja) * 2012-05-23 2013-12-09 Daikin Industries Ltd 冷凍装置
JP2013245837A (ja) * 2012-05-23 2013-12-09 Daikin Industries Ltd 冷凍装置
JP2014228177A (ja) * 2013-05-21 2014-12-08 日立アプライアンス株式会社 空気調和装置
JP2017015366A (ja) * 2015-07-06 2017-01-19 株式会社不二工機 アキュームレータ
CN107062715A (zh) * 2017-04-12 2017-08-18 青岛海信日立空调系统有限公司 一种气液分离器、空调系统以及冲刷过滤件的方法
WO2018088127A1 (fr) * 2016-11-10 2018-05-17 サンデン・オートモーティブクライメイトシステム株式会社 Accumulateur
JP2018128202A (ja) * 2017-02-09 2018-08-16 株式会社デンソー 貯液器
WO2019073564A1 (fr) * 2017-10-12 2019-04-18 三菱電機株式会社 Séparateur gaz-liquide et circuit de réfrigérant
CN113167507A (zh) * 2019-02-25 2021-07-23 Ats日本株式会社 制冷控制系统和冷却系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7578883B2 (ja) 2022-09-30 2024-11-07 ダイキン工業株式会社 冷凍サイクル装置
JP7578885B2 (ja) 2022-09-30 2024-11-07 ダイキン工業株式会社 冷凍サイクル装置
JP7578884B2 (ja) 2022-09-30 2024-11-07 ダイキン工業株式会社 冷凍サイクル装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS503162U (fr) * 1973-05-07 1975-01-14
JPH07189908A (ja) * 1993-12-28 1995-07-28 Mitsubishi Electric Corp アキュムレータ及び冷凍サイクル装置
JPH10141813A (ja) * 1996-11-06 1998-05-29 Mitsubishi Electric Corp アキュムレータ
JP2003262418A (ja) * 2002-03-06 2003-09-19 Mitsubishi Electric Corp 冷凍空調装置
JP2007139250A (ja) * 2005-11-16 2007-06-07 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0620056Y2 (ja) * 1987-12-29 1994-05-25 ダイキン工業株式会社 アキュムレータ
JPH01112375U (fr) * 1988-01-21 1989-07-28
JPH0569570U (ja) * 1992-02-25 1993-09-21 カルソニック株式会社 リキッドタンク

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS503162U (fr) * 1973-05-07 1975-01-14
JPH07189908A (ja) * 1993-12-28 1995-07-28 Mitsubishi Electric Corp アキュムレータ及び冷凍サイクル装置
JPH10141813A (ja) * 1996-11-06 1998-05-29 Mitsubishi Electric Corp アキュムレータ
JP2003262418A (ja) * 2002-03-06 2003-09-19 Mitsubishi Electric Corp 冷凍空調装置
JP2007139250A (ja) * 2005-11-16 2007-06-07 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9791176B2 (en) 2012-05-23 2017-10-17 Daikin Industries, Ltd. Refrigeration apparatus
JP2013245836A (ja) * 2012-05-23 2013-12-09 Daikin Industries Ltd 冷凍装置
EP2865970A4 (fr) * 2012-05-23 2016-04-06 Daikin Ind Ltd Congélateur
JP2013245837A (ja) * 2012-05-23 2013-12-09 Daikin Industries Ltd 冷凍装置
JP2014228177A (ja) * 2013-05-21 2014-12-08 日立アプライアンス株式会社 空気調和装置
JP2017015366A (ja) * 2015-07-06 2017-01-19 株式会社不二工機 アキュームレータ
WO2018088127A1 (fr) * 2016-11-10 2018-05-17 サンデン・オートモーティブクライメイトシステム株式会社 Accumulateur
JP2018128202A (ja) * 2017-02-09 2018-08-16 株式会社デンソー 貯液器
CN107062715A (zh) * 2017-04-12 2017-08-18 青岛海信日立空调系统有限公司 一种气液分离器、空调系统以及冲刷过滤件的方法
JPWO2019073564A1 (ja) * 2017-10-12 2020-10-01 三菱電機株式会社 気液分離器および冷媒回路
WO2019073564A1 (fr) * 2017-10-12 2019-04-18 三菱電機株式会社 Séparateur gaz-liquide et circuit de réfrigérant
CN113167507A (zh) * 2019-02-25 2021-07-23 Ats日本株式会社 制冷控制系统和冷却系统
CN113167507B (zh) * 2019-02-25 2023-03-31 Ats日本株式会社 制冷控制系统和冷却系统
US11841177B2 (en) 2019-02-25 2023-12-12 Ats Japan Co., Ltd. Refrigerant control system and cooling system

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