EP0485873B1 - Vorrichtung für Rückgewinnung und Reinigung von Kältemittel - Google Patents

Vorrichtung für Rückgewinnung und Reinigung von Kältemittel Download PDF

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Publication number
EP0485873B1
EP0485873B1 EP91118875A EP91118875A EP0485873B1 EP 0485873 B1 EP0485873 B1 EP 0485873B1 EP 91118875 A EP91118875 A EP 91118875A EP 91118875 A EP91118875 A EP 91118875A EP 0485873 B1 EP0485873 B1 EP 0485873B1
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EP
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Prior art keywords
refrigerant
compressor
conduit
valve means
valve
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EP91118875A
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English (en)
French (fr)
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EP0485873A1 (de
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Lowell Edward Paige
Chester David Ripka
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Carrier Corp
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Carrier Corp
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Priority claimed from US07/612,643 external-priority patent/US5127232A/en
Priority claimed from US07/612,641 external-priority patent/US5174124A/en
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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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/002—Collecting refrigerant from a cycle

Definitions

  • a wide variety of mechanical refrigeration systems are currently in use in a wide variety of applications. These applications include domestic refrigeration, commercial refrigeration, air conditioning, dehumidifying, food freezing, cooling and manufacturing processes, and numerous other applications.
  • the vast majority of mechanical refrigeration systems operate according to similar, well known principals, employing a closed-loop fluid circuit through which a refrigerant flows.
  • a number of saturated fluorocarbon compounds and azeotropes are commonly used as refrigerants in refrigeration systems. Representative of these refrigerants are R-12, R-22, R-500 and R-502.
  • Such service may include removal, of, and replacement or repair of, a component of the system.
  • the refrigerant can become contaminated by foreign matter within the refrigeration circuit, or by excess moisture in the system. The presence of excess moisture can cause ice formation in the expansion valves and capillary tubes, corrosion of metal, copper plating and chemical damage to insulation in hermetic compressors. Acid can be present due to motor burn out which causes overheating of the refrigerant. Such burn outs can be temporary or localized in nature as in the case of a friction producing chip which produces a local hot spot which overheats the refrigerant.
  • the main acid of concern is HCL but other acids and contaminants can be produced as the decomposition products of oil, insulation, varnish, gaskets and adhesives. Such contamination may lead to component failure or it may be desirable to change the refrigerant to improve the operating efficiency of the system.
  • devices that are designed to recover the refrigerant from refrigeration systems.
  • the devices often include means for processing the refrigerants so recovered so that the refrigerant may be reused.
  • Representative examples of such devices are shown in the following United States Patents: 4,441,330 "Refrigerant Recovery And Recharging System” to Lower et al; 4,476,688 “Refrigerant Recovery And Purification System” to Goddard; 4,766,733 “Refrigerant Reclamation And Charging Unit” to Scuderi; 4,809,520 “Refrigerant Recovery And Purification System” to Manz et al; 4,862,699 “Method And Apparatus For Recovering, Purifying and Separating Refrigerant From Its Lubricant” to Lounis; 4,903,499 “Refrigerant Recovery System” to Merritt; and 4,942,741 "Refrigerant Recovery Device” to Hancock et al.
  • a recovery compressor is used to withdraw the refrigerant from the unit being serviced.
  • Another feature considered desirable in such recovery systems is to have a refrigerant quality test system incorporated in the recovery systems itself.
  • protection of the recovery compressor is achieved by providing an apparatus for recovering compressible refrigerant from a refrigeration system and delivering the recovered refrigerant to a refrigeration storage means.
  • the operation of the apparatus includes the steps of withdrawing refrigerant from a refrigeration system being serviced and compressing the withdrawn refrigerant in a compressor to form a high pressure gaseous refrigerant.
  • the high pressure gaseous refrigerant is delivered to a condenser where it is condensed to form liquid refrigerant.
  • the liquid refrigerant from the condenser is delivered to the refrigerant storage means.
  • Means are provided for determining the pressure ratio across the recovery system compressor and monitoring the determined pressure ratio. When the monitored pressure ratio exceeds a predetermined value above which the compressor may be adversely affected the system is caused to stop the withdrawal of refrigerant from the refrigeration system being serviced.
  • the system begins to withdraw stored refrigerant from the storage means.
  • the refrigerant withdrawn from the storage means is then compressed in the same compressor which was used to compress refrigerant withdrawn from the refrigeration system.
  • This refrigerant is then condensed to form liquid refrigerant which is then passed through a suitable expansion device and delivered back to the storage means to thereby cool the storage means and the refrigerant contained therein.
  • This cooling cycle is performed for a period of time until the temperature of the storage means falls to a predetermined value. At that point the system resumes withdrawal of refrigerant from the refrigeration system being serviced. When the suction pressure of the recovery system compressor falls below a predetermined value the recovery operation is terminated.
  • a refrigerant recovery system is operated to withdraw compressible refrigerant from a refrigeration system by first drawing liquid refrigerant from the system being serviced through a suitable conduit and delivering the withdrawn refrigerant to a refrigerant storage means.
  • the refrigerant storage means At least a portion of the refrigerant so withdrawn exits in gaseous form.
  • a portion of this gaseous refrigerant is withdrawn from the storage means and compressed to form a high pressure gaseous refrigerant.
  • the high pressure gaseous refrigerant is then condensed to form a high pressure liquid refrigerant.
  • the high pressure liquid refrigerant is passed through an expansion device where the refrigerant under goes a pressure drop and is at least partially flashed to a vapor.
  • the liquid vapor mixture is then delivered to the storage means where it evaporates and absorbs heat from the refrigerant within the storage means thereby cooling the storage means and lowering the pressure therein, thereby increasing the withdrawal of liquid refrigerant from the refrigeration system through the conduit.
  • the rate of liquid level change in the storage means is monitored. When that rate reaches a value which indicates that liquid is no longer being withdrawn, the system shifts automatically to the vapor recovery mode of operation.
  • control system means for sensing a system control parameter which has a detectable change in value which occurs at a time which may be correlated with the time at which the state of the refrigerant being withdrawn from the refrigeration system changes from a liquid to vapor.
  • a signal indicating that the detectable change has occurred causes the system to shift from a liquid recovery mode to a vapor recovery mode.
  • Purity of the recovered refrigerant may be determined by use of a method and apparatus for sampling the purity of the refrigerant flowing through a refrigeration system.
  • the refrigeration system includes a compressor having an inlet port which has an inlet conduit associated therewith and defining in part the low pressure side of the refrigeration system.
  • the compressor further has an outlet port for having an out conduit associated therewith which defines in part the high pressure side of the refrigeration system.
  • a refrigerant sampling chamber is operatively connected in parallel in fluid flow communication with the compressor. The compressor is then operated to establish the flow of refrigerant through the system and a quantity of refrigerant is withdrawn from the high pressure side of the system. The withdrawn quantity of refrigerant is then passed through the sampling chamber and thence returned to the low pressure side of the system.
  • FIG. 10 An apparatus for recovering and purifying the refrigerant contained in a refrigeration system is generally shown at reference numeral 10 in Figure 1.
  • the refrigeration system to be evacuated is generally indicated at 12 and may be virtually any mechanical refrigeration system.
  • the interface or tap between the recovery and purification system 10 and the system being serviced 12 is a standard gauge and service manifold 14.
  • the manifold 14 is connected to the refrigeration system to be serviced in a standard manner with one line 16 connected to the low pressure side of the system 12 and another line 18 connected to the high pressure side of the system.
  • a high pressure refrigerant line 20 is interconnected between the service connection 22 of the service manifold and a T connection 11 for coupling the line 20 to the recovery system 10.
  • a filter-dryer 13 which is mounted external of the recovery system. This device as will be seen, is normally installed in the line 20 only when the system is to be operated first in the liquid recovery mode of operation.
  • the recovery system 10 includes two sections, as shown in Figure 1 the components and controls of the recovery system are contained within a self contained compact housing (not shown) schematically represented by the dotted line 24.
  • a refrigerant storage section of the system is contained within the confines of the dotted lines 26.
  • the first path i.e. the liquid path
  • an electrically actuatable solenoid valve SV7 This valve will selectively allow refrigerant to pass therethrough when actuated to its open position or will prevent the flow of refrigerant therethrough when electrically actuated to its closed position.
  • Additional electrically actuatable solenoid valves contained in the system operate in the same conventional manner.
  • liquid refrigerant line 15 extends to the refrigerant storage section of the system 26 where it communicates through a valve 90 with a refrigerant storage cylinder 86.
  • liquid refrigerant passes through the line 15 directly from the refrigeration system 12 to the storage cylinder 86.
  • gaseous refrigerant flowing through the interconnecting line 20 flows through the T-11 and to the right to electrically actuatable solenoid valve SV3.
  • refrigerant passes through a conduit 28 through a check valve 98 to a second electrically actuatable solenoid valve SV2.
  • an appropriate conduit 30 conducts the refrigerant to the inlet of a combination accumulator/oil trap 32 having a drain valve 34.
  • Refrigerant gas is then drawn from the oil trap through conduit 36 to an acid purification filter-dryer 38 where impurities such as acid, moisture, foreign particles and the like are removed before the gases are passed via conduit 40 to the suction port 42 of the compressor 44.
  • a suction line accumulator 46 is disposed in the conduit 42 to assure that no liquid refrigerant passes to the suction port 42 of the compressor.
  • the compressor 44 is preferably of the rotary type, which are readily commercially available from a number of compressor manufacturers but may be of any type such as reciprocating, scroll or screw.
  • gaseous refrigerant is directed through conduit 50 to a conventional float operated oil separator 52 where oil from the recovery system compressor 44 is separated from the gaseous refrigerant and directed via float controlled return line 54 to the conduit 40 communicating with the suction port of the compressor.
  • oil from the recovery system compressor 44 is separated from the gaseous refrigerant and directed via float controlled return line 54 to the conduit 40 communicating with the suction port of the compressor.
  • gaseous refrigerant passes via conduit 56 to the inlet of a heat exchanger/condenser coil 60.
  • An electrically actuated condenser fan 62 is associated with the coil 60 to direct the flow of ambient air through the coil as will be described in connection with the operation of the system.
  • an appropriate conduit 66 conducts refrigerant to a T-connection 68.
  • one conduit 70 passes to another electrically actuated solenoid valve SV4 while the other branch 72 of the T passes to a suitable refrigerant expansion device 74.
  • the expansion device 74 is a capillary tube and a strainer 76 is disposed in the refrigerant line 72 upstream from the capillary tube to remove any particles which might potentially block the capillary. It should be appreciated that the expansion device could comprise any of the other numerous well known refrigerant expansion devices which are widely commercially available.
  • the conduit 72 containing the expansion device 74 and the conduit 70 containing the valve SV4 rejoin at a second T connection 78 downstream from both devices.
  • the solenoid valve SV4 and the expansion device 74 are in a parallel fluid flow relationship.
  • the solenoid valve SV4 when the solenoid valve SV4 is open the flow of refrigerant will be, because of the high resistance of the expansion device, through the solenoid valve in a substantially unrestricted manner.
  • the valve SV4 is closed, the flow of refrigerant will be through the high resistance path provided by the expansion device.
  • Combination devices such as electronically actuated expansion valves are known which would combine the functions of the valves SV4 and the capillary tube 74, however, as configured and described above, the desired function is obtained at a minimum cost.
  • a conduit 80 passes to an appropriate coupling (not shown) for connection of the system as defined by the confines of the line 24, via a flexible refrigerant line 82 to the liquid inlet port 84 of the previously referred to refillable refrigerant storage container 86.
  • the container 86 is of conventional construction and includes a second port 88 adapted for vapor outlet.
  • the storage cylinder 86 further includes a liquid level indicator 92.
  • the liquid level indicator for example, may comprise a compact continuous liquid level sensor of the type available from Imo Delaval Inc., Gems Sensors Division. Such an indicator is capable of providing an electrical signal indicative of the level of the refrigerant contained within the storage cylinder 86.
  • Refrigerant line 94 interconnects the vapor outlet 88 of the cylinder 86 with a T connection 96 in the conduit 28 extending between solenoid valve SV3 and solenoid valve SV2.
  • An additional electrically actuated solenoid valve SV1 is located in the line 94.
  • a check valve 98 is also positioned in the conduit 28 at a location downstream of the T-96 which is adapted to allow flow in the direction from SV3 to SV2 and to prevent flow in the direction from SV2 to SV3.
  • a refrigerant gas contamination detection circuit 100 is included in the system in a parallel fluid flow arrangement with the compressor 44.
  • the contamination detection circuit 100 includes an inlet conduit 102 in fluid communication with the conduit 56 extending from the oil separator 52 to the condenser inlet 58.
  • the inlet conduit 102 has an electrically actuated solenoid valve SV6 disposed there along and from there passes to the inlet of a sampling tube holder 104.
  • the outlet of the sampling tube holder 104 is interconnected via conduit 106 with the conduit 40 which communicates with the suction port 42 of the compressor.
  • An electrically controlled solenoid valve SV5 is disposed in the conduit 106.
  • the solenoid valves SV5 and SV6 when closed, isolate the sampling tube holder 104 from the system and allow easy replacement of the sampling tube contained therein.
  • the sampling tube holder may be of the type described in U. S. Patent 4,389,372 Portable Holder Assembly for Gas Detection Tube.
  • the refrigerant contaminant testing system is preferably of the type shown and described in detail in U. S. Patent 4,923,806 entitled Method and Apparatus For Refrigerant Testing In A Closed System and assigned to the assignee of the present invention.
  • Each of the above identified patents is hereby incorporated herein by reference in its entirety.
  • Automatic control of all of the components of the refrigerant recovery system 10 is carried out by an electronic controller 108 which is formed of a micro-processor having a memory storage capability and which is micro-programmable to control the operation of all of the solenoid valves SV1 through SV7 as well as the compressor motor and the condenser fan motor.
  • Inputs to the controller 108 include a number of measured or sensed system control parameters.
  • these control parameters include the temperature of the storage cylinder Tstor which comprises a temperature transducer capable of accurately providing a signal indicative of the temperature of the refrigerant in the storage cylinder 86.
  • Ambient temperature is measured by a temperature transducer positioned at the inlet to the condenser coil or condenser fan 62 and is referred to as Tamb.
  • the temperature of the refrigerant flowing through the compressor discharge line 50 is sensed by a temperature transducer 110 positioned on the compressor discharge line 50.
  • a pressure transducer labeled P2 is in fluid flow communication with the suction line 40 to the compressor while a second pressure transducer P3 is in fluid communication with the high pressure refrigerant line 56 passing to the condenser.
  • the pressure ratio across the compressor 44 is defined as the ratio P3/P2.
  • An additional input to the controller 108 is the signal from the liquid level indicator 92.
  • FIG. 10 it will be noted that the operating modes of the system are identified and the condition of the electrically actuatable components of the system are shown in the different modes.
  • the Standby mode the system has been turned on and all electrically actuatable mechanical systems are de-energized and ready for operation.
  • the electrically actuated solenoid valves SV1 through SV4 are all open thereby equalizing the pressures within the system so that it may be serviced without fear of encountering high pressure refrigerant.
  • the recovery and purification system 10 is capable of operating in both liquid recovery and vapor recovery modes. It should be appreciated that a vapor recovery cycle may begin under two different sets of circumstances: 1) in the case of a system containing more than 2.27 Kg of refrigerant the vapor recovery cycle will follow a previously performed liquid recovery cycle; and 2) in the case of a refrigeration system containing less than 2.27 Kg of refrigerant the vapor recover cycle represents the initiation of the recovery sequence.
  • the Recover mode is the mode in which the device 10 has been coupled to an air conditioning system 12 for removal of refrigerant therefrom.
  • the first step performed by the controller 108 when the Recover cycle is selected is to compare the compressor discharge pressure P3 to the compressor inlet pressure P2. If the pressure differential (P3-P2) is greater than 206.92 KN/m2 the controller 108 will open valves SV1-SV4 in order to equalize the pressures within the system. When the difference between P3 and P2 falls to less than 68.98 KN/m2 the system will then go to the Recover mode of operation.
  • valve SV2 Upon initiation of the Recover mode the controller 108 will open valves SV2, SV3 and SV4, valve SV1 will remain closed. Valves SV5 and SV6 as noted in Figure 4 operate together as a single output from the micro-processor (controller) and the only time these valves are opened is when the contaminant testing process is being carried out. These valves will not be discussed further in connection with the other modes of operation of the system.
  • the compressor 44 and the condenser fan 62 are also actuated upon initiation of the Recover mode.
  • valve SV3 open refrigerant from the system being serviced 12 is forced by the pressure of the refrigerant in the system, and by the suction created by operation of the compressor 44, through conduit 20, through valve SV3, check valve 98, valve SV2 and conduit 30 to the accumulator/oil trap 32.
  • the oil contained in the refrigerant being removed from the system being serviced falls to the bottom of the trap along with any liquid refrigerant withdrawn from the system.
  • Gaseous refrigerant is drawn from the accumulator/oil trap 32 through the filter dryer 38 where moisture, acid and any particulate matter is removed therefrom, and, from there passes via conduit 40, through the suction accumulator 46 to the compressor 44.
  • the compressor 44 compresses the low pressure gaseous refrigerant entering the compressor into a high pressure gaseous refrigerant which is delivered via conduit 50 to the oil separator 52.
  • the oil separated from the high pressure gaseous refrigerant in the separator 52 is the oil from the recovery compressor 44 and this oil is returned via conduit 54 to the suction line 40 of the compressor to assure lubrication of the compressor.
  • From the oil separator 52 the high pressure gaseous refrigerant passes via conduit 56 to the condenser coil 60 where the hot compressed gas condenses to a liquid.
  • Liquified refrigerant leaves the condensing coil 60 via conduit 66 and passes through the T68 through the open solenoid valve SV4, and passes via the liquid lines 80 and 82, to the refrigerant storage cylinder 86 through liquid inlet port 84.
  • While refrigerant recovery is going on the controller 108 is receiving signals from the pressure transducers P3 and P2, calculating the pressure ratio P3/P2, and, comparing the calculated ratio to a predetermined value.
  • Compressor suction pressure P2 is also being looked at alone and being compared to a predetermined Recovery Termination Suction Pressure. As shown in Figure 2, the predetermined Recovery Termination Suction Pressure is 27.59 KN/m2, and P2 falls below this value the Recover mode is terminated and the controller 108 initiates the refrigerant quality test cycle, identified as Totaltest. This cycle will be described below following a complete description of the other modes of operation.
  • Totaltest is a registered Trademark of Carrier Corporation for "Testers For Contaminants in A Refrigerant".
  • the selection of the predetermined recovery termination suction pressure of 27.59 KN/m2 results from recovery system operation wherein it has been shown that a compressor suction pressure, P2, of 27.59 KN/m2 or less results in recovery of 98 to 99% of the refrigerant from the system being serviced. Achieving this pressure during the first Recover mode cycle is unusual, however, it is achievable.
  • P2 may be drawn down to the 27.59 KN/m2 termination value in low ambient temperature conditions where the condensing coil temperature (which is ambient air cooled) is low enough to allow P3 to remain low enough for P2 to reach 27.59 KN/m2 before the pressure ratio limit is reached.
  • the microprocessor in the controller 1C8 performs what is referred to as the Recovery Cycle Test. If the Recovery Cycle just performed is the first Recovery Cycle performed and the compressor suction pressure P2 is greater than or equal to 68.98 KN/m2 the system will shift to what is known as a Cylinder Cool mode of operation. If the Recovery Cycle just performed is a second or subsequent recovery cycle and the compressor suction pressure P2 is less than 68.98 KN/m2 the controller will consider the refrigerant Recovery as completed and will initiate the refrigerant contaminant test cycle (Totaltest).
  • the latter conditions are conditions that are found to exist at high ambient temperatures. For example, such conditions may exist when recovering R-22 from an air conditioning system at an ambient temperature of 40.6 °C and above. Under such conditions it has been found that attempts to reduce the compressor suction pressure P2 to values less than 68.98 KN/m2 are counterproductive in that a substantial length of operating time would be necessary in order to obtain a very small additional drop in suction pressure.
  • the controller 108 will initiate the Cylinder Cool mode of operation.
  • the solenoid valves SV1 and SV2 are energized and thereby in the open condition.
  • Solenoid valves SV3 and SV4 are closed, and, the compressor motor and condenser fan motor continue to be energized.
  • the Cylinder Cool mode of operation essentially converts the system to a closed cycle refrigeration system wherein the refrigerant storage cylinder 86 functions as a flooded evaporator. By closing solenoid valve SV3 the refrigerant recovery and purification system 10 is isolated from the refrigeration system 12 being serviced.
  • solenoid valve SV1 establishes a fluid path between the vapor outlet 88 of the storage cylinder 86 and the conduit 28 which is in communication with the low pressure side of the compressor 44.
  • the closing of solenoid valve SV4 routes the refrigerant passing from the condenser 60 through the refrigerant expansion device 74.
  • the compressor 44 compresses low pressure gaseous refrigerant entering the compressor and delivers a high pressure gaseous refrigerant via conduit 50 to the oil separator 52. From the oil separator 52 the high pressure gaseous refrigerant passes via conduit 56 to the condenser coil 60 where the hot compressed gas condenses to a liquid. Liquified refrigerant leaves the condensing coil 60 via conduit 66 and passes through the T-connection 68 through the strainer 76 and, via conduit 72, to the refrigerant expansion device 74.
  • the thus condensed refrigerant flows through the expansion device 74 where the refrigerant undergoes a pressure drop, and is at least partially, flashed to a vapor.
  • the liquid-vapor mixture then flows via conduits 78 and 82 to the refrigerant storage cylinder 86 where it evaporates and absorbs heat from the refrigerant within the cylinder 86 thereby cooling the refrigerant.
  • Low pressure refrigerant vapor then passes from the storage cylinder 86, via vapor outlet port 88, through conduit 94 and solenoid valve SV1 to the T connection 96. From there it passes through the check valve 98, solenoid valve SV2, oil separator/accumulator 32, filter dryer 38 and conduit 40 to return to the compressor 44, to complete the circuit.
  • the cylinder temperature As the Cylinder Cool mode of operation continues, the cylinder temperature, as measured by the temperature transducer Tstor, continues to drop as the refrigerant is continuously circulated through the closed refrigeration circuit. Also during this time the refrigerant is passed through the refrigeration purifying components, i.e. the oil separator 32 and the filter dryer 38, a plurality of times to thereby further purify the refrigerant.
  • the refrigeration purifying components i.e. the oil separator 32 and the filter dryer 38
  • the Cylinder Cool mode of operation will terminate when any one of three conditions occur; 1) the cylinder temperature, as measured by Tstor falls to a level 38.9 °C below ambient temperature (Tamb), or, 2) when the Cylinder Cooling mode of operation has gone on for a duration of 15 minutes, or, 3) when the cylinder temperature Tstor falls to -17.8°C.
  • Tamb ambient temperature
  • the result is substantially the same, i.e., the temperature (Tstor) of the refrigerant stored in the cylinder 86 is now well below ambient temperature.
  • the pressure within the cylinder, corresponding to the lowered temperature is substantially lower than any other point in the system.
  • the controller 108 will shift the system to a second Recover mode of operation.
  • the solenoid valves, and compressor and condenser motors are energized as described above in connection with the first Recover mode. Because of the low temperature Tstor that has been created in the refrigerant storage cylinder, however, the capability of the system to withdraw refrigerant from the unit being serviced, without subjecting the recovery compressor to high pressure differentials is dramatically increased.
  • the system will then operate as described until conditions exist which result in the controller 108 switching to the refrigerant contaminant test (Totaltest) mode of operation.
  • Totaltest refrigerant contaminant test
  • an operator should make sure that a sampling tube has been placed in the sampling tube holder 104.
  • solenoid valves SV1, SV2, SV4 and SV5/SV6 are all energized to an open position.
  • the solenoid valve SV3 is not energized and is therefore closed.
  • the flow of refrigerant through the recovery system is similar to that described above in connection with the Cylinder Cooling mode except that the solenoid valve SV4 is open and therefore the refrigerant does not pass through the expansion device 74.
  • the solenoid valves SV5 and SV6 open, the pressure differential existing between the high and low pressure side of the system induces a flow of refrigerant through conduit 102 solenoid valve SV6, the sampling tube holder 104 (and the tube contained therein), solenoid valve SV5 and conduit 106 to thereby return the refrigerant being tested to the suction side of the compressor 44.
  • a suitable orifice is provided in conduit 102, or in the sampling tube holder 104, to provide the necessary pressure drop to assure that the flow of refrigerant through the testing tube held in the sampling tube holder 104 is at a rate that will assure that the testing tube will receive the proper flow of refrigerant therethrough during the Totaltest run time in order to assure a reliable test of the quality of the refrigerant passing therethrough.
  • the run time of the refrigerant quality test is indicated as X minutes.
  • the normal run time for a commercially available Totaltest system is about ten minutes and the controller may be programmed to run the test for that length of time or different time for different refrigerants.
  • the quality test however may be terminated sooner if the refrigerant being tested contains a large amount of acid and the indicator in the test tube changes color in less than the programmed run time. If this occurs, the refrigerant quality test may be terminated, and, an additional refrigerant purification cycle initiated.
  • the additional purification cycle is identified as the Recycle mode and a flow chart showing the system operating logic is shown in Figure 3.
  • the condition of the electrically actuable components is the same in Recycle as it is for the Cylinder Cool mode except that the solenoid valve SV4 is open so that the refrigerant does not flow through the expansion device 74 but flows through the open solenoid valve SV4. This increases the volume flow of refrigerant through the system during the Recycle mode.
  • the function of this mode is strictly to further purify the refrigerant by multiple passes through the oil trap 32 and the filter dryer 38.
  • the length of time in which the system is run in the Recycle mode is determined by the operator as a number of minutes "X" which varies as a function of refrigerant type and quality and ambient air temperature.
  • the type of refrigerant is known, the ambient temperature may be measured, and the quality is determined by the operator upon the evaluation of the test tube used in the refrigerant quality test cycle.
  • the system upon the end of the selected recycle time the system, if so selected by the operator, will run another refrigerant quality test, and, if the results of this test so indicate another recycle period may initiated following the procedure set forth above.
  • the object of the system and control scheme described above is to remove as much refrigerant as possible from a system being serviced, under any given ambient conditions, or system conditions, while, at all times monitoring system control parameters which will assure that the compressor of the Recovery system is not subjected to adverse operating conditions.
  • the system control parameter is the pressure ratio P3/P2, across the recovery compressor 44.
  • P3/P2 the pressure ratio above which the compressor could be adversely affected. It should be appreciated that for different compressors the value of this parameter could be different.
  • the ultimate goal in the control of this system is to limit compressor operation to predetermined limits to assure long and reliable compressor life.
  • the internal compressor temperature is considered by compressor experts to be the controlling factor in preventing internal compressor damage during operation.
  • the pressure ratio has been found to be an extremely reliable effective control parameter which may be related to the internal compressor temperature and has thus been selected as the preferred control parameter in the above described preferred embodiment.
  • Pressure differential (i.e. P3-P2) could also be effectively used to control the system.
  • an internal compressor temperature at which the lubricating oil begins to break down is about 162.8 °C. Above this temperature adverse compressor operation and damage may be expected.
  • the controller 108 has been programmed such that, should the compressor discharge temperature, monitored by the temperature transducer 110 exceed a maximum of 107.2 °C regardless of pressure ratio conditions, the system will be shut off.
  • the system control parameter being sensed for compressor protection could be the compressor suction pressure P2.
  • the microprocessor of the controller 108 would be programmed with compressor suction pressures P2 which would be considered indicative of adverse compressor operation, for a range of ambient air temperatures and for the different refrigerants which may be processed by the system.
  • a suction pressure P2 in the range of 89.66 KN/m2 to 103.46 KN/m2 would be programmed to change the system from a Recover mode to a Cylinder Cooling mode of operation.
  • the outstanding refrigerant recovery capability of a system according to the present invention is reflected in the following example.
  • the recovery apparatus was connected to a refrigeration system having a system charge of 2.04 Kg of refrigerant R-12 at an ambient temperature of 38.9 °C.
  • a refrigeration system having a system charge of 2.04 Kg of refrigerant R-12 at an ambient temperature of 38.9 °C.
  • Such a system is typical of an automobile air conditioning system.
  • the storage cylinder 86 contains clean refrigerant which may be returned to the refrigeration system.
  • the Recharge mode when selected, results in simultaneous opening of valves SV1 and SV3 to establish a direct refrigerant path from the storage cylinder 86 to the refrigeration system 12. All other valves and the compressor and condenser are de-energized in this mode.
  • the amount of refrigerant to be delivered to the system is selected by the operator, and, the controller 108, with input from the liquid level sensor 92 will assure accurate recharge of the selected quantity of refrigerant to the system.
  • liquid recovery mode will now be described in detail in connection with the flow chart of figure 4A. It should be appreciated that the liquid recovery mode is designed to be used in larger systems for example systems having a refrigerant charge of greater than 2.27 Kg of refrigerant. In systems where less than 2.27 Kg of refrigerant are contained in the system the liquid recover mode of operation may be omitted and the operator may go directly to the previously described vapor recovery mode which will be subsequently described.
  • valves SV1, SV2 and SV7 upon initiation of the Liquid Recover mode the controller 108 will open valves SV1, SV2 and SV7.
  • the valves SV3, SV4, SV5 and SV6 will remain closed.
  • Valves SV5 and SV6 as noted in Figure 10 operate together as a single output from the microprocessor (controller 108) and the only time these valves are open is when the contaminant testing process is being carried out. These valves will not be discussed further in connection with other modes of operation of the system.
  • the motors of the compressor 44 and the condenser fan 62 are also energized upon initiating the liquid recover mode.
  • valve SV3 closed and valve SV7 open refrigerant from the system being serviced 12 is forced by the pressure of the refrigerant in the system through conduit 20, through the T-11, through valve SV7 and via liquid refrigerant line 15 to the valve 90 on the refrigerant storage cylinder 86 and directly into refrigerant storage cylinder.
  • the compressor 44 acts to withdraw low pressure gaseous refrigerant directly from the storage cylinder 86.
  • This refrigerant passes via conduit 94 and T-96. through the check valve 98, valve SV2 and conduit 30 to the oil separator 32. From the oil separator it passes via conduit 36 to the filter drier 38, and thence via conduit 40 and accumulator 46 to the compressor 44 delivers high pressure gaseous refrigerant via conduit 50 to the oil separator 52. From the oil separator 52 the high pressure gaseous refrigerant passes via conduit 56 to the condenser coil 60 where the hot compressed gas condenses to a liquid.
  • Liquified refrigerant leaves the condensing coil 60, via conduit 66 and passes through the T-connection 68 through the strainer 76 and, via conduit 72 to the refrigerant expansion device 74.
  • the thus condensed refrigerant flows through the expansion device 74 where the refrigerant undergoes a pressure drop, and is at least partially flashed to a vapor.
  • the liquid-vapor mixture then flows via conduit 78 and 82 back to the refrigerant storage cylinder 86 where it evaporates and absorbs heat from the refrigerant within the cylinder 86 thereby lowering the pressure and temperature within the storage cylinder 86.
  • the liquid recovery mode is run according to the illustrated embodiment, for two minutes at which time the system is shifted to the Cylinder Cool cycle.
  • the solenoid valve SV7 is closed and the system operates in a closed circuit, as described with no connection to the system being serviced.
  • the Cylinder Cool mode of operation continues the cylinder temperature continues to drop as the refrigerant is continuously circulated through the closed refrigeration circuit.
  • the refrigerant is passed through the refrigeration purifying components, i.e. the oil separator 32 and the filter dryer 38, a plurality of times to thereby further purify the refrigerant.
  • the system is run in the Cylinder Cool cycle for five minutes in order to assure that the temperature and pressure within the storage cylinder is reduced such that it is substantially lower than ambient temperature.
  • the system returns to liquid recovery operation.
  • the controller 108 continues to receive the signal generated by the liquid level sensor 92 which is indicative of the liquid level within the storage cylinder 86.
  • the processor receives a succession of these signals and determines a rate of liquid level increase in the storage cylinder 86.
  • the processor then generates a signal indicative of the rate of liquid level increase.
  • the processor is further programmed to look at the signal indicative of the rate of liquid level increase and determine whether that rate is commensurate with the withdrawal of liquid refrigerant from the system.
  • Figure 5 illustrates the decrease in the rate of refrigerant recovery, and, accordingly, the decrease in the rate of increase of the liquid level within the cylinder 86 which occurs when the recovery of refrigerant shifts from a liquid to a vapor state.
  • the straight line portion of the graph illustrates the linear increase in the amount of refrigerant recovered as time goes by when recovery is in the liquid state.
  • the rate of refrigerant being recovered is in the vapor state.
  • the accuracy of the information which liquid level sensors are able to provide varies widely.
  • the operation of the Liquid Recovery system as described above is such that the system will perform a successful recovery using a level sensor that provides less accurate readings.
  • the Liquid Recovery mode of operation described above, as outlined in Figure 4A may be performed by omitting the first Cylinder Cool cycle and the return to Liquid Recovery cycle.
  • Vapor Recover and Cylinder Cool modes of operation are illustrated in the flow chart of Figure 4B.
  • the operation of the system at this time is the same as the previously described Vapor Recovery and Cylinder Cool cycles and will not be repeated.
  • Figures 6A and B illustrate the operation of the system in the liquid recovery mode where the shift from liquid recovery to vapor recovery is controlled by a parameter which may be correlated to the change of state of the refrigerant being withdrawn. Operation of the system is the same as that described in connection with Figure 4A and B except for the source of the control signals.
  • the controller 108 continues to receive signals related to a number of conditions within the system. Specifically the temperature transducer Tstor provides a signal indicative of the temperature of the refrigerant in the storage cylinder 86.
  • the pressure transducer P2 and P3, provide information with respect to the pressure entering and leaving, respectively the compressor 44. These three parameters will collectively be referred to as system control parameters.
  • FIGS 7, 8 and 9 illustrate the value of the system control parameters Tstor, P3 and P2 respectively as a function of the length of time the liquid recovery cycle has been run.
  • the microprocessor of the controller 108 is programmed to terminate the recovery mode of operation automatically when one of these selected system control parameters falls a predetermined amount below its maximum value.
  • Tstor is the preferred controlled parameter and in the preferred embodiment the termination of liquid recovery occurs when Tstor drops 2.8 °C from its maximum value.
  • the control parameter being P2 or P3 a drop of 34.49 KN/m2 from the maximum value has been found to cause the shift from liquid recovery to vapor recovery to occur at an appropriate time.
  • this Cylinder Cool mode of operation will terminate when any one of three conditions occur; 1) the cylinder temperature, as measured by Tstor falls to a level 38.9 °C below ambient temperature (Tamb), or, 2) when the cylinder cool mode of operation has gone for a duration of 15 minutes, or, 3) when the cylinder temperature Tstor falls to -17.8°C.
  • the result is substantially the same, i.e., the temperature (Tstor) of the refrigerant stored in the cylinder 86 is well below ambient temperature. At this point the system will shift to a vapor recovery mode of operation to complete the withdrawal of the refrigerant from the system being serviced.

Claims (6)

  1. Vorrichtung der Art zur Rückgewinnung kompressiblen Kältemittels von einem Kühlsystem, die aufweist:
    Kompressormittel (44) zur Verdichtung eines dorthin beförderten gasförmigen Kältemittels, wobei die Kompressormittel eine Saugöffnung (42) und eine Austrittsöffnung (48) haben,
    erste Leitungsmittel (20, 30, 36, 40), um das Kühlsystem mit der Saugöffnung der Kompressormittel zu verbinden,
    Kondensatormittel (60), um Kältemittel hindurchzuführen, wobei die Kondensatormittel einen Einlaß (58) und einen Auslaß (64) haben,
    zweite Leitungsmittel (54, 56), um die Austrittsöffnung der Kompressormittel mit dem Einlaß der Kondensatormittel zu verbinden,
    Mittel zur Speicherung von Kältemittel (86),
    dritte Leitungsmittel (66, 82), um den Auslaß der Kondensatormittel mit den Mitteln zur Speicherung von Kältemittel zu verbinden,
    vierte Leitungsmittel (94), um die Mittel zur Speicherung von Kältemittel mit den ersten Leitungsmitteln zu verbinden,
    erste Ventilmittel (SV3), betreibbar zwischen offenen und geschlossenen Zuständen und in den ersten Leitungsmitteln in Stromrichtung oberhalb von der Verbindung der vierten Leitungsmittel mit den ersten Leitungsmitteln angeordnet,
    zweite Ventilmittel (SV4), betreibbar zwischen einem offenen Zustand und einem Kältemittelexpansionszustand und in den dritten Leitungsmitteln angeordnet,
    dritte Ventilmittel (SV1), betreibbar zwischen offenen und geschlossenen Zuständen und in den vierten Leitungsmitteln angeordnet,
    Mittel zum Abtasten eines Systemsteuerungsparameters (110, P2, P3), der in Zusammenhang mit dem Schutz des Kompressors steht, und zur Bereitstellung eines Signals, das einen Wert hat, der den abgetasteten Systemsteuerungsparameter kennzeichnet,
    und Prozessormittel (108), um das von den Abtastmitteln bereitgestellte Signal zu empfangen, und um die ersten Ventilmittel (SV3) in einen offenen Zustand, die zweiten Ventilmittel (SV4) in einen offenen Zustand, und die dritten Ventilmittel (SV1) in einen geschlossenen Zustand zu bringen, entsprechend dem Signal mit einem Wert innerhalb eines vorbestimmten Bereichs, in dem der Kompressor nicht nachteilig beeinflusst wird, und um die ersten Ventilmittel (SV3) in einen geschlossenen Zustand, die zweiten Ventilmittel (SV4) in einen Kältemittelexpansionszustand und die dritten Ventilmittel (SV1) in einen offenen Zustand zu bringen, entsprechend dem Signal mit einem Wert innerhalb eines vorbestimmten Bereichs, in dem der Kompressor nachteilig beeinflusst wird.
  2. Vorrichtung nach Anspruch 1, in der die Mittel zum Abtasten eines Systemsteuerungsparameters aufweisen:
    ein erstes Druckumwandlungsmittel (P2), um den Druck des in den Kompressor (44) eintretenden Kältemittels abzutasten und um ein erstes, diesen Druck kennzeichnendes Drucksignal bereitzustellen,
    und ein zweites Druckumwandlungsmittel (P3), um den Druck des den Kompressor verlassenden Kältemittels abzutasten und um ein zweites, diesen Druck kennzeichnendes Drucksignal bereitzustellen,
    Mittel, um das erste Drucksignal und das zweite Drucksignal zu verarbeiten, um das Druckverhältnis über den Kompressor zu bestimmen und das Signal bereitzustellen, das einen Wert hat, der den Systemsteuerungsparameter kennzeichnet, wobei der abgetastete Systemsteuerungsparameter das Kompressordruckverhältnis ist.
  3. Vorrichtung nach Anspruch 1, die aufweist:
    Mittel zur Reinigung (32, 38) des Kältemittels, das durch die ersten Leitungsmittel von dem Kühlsystem zu den Kompressormitteln geht,
    fünfte Leitungsmittel (102), die an einem Ende mit den zweiten Leitungsmitteln in Fließverbindung stehen, um hiervon das Abziehen einer Menge Kältemittels zu ermöglichen,
    sechste Leitungsmittel (106), die an einem Ende mit den ersten Leitungsmitteln in Fließverbindung stehen, in Stromrichtung abwärts von den Mitteln zur Reinigung,
    Mittel (104), um das Betreiben einer Prüfröhre für die Kältemittelreinheit in einer geschlossenen Strömungsverbindung mit den anderen Enden der fünften (102) und sechsten (106) Leitungsmittel zu unterstützen, um dadurch eine Strömungsverbindung zwischen diesen einzurichten,
    vierte Ventilmittel (SV6), betreibbar zwischen einem offenem und einem geschlossenem Zustand, in den fünften Leitungsmitteln angeordnet,
    fünfte Ventilmittel (SV5), betreibbar zwischen offenen und geschlossenen Zuständen und in den sechsten Leitungsmitteln angeordnet,
    Mittel (108), um den Kompressor zu betätigen und die ersten Ventilmittel (SV3) in einen offenen Zustand zu bringen und die vierten, fünften und dritten Ventilmittel (SV6, SV5, SV1) in einen geschlossenen Zustand zu bringen und dadurch das System in einem Kältemittelrückgewinnungsmodus zu betreiben,
    Mittel (108), um den Kompressor (44) zu betätigen und die ersten Ventilmittel (SV3) in eine geschlossene Position, die vierten Ventilmittel (SV6) in eine geschlossene Position, die fünften Ventilmittel (SV5) in eine geschlossene Position und die dritten Ventilmittel (SV1) in eine offene Position zu bringen, um dadurch einen geschlossenen Kältemittelzirkulationsweg festzulegen, der einen Kältemittelreinigungsbetriebsmodus festlegt,
    Mittel (108), um den Kompressor (44) zu betätigen und die ersten Ventilmittel (SV3) in eine geschlossene Position zu bringen, die dritten Ventilmittel (SV1) in eine offene Position zu bringen, die vierten Ventilmittel (SV6) in eine offene Position zu bringen und die fünften Ventilmittel (SV5) in eine offene Position zu bringen, um dadurch einen Kältemittelkreislauf festzulegen, bei dem Kältemittel in einem Kältemittelqualitätstestbetriebsmodus durch die Kältemittelreinheitsprüfröhre geführt wird.
  4. Vorrichtung nach Anspruch 1, die weiterhin aufweist:
    siebte Leitungsmittel (15), um das Kühlsystem (12) mit den Mitteln zur Speicherung von Kältemittel (86) zu verbinden,
    sechste Ventilmittel (SV7), betreibbar zwischen offenen und geschlossenen Zuständen und in den siebten Leitungsmitteln (15) angeordnet,
    wobei die siebten Leitungsmittel (15) einen Kältemittelweg von dem Kühlsystem (12) direkt zu den Mitteln zur Speicherung von Kältemittel (86) festlegen,
    wobei, wenn die ersten Ventilmittel (SV3) geschlossen sind und sowohl die dritten Ventilmittel (SV1) und die sechsten Ventilmittel (SV7) offen sind, Kältemittel von den Mitteln zur Speicherung von Kältemittel (86) durch die vierten und ersten Leitungsmittel (94, 30, 40), durch die Kompressormittel (44), durch die zweiten Leitungsmittel (54, 56), durch die Kondensatormittel (60), durch die dritten Leitungsmittel (66, 82) und die darin angeordneten Expansionsmittel (74) zurück zu den Mitteln zur Speicherung von Kältemittel (86) fließt und einen Kühlkreislauf festlegt, der die Temperatur und den Druck innerhalb der Mittel zur Speicherung von Kältemittel (86) verringert und dadurch den Fluß des Kältemittels von dem Kühlsystem (12) durch die ersten Leitungsmittel zu den Mitteln zur Speicherung von Kältemittel fördert,
    und wobei, wenn sowohl die ersten Ventilmittel (SV3) als auch die sechsten Ventilmittel (SV7) geschlossen sind und die dritten Ventilmittel (SV1) offen sind, die Vorrichtung zur Rückgewinnung von dem Kühlsystem (12) isoliert sein wird, und der Kühlkreislauf in einem geschlossenen Kreislauf arbeiten wird, um die Temperatur und den Druck innerhalb der Vorrichtung zur Rückgewinnung zu verringern.
  5. Vorrichtung nach Anspruch 4, die weiter aufweist:
    Mittel zum Abtasten des Flüssigkeitsspiegels (92) in den Mitteln zur Speicherung von Kältemittel (86) und zur Erzeugung eines den Flüssigkeitsspiegel in den Mitteln zur Speicherung von Kältemittel kennzeichnenden Signals,
    Prozessormittel (108), um eine Folge der Signale zu empfangen, die den Flüssigkeitsspiegel kennzeichnen, und um ein Maß des Ansteigens des Flüssigkeitsspiegels in den Mitteln zur Speicherung von Kältemittel zu bestimmen und um ein Signal zu erzeugen, das das Maß des Ansteigens des Flüssigkeitsspiegels kennzeichnet,
    Prozessormittel (108), um das Signal zu empfangen, das das Maß des Ansteigens des Flüssigkeitsspiegels kennzeichnet, und um die sechsten Ventilmittel (SV7) in einen offenen Zustand und die ersten Ventilmittel (SV3) in einen geschlossenen Zustand zu bringen, entsprechend dem Maß des Ansteigens des Flüssigkeitsspiegels, das einen vorbestimmten Wert des Maßes des Ansteigens des Flüssigkeitsspiegels übersteigt, der kennzeichnend für die Rückgewinnung von flüssigem Kältemittel von dem Kühlsystem (12) ist, und um die sechsten Ventilmittel (SV7) in einen geschlossenen Zustand und die ersten Ventilmittel (SV3) in einen offenen Zustand zu bringen, entsprechend dem Signal, das das Maß des Ansteigens des Flüssigkeitsspiegels kennzeichnet, das unter den vorbestimmten Wert des Maßes des Flüssigkeitsspiegels fällt, der kennzeichnend für die Rückgewinnung von Flüssigkeit von dem Kühlsystem ist.
  6. Vorrichtung nach Anspruch 4, die weiter aufweist:
    Mittel zum Abtasten eines Systemsteuerparameters (P2, P3, Tstor), der eine erkennbare Wertänderung hat, die zu einem Zeitpunkt auftritt, der mit dem Zeitpunkt in Verbindung gebracht werden kann, an dem sich der Zustand des Kältemittels, das aus dem Kühlsystem (12) abgezogen wird, sich von flüssig zu dampfförmig ändert, und um ein Signal bereitzustellen, das anzeigt, daß die erkennbare Änderung aufgetreten ist,
    Mittel (108), um die sechsten Ventilmittel (SV7) in eine offene Position und die ersten Ventilmittel (SV3) in eine geschlossene Position zu bringen, wodurch die Vorrichtung betrieben wird, um flüssiges Kältemittel von dem Kühlsystem durch die siebte Leitung abzuziehen,
    und um die sechsten Ventilmittel (SV7) in eine geschlossene Position und die ersten Ventilmittel (SV3) in eine offene Position zu bringen, um gasförmiges Kältemittel von dem Kühlsystem durch die erste Leitung abzuziehen, entsprechend dem Signal, das anzeigt, daß die erkennbare Änderung aufgetreten ist.
EP91118875A 1990-11-13 1991-11-06 Vorrichtung für Rückgewinnung und Reinigung von Kältemittel Expired - Lifetime EP0485873B1 (de)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
US61263890A 1990-11-13 1990-11-13
US61264290A 1990-11-13 1990-11-13
US612638 1990-11-13
US07/612,643 US5127232A (en) 1990-11-13 1990-11-13 Method and apparatus for recovering and purifying refrigerant
US612641 1990-11-13
US612643 1990-11-13
US612642 1990-11-13
US07/612,641 US5174124A (en) 1990-11-13 1990-11-13 Apparatus for sampling the purity of refrigerant flowing through a refrigeration circuit

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EP0485873A1 EP0485873A1 (de) 1992-05-20
EP0485873B1 true EP0485873B1 (de) 1994-05-11

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US5146761A (en) * 1991-06-17 1992-09-15 Carrier Corporation Method and apparatus for recovering refrigerant
US5146760A (en) * 1991-06-17 1992-09-15 Carrier Corporation Method and apparatus for compressor protection in a refrigerant recovery system
US5181390A (en) * 1992-01-02 1993-01-26 Cavanaugh Wayne B Manually operated refrigerant recovery apparatus
FR2758998B1 (fr) * 1997-02-05 1999-04-02 Dehon Sa Anciens Etablissement Procede de regeneration d'un fluide pollue et installation pour la mise en oeuvre du procede
JP4538980B2 (ja) * 2001-04-20 2010-09-08 三菱電機株式会社 冷媒回収装置および回収方法
JP2002350014A (ja) * 2001-05-22 2002-12-04 Daikin Ind Ltd 冷凍装置
CN111829217A (zh) * 2020-08-04 2020-10-27 北京美德瑞科技有限公司 冷媒回收机推拉回收与正常回收自动转换系统
CN112856864B (zh) * 2021-01-16 2023-07-21 北海职业学院 一种制冷剂净化系统
CN114215734B (zh) * 2021-11-05 2024-03-19 合肥通用机械研究院有限公司 一种压缩机测试装置用低压工质完全回收系统及回收方法

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US4285206A (en) * 1979-02-05 1981-08-25 Draf Tool Co., Inc. Automatic refrigerant recovery, purification and recharge apparatus
US4441330A (en) * 1980-12-01 1984-04-10 Robinair Manufacturing Corporation Refrigerant recovery and recharging system
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US4646527A (en) * 1985-10-22 1987-03-03 Taylor Shelton E Refrigerant recovery and purification system
AU2825589A (en) * 1988-06-24 1990-01-12 Murray Corporation Method and apparatus for full evacuation of air conditioner or refrigeration system
JPH076710B2 (ja) * 1989-01-30 1995-01-30 ダイキン工業株式会社 冷媒回収装置
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US4981020A (en) * 1990-02-02 1991-01-01 Scuderi Carmelo J Apparatus for recovering refrigerant

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DE69101964D1 (de) 1994-06-16
JPