EP0838643A2 - Kältekreislauf mit zeotropem Kältemittel - Google Patents

Kältekreislauf mit zeotropem Kältemittel Download PDF

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Publication number
EP0838643A2
EP0838643A2 EP98101094A EP98101094A EP0838643A2 EP 0838643 A2 EP0838643 A2 EP 0838643A2 EP 98101094 A EP98101094 A EP 98101094A EP 98101094 A EP98101094 A EP 98101094A EP 0838643 A2 EP0838643 A2 EP 0838643A2
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EP
European Patent Office
Prior art keywords
refrigerant
open
composition ratio
close valve
pipe
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.)
Granted
Application number
EP98101094A
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English (en)
French (fr)
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EP0838643B1 (de
EP0838643A3 (de
Inventor
Kensaku Oguni
Kazumoto Urata
Masatoshi Muramatsu
Takeshi Endo
Hiroaki Matsushima
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Hitachi Ltd
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Hitachi Ltd
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Publication of EP0838643A3 publication Critical patent/EP0838643A3/de
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Publication of EP0838643B1 publication Critical patent/EP0838643B1/de
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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
    • 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
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers

Definitions

  • the invention relates to a refrigeration cycle using a nonazeotrope refrigerant according to the pre-characterizing portion of claim 1.
  • the non-azeotrope refrigerant is a refrigerant in which two or more types of refrigerants having different boiling points are mixed, and has characteristics shown in Fig. 3.
  • Fig. 3 is a vapor-liquid equilibrium diagram illustrating characteristics of a nonazeotrope refrigerant in which two types of refrigerants are mixed.
  • the horizontal axis indicates the composition ratio X of a refrigerant having a low boiling point, and the vertical axis indicates temperature.
  • a saturation vapor line and a saturation liquid line exist in a high temperature region indicated by pressure P H when, for example, pressure is high and when, conversely, pressure is low, these lines exist in a low temperature region indicated by pressure P L .
  • a saturation liquid line and a saturation vapor line are determined by the composition thereof.
  • X 0 denotes the composition ratio of a refrigerant sealed in a refrigeration cycle.
  • Points P1 to P4 indicate the typical points of the refrigeration cycle, and point P1 indicates a compressor outlet portion; point P2 indicates a condenser outlet portion; point P3 indicates an evaporator inlet portion; and point P4 indicates a compressor inlet portion.
  • Fig. 4 is an illustration of a problem caused by the leakage of a refrigerant to the outside. If liquid leaks, the remaining mixture refrigerant enters the state of X 1 in which the ratio of a low boiling-point refrigerant is large; if vapor leaks, the remaining mixture refrigerant enters the state of X 2 in which the ratio of a high boiling-point refrigerant is large.
  • X 0 indicates the composition ratio of a refrigerant which is sealed in initially. If a state in which the composition is X 0 is compared with a state in which the composition is X 1 at the same pressure, the temperature when the composition is X 1 is lower. If, however, a state in which the composition is X 0 is compared with a state in which the composition is X 2 at the same pressure, the temperature when the composition is X 2 is higher.
  • Fig. 5 shows general characteristics of a refrigeration cycle with respect to the composition ratio of the low boiling-point refrigerant.
  • the composition ratio of the refrigerant remaining within the refrigeration cycle changes from the initial composition ratio, i.e., from the designed composition ratio for the apparatus depending upon leaked portions. Even if there is no leakage to the outside, there is a possibility that the composition ratio of the refrigerant circulating within the refrigeration cycle may vary in the non-steady state of the refrigeration cycle.
  • Japanese Patent Unexamined Publication No. 59-129366 discloses that an electrostatic capacitance sensor is used as a means for detecting the composition of a refrigerant circulating within the refrigeration cycle. Further, it is disclosed that the refrigeration cycle comprises a first liquid receiver and a second liquid receiver, an electric heater being disposed in the second liquid receiver. When the outdoor air temperature is low during a heating operation, the electric heater of the second liquid receiver is operated and controlled so that a set refrigerant concentration is reached.
  • an apparatus comprising a separator for separating a low-boiling-point refrigerant, a liquid receiver for storing a low-boiling-point refrigerant, and a control valve for returning the refrigerant from the liquid receiver, which apparatus controls the composition of the refrigerant on the basis of the temperature of an element to be cooled.
  • a mixture refrigerant composition variable refrigeration cycle in which the upper portion of the liquid receiver is connected to a refrigerant tank and the lower portion of the liquid receiver is connected to the refrigerant tank, which refrigeration cycle comprises a refrigerant tank capable of exchanging heat with a gas pipe through which a heat-source-side heat exchanger is connected to a use-side heat exchanger, a liquid receiver and the like.
  • the composition ratio of the refrigerant within the refrigeration cycle may vary when the refrigerant leaks out of the refrigeration cycle or during the non-steady operation of the refrigeration cycle.
  • the capacity of the refrigeration cycle can be varied by making the composition variable. Therefore, to obtain a high-capacity refrigeration cycle, it is important to control the refrigerant composition ratio within the refrigeration cycle so as to realize a stable operation. There has been a demand for a method of varying this composition ratio inexpensively. Further, it is necessary to use a refrigerant which does not contain chlorine and does not damage the ozone layer, in which a consideration is given to safeguard the earth environment.
  • US-A-5 186 012 discloses a heat pump system using a non-azeotropic refrigerant mixture comprising a main refrigeration circuit, an engine coolant circuit, and a refrigerant rectifier circuit interfacing with the main refrigeration circuit and the engine coolant circuit.
  • the refrigerant rectifier circuit comprises in order of decreasing relative elevation a condenser, a storage vessel in communication with a condenser, a rectifier in communication with a storage tank and a condenser, a receiver vessel in communication with a rectifier, and a boiler in communication with the rectifier and the receiver vessel.
  • a ratio detecting means is disposed in the receiver.
  • the refrigerant rectifier circuit is used to adjust the relative concentrations of lower boiling point refrigerant, and higher boiling point refrigerant in the non-azeotropic refrigerant mixture thereby changing the cooling or heating capacity of the heat pump system.
  • liquid refrigerant can be taken from the receiver.
  • the composition ratio detecting means is not disposed in the receiver but between the heat-source-side heat exchanger and the receiver. This arrangement of the composition ratio detecting means allows a more accurate measurement of the refrigerant composition ratio mainly used in the refrigeration cycle.
  • Fig. 1 illustrates a refrigeration cycle in which a plurality of indoor machines are connected to one outdoor machine in accordance with a first embodiment of the present invention.
  • reference numeral 1 denotes a compressor
  • reference numeral 2 denotes an outdoor heat exchanger
  • reference numeral 3 denotes an outdoor air blower
  • reference numeral 4 denotes a four-way valve
  • reference numeral 5 denotes an accumulator
  • reference numeral 6 denotes a receiver
  • reference numeral 7 denotes an outdoor refrigerant control valve which acts as a pressure reducing mechanism during a heating operation.
  • Reference numeral 8 denotes a sensor for detecting the composition of a non-azeotrope refrigerant
  • reference numeral 10 denotes a refrigerant tank
  • reference numeral 11 denotes a cooling unit
  • reference numerals 12, 13 and 14 denote open/close valves
  • reference numerals 15, 16 and 17 denote pipes
  • reference numerals 91, 92, 93 and 94 denote check valves which constitute an outdoor machine.
  • Reference numerals 20a and 20b denote indoor heat exchangers; reference numerals 21a and 21b denote indoor refrigerant control valves which act as a pressure reducing mechanism during a cooling operation; reference numerals 22 and 23 denote refrigerant distribution units; and reference numerals 24 and 25 denote pipes for connecting indoor machines to outdoor machines. The illustration of the indoor air blower is omitted.
  • a detecting apparatus in which an electrostatic capacitance sensor 8 for detecting the composition of a non-azeotrope refrigerant is used, and a control apparatus for controlling the open/close valves 12, 13 and 14 are disposed on the outdoor side.
  • Fig. 1 the illustration of the control system of the refrigeration cycle is omitted.
  • a refrigerant which does not contain chlorine and does not damage the ozone layer is used as the refrigerant.
  • HFC32 and HFC134a are used as the non-azeotrope refrigerant will be explained.
  • the refrigerant discharged from the compressor flows in the following order: the four-way valve 4 ⁇ the outdoor heat exchanger 2 ⁇ the check valve 93 ⁇ the composition sensor 8 ⁇ the outdoor refrigerant control valve 7 ⁇ the check valve 92 ⁇ the receiver 6.
  • the refrigerant is distributed by a refrigerant distribution unit 23, a part of the refrigerant flows in the order: the indoor heat exchanger 20a ⁇ the indoor refrigerant control valve 21a, and the other flow in the order: the indoor heat exchanger 20b ⁇ the indoor refrigerant control valve 21b.
  • the indoor heat exchangers 20a and 20b act as evaporators and a cooling operation is performed.
  • the refrigerant discharged from the compressor flows in the following order: the four-way valve 4 ⁇ the pipe 24 ⁇ the distribution unit 22.
  • a part of the refrigerant flows in the order: the indoor refrigerant control valve 21a ⁇ the indoor heat exchanger 20a, and the other flow in the order: the indoor refrigerant control valve 21b ⁇ the indoor heat exchanger 20b.
  • the indoor heat exchangers 20a and 20b act as condensers and a heating operation is performed.
  • a cooling unit 11 is a double-pipe heat exchanger.
  • the open/close valves 12 and 13 are opened.
  • the liquid in the bottom of the receiver 6 flows out through the open/close valve 12, and the liquid is formed into a low-temperature refrigerant by the pressure reducing effect of the open/close valve 12 and guided into the inner pipe of the cooling unit 11.
  • gas inside the receiver 6 flows out through the open/close valve 13 and is guided into the outer pipe of the cooling unit 11.
  • the low-temperature refrigerant gas of the inner pipe exchanges heat with the gas of the outer pipe, and the low-temperature refrigerant is gasified and guided into the accumulator 5 through the pipe 15.
  • the condensed liquefied refrigerant of the outer pipe is guided into the refrigerant storage tank 10.
  • the open/close valves 12 and 13 are closed. The above operation and effect make it possible to store the liquid refrigerant in the refrigerant storage tank 10.
  • the open/close valve 14 is opened so that the liquid refrigerant can be discharged to the accumulator 5 through the pipe 15.
  • composition varying effect will be explained below.
  • Fig. 6 illustrates changes of the state of the refrigerant in a refrigerant passage from the condenser to the receiver when a non-azeotrope refrigerant is used as a thermal medium.
  • the horizontal axis indicates the composition ratio X of the lowboiling-point refrigerant, i.e., HFC32, and the vertical axis indicates temperature, with pressure being constant.
  • the composition ratio X 0 indicates the composition ratio of the refrigerant sealed in the refrigeration cycle.
  • Point A indicates the state of the inlet of the condenser; point B indicates the condensation start point; point C indicates the state of the inside of the receiver; and point D indicates the state of the outlet of the cooling unit.
  • Point C indicates that the flow rate of the liquid is very small.
  • Point E indicates the liquid state inside the receiver, and the composition ratio of HFC32 is X 1 .
  • Point F indicates the gas state, and the composition ratio of HFC32 is X g . It can be seen that the composition ratio of gas at point F is greater than the composition ratio X 0 of the refrigerant sealed in the refrigeration cycle, and the composition ratio in the refrigeration cycle can be varied by taking out gas.
  • a gas refrigerant having a large composition ratio of HFC32 taken out from the upper portion of the receiver 6 is liquefied in the cooling unit 11 and stored in the tank 10.
  • the composition ratio of the refrigerant within the refrigeration cycle becomes smaller than X 0 .
  • the composition ratio of the refrigerant within the refrigeration cycle is smaller than X 0 , it is possible to return the refrigerant having a large composition ratio of HFC32 to the refrigeration cycle by opening the open/close valve 14.
  • the refrigerant composition ratio in the main refrigeration cycle can be varied by taking out or returning the gas refrigerant inside the receiver.
  • the present invention may be applied to a mixture refrigerant of more than two types.
  • the present invention may be applied to a threetype mixture refrigerant of HFC32, HFC125 and HFC134a shown in Fig. 7.
  • the numeric values shown in Fig. 7 indicate weight percentage (%) of HFC32, HFC125 and HFC134a, and a mixture refrigerant of various weight percentages may be considered.
  • HFC32, HFC125 and HFC134a the boiling points of HFC32 and HFC125 are higher than that of HFC134a, and therefore the present invention utilizing the difference between the boiling points of mixed refrigerants may be applied.
  • HFC32 and HFC125 exhibit azeotropic characteristics which can be regarded as a single refrigerant, and the abovedescribed mixture refrigerant can be assumed as a mixture refrigerant of the azeotrope refrigerant of HFC32 and HFC125, and HFC134a.
  • the composition varying function of the present invention may be exhibited for a mixture refrigerant of HFC32, HFC125 and HFC134a.
  • gas in the upper portion of the receiver 6 is a low boiling-point refrigerant having a large refrigerant composition ratio, whose compositions of HFC32 and HFC125 from among the three types of refrigerants are large.
  • the gas having large compositions of HFC32 and HFC125, taken out from the upper portion of the receiver 6, is liquefied by the cooling unit 11 and stored in the tank 10.
  • the composition ratios of low-boiling-point refrigerants, i.e., HFC32 and HFC125 are small, and the composition ratio of the high-boiling-point refrigerant, i.e., HFC134a, is large.
  • composition ratio within the refrigeration cycle it is possible to return the composition ratio of the HFC32 and HFC125 to the original state by opening the open/close valve 14. As stated above, it is possible to vary the composition of the refrigerant in the case of a three-type mixture refrigerant.
  • Fig. 8 is a sectional view of the electrostatic capacitance type composition detecting sensor 8 shown in Fig. 1.
  • reference numeral 53 denotes an outer tube electrode
  • reference numeral 54 denotes an inner tube electrode, both of which are hollow tubes.
  • the inner tube electrode 54 is fixed at its both ends by stoppers 55a and 55b in which a circular groove is provided in the central portion of the outer tube electrode 53.
  • the outer diameter of the stoppers 55a and 55b is nearly the same as the inner diameter of the outer tube electrode 53, and the side opposite to the inner tube electrode holding side is fixed by the refrigerant introduction pipe 59 having an outer diameter nearly the same as the inner diameter of the outer tube electrode 53.
  • the refrigerant introduction pipe 59 is fixed to the outer tube electrode 53.
  • the inner tube electrode 54 is fixed to the central portion of the outer tube electrode 53.
  • An outer-tube electrode signal line 56 and an inner-tube electrode signal line 57 are connected to the outer tube electrode 53 and the inner tube electrode 54 in order to detect an electrostatic capacitance value.
  • a signal line guide tube 58 e.g. a hermetic terminal for guiding the inner-tube electrode signal line 57 to the outside of the outer tube electrode 53 and for preventing the refrigerant inside from escaping to the outside, are disposed outside the inner-tube electrode signal line 57.
  • At least one through passage having a size smaller than the inner diameter of the inner tube electrode 54 is disposed in the central portion thereof, and at least one passage for the refrigerant is disposed at a place between the inner tube electrode 54 and the outer tube electrode 53, so that the flow of the mixture refrigerant flowing through the inside is not obstructed.
  • Fig. 9 illustrates the relationship between the composition ratio of the refrigerant and the electrostatic capacitance value when the electrostatic capacitance sensor is used.
  • Fig. 9 illustrates measured values obtained when HFC134a is used as a high boiling-point refrigerant and HFC32 is used as a low boiling-point refrigerant from among the mixture refrigerant and they are sealed in the composition ratio detecting sensor shown in Fig. 8 as gas and liquid, respectively.
  • the horizontal axis indicates the composition ratio of the HFC32, and the vertical axis indicates the electrostatic capacitance value which is an output from the composition ratio detecting sensor 8.
  • a comparison of the electrostatic capacitance value of gas of each refrigerant with that of liquid of each refrigerant shows that the liquid refrigerant has a larger value, and the difference between the electrostatic capacitance value of gas and that of liquid is large, in particular, in the HFC134a. This indicates that the electrostatic capacitance value varies when the dryness of the refrigerant varies.
  • a comparison between the electrostatic capacitance values of HFC134a and HFC32 shows that HFC32 has a larger electrostatic capacitance value for both liquid and gas. This indicates that only a gas or liquid refrigerant exists in the composition ratio detecting sensor 8, and when the composition of the refrigerant varies, the electrostatic capacitance value varies.
  • the composition ratio detecting sensor 8 since the inside of the composition ratio detecting sensor 8 enters a two-phase state of gas and liquid, the electrostatic capacitance value varies due to the dryness of the refrigerant in addition to the composition ratio of the mixture refrigerant, it becomes impossible to detect the composition ratio. Therefore, when the composition ratio of the mixture refrigerant is detected by using the composition ratio detecting sensor 8, it is necessary to dispose the composition ratio detecting sensor 8 in a portion where the refrigerant is always gas or liquid in the refrigeration cycle. In this embodiment, since the check valves 91 to 94 are arranged, the refrigerant passing through the composition ratio detecting sensor 8 is in a liquid state. Means other than the electrostatic capacitance type may be used for the composition ratio detecting means.
  • Fig. 10 is a flowchart illustrating a method of controlling the refrigeration cycle shown in Fig. 1.
  • the composition ratio is determined on the basis of a signal from the composition ratio detecting sensor 8.
  • a check is made to determine whether the detected composition ratio X is greater than the composition ratio X 0 of the refrigerant sealed in the refrigeration cycle.
  • the open/close valves 12 and 13 are opened.
  • the open/close valves 12 and 13 are closed.
  • composition of the refrigerant within the refrigeration cycle to X 0 or thereabouts, making it possible to prevent the pressure on the high pressure side from abnormally increasing and making a stable operation possible. Since the composition ratio of the nonazeotrope refrigerant can be varied, it becomes possible to vary the heating and cooling capacity as shown in Fig. 3.
  • Fig. 11 also shows a refrigeration cycle in which the composition ratio of the non-azeotrope refrigerant can be varied, and the functions of the embodiment shown in Fig. 1 are integrated.
  • Components in Fig. 11 having the same reference numerals as those in Fig. 1 designate identical components.
  • Reference numerals 33 and 34 denote pipes.
  • Reference numeral 40 denotes a refrigerant tank; reference numerals 41 and 43 denote open/close valves; and reference numerals 42 and 44 denote pipes.
  • the refrigerant tank 40 is formed integral with the accumulator 5 as shown in Fig.
  • the gas refrigerant inside the receiver 6 can be condensed and liquefied by making the gas refrigerant flow into the tank 40 via the open/close valve 41 and exchanging heat with the accumulator 5. It is also possible to make the liquid refrigerant in the bottom portion of the tank 40 flow out into the accumulator 5 via the open/close valve 43 so that the liquid refrigerant is returned to the main refrigeration cycle. Therefore, by opening the open/close valve 41, it is possible to release gas having a large composition ratio of HFC32 from the main refrigeration cycle and decrease the composition ratio of HFC32. On the other hand, by opening the open/close valve 43, it is possible to release the liquid refrigerant having a large composition ratio of HFC134a from the main refrigeration cycle and decrease the composition ratio of HFC134a.
  • Fig. 12 is a detailed view of the receiver 6, the accumulator 5 and the tank 40, all of which are shown in Fig. 11.
  • Components in Fig. 12 having the same reference numerals as those in Fig. 11 designate identical components.
  • a pipe 34 through which the accumulator 5 is connected to the compressor 1 is formed into a U-shape inside the accumulator 5, and the end portion thereof is open in the upper portion of the accumulator 5.
  • a hole 36 for returning oil circulating within the refrigeration cycle is disposed in the bottommost portion of the U-shape, and a hole 35 for making a part of gas flow out is disposed in the topmost portion of the U-shape.
  • a pipe 42 and the open/close valve 41 are connected to each other at an appropriate position in the upper portion of the receiver 6 and at an appropriate position in the upper portion of the refrigerant tank 40. Further, a pipe 44 and the open/close valve 43 are connected to each other at appropriate positions of the lower portion of the accumulator 5 and the refrigerant tank 40.
  • the refrigerant tank 40 is formed integral in the lower portion of the accumulator 5 in Fig. 12, the refrigerant tank 40 may be arranged in any way if heat can be exchanged between the accumulator 5 and the refrigerant tank 40.
  • Fig. 13 is a flowchart for controlling the refrigeration cycle shown in Fig. 11.
  • the composition ratio is determined on the basis of a signal from the composition ratio detecting sensor.
  • a check is made to determine whether the detected composition ratio X is greater than the composition ratio X 0 of the refrigerant sealed in the refrigeration cycle.
  • the open/close valve 41 is opened.
  • the open/close valve 41 is closed.
  • the open/close valve 43 is opened.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP98101094A 1993-06-24 1994-06-21 Kältekreislauf mit nicht-azeotropem Kältemittel Expired - Lifetime EP0838643B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP15324693 1993-06-24
JP15324693A JPH0712411A (ja) 1993-06-24 1993-06-24 冷凍サイクルおよび冷凍サイクルの冷媒組成比制御方法
JP153246/93 1993-06-24
EP19940109583 EP0631095B1 (de) 1993-06-24 1994-06-21 Verfahren zum Einfüllen eines nichtazeotropen Kältemittels in einen Kältekreislauf und zum Einstellen dessen Zusammensetzung

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP19940109583 Division EP0631095B1 (de) 1993-06-24 1994-06-21 Verfahren zum Einfüllen eines nichtazeotropen Kältemittels in einen Kältekreislauf und zum Einstellen dessen Zusammensetzung

Publications (3)

Publication Number Publication Date
EP0838643A2 true EP0838643A2 (de) 1998-04-29
EP0838643A3 EP0838643A3 (de) 2000-11-15
EP0838643B1 EP0838643B1 (de) 2003-04-09

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Application Number Title Priority Date Filing Date
EP19940109583 Expired - Lifetime EP0631095B1 (de) 1993-06-24 1994-06-21 Verfahren zum Einfüllen eines nichtazeotropen Kältemittels in einen Kältekreislauf und zum Einstellen dessen Zusammensetzung
EP98101094A Expired - Lifetime EP0838643B1 (de) 1993-06-24 1994-06-21 Kältekreislauf mit nicht-azeotropem Kältemittel

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP19940109583 Expired - Lifetime EP0631095B1 (de) 1993-06-24 1994-06-21 Verfahren zum Einfüllen eines nichtazeotropen Kältemittels in einen Kältekreislauf und zum Einstellen dessen Zusammensetzung

Country Status (3)

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EP (2) EP0631095B1 (de)
JP (1) JPH0712411A (de)
DE (2) DE69432489T2 (de)

Cited By (2)

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EP1186839A3 (de) * 2000-09-08 2002-08-28 Hitachi Air Conditioning Systems Co., Ltd. Kältekreislauf
EP3919839A1 (de) 2020-06-04 2021-12-08 Commissariat à l'Energie Atomique et aux Energies Alternatives Verfahren zur bestimmung der entwicklung der zirkulierenden zusammensetzung eines arbeitsfluids

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US5927087A (en) * 1994-11-29 1999-07-27 Ishikawa; Atuyumi Refrigerating cycle
JPH08152207A (ja) * 1994-11-29 1996-06-11 Sanyo Electric Co Ltd 空気調和機
JPH08254363A (ja) * 1995-03-15 1996-10-01 Toshiba Corp 空調制御装置
JP3655681B2 (ja) * 1995-06-23 2005-06-02 三菱電機株式会社 冷媒循環システム
JPH10267436A (ja) * 1997-01-21 1998-10-09 Mitsubishi Electric Corp 冷凍空調装置
JP3185722B2 (ja) * 1997-08-20 2001-07-11 三菱電機株式会社 冷凍空調装置および冷凍空調装置の冷媒組成を求める方法
US5848537A (en) * 1997-08-22 1998-12-15 Carrier Corporation Variable refrigerant, intrastage compression heat pump
JP4848608B2 (ja) * 2001-09-12 2011-12-28 三菱電機株式会社 冷媒回路
KR20050072299A (ko) * 2004-01-06 2005-07-11 삼성전자주식회사 냉난방 공기조화시스템
US20090301108A1 (en) * 2008-06-05 2009-12-10 Alstom Technology Ltd Multi-refrigerant cooling system with provisions for adjustment of refrigerant composition
US9857113B2 (en) * 2011-06-16 2018-01-02 Mitsubishi Electric Corporation Air-conditioning apparatus
US10001308B2 (en) 2011-12-22 2018-06-19 Mitsubishi Electric Corporation Refrigeration cycle device
KR102477524B1 (ko) * 2018-01-26 2022-12-15 엘지전자 주식회사 공기조화기
NO344169B1 (en) * 2018-06-04 2019-09-30 Waertsilae Gas Solutions Norway As Method and system for storage and transport of liquefied petroleum gases
JP7258106B2 (ja) * 2018-06-29 2023-04-14 三菱電機株式会社 冷凍サイクル装置

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EP3919839A1 (de) 2020-06-04 2021-12-08 Commissariat à l'Energie Atomique et aux Energies Alternatives Verfahren zur bestimmung der entwicklung der zirkulierenden zusammensetzung eines arbeitsfluids
FR3111193A1 (fr) 2020-06-04 2021-12-10 Commissariat A L'energie Atomique Et Aux Energies Alternatives Procédé de détermination de l’évolution de la composition circulante d’un fluide de travail

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EP0631095A3 (de) 1995-03-01
EP0838643B1 (de) 2003-04-09
EP0838643A3 (de) 2000-11-15
DE69422551D1 (de) 2000-02-17
JPH0712411A (ja) 1995-01-17
EP0631095B1 (de) 2000-01-12
DE69432489D1 (de) 2003-05-15
DE69432489T2 (de) 2004-02-12
EP0631095A2 (de) 1994-12-28
DE69422551T2 (de) 2000-08-03

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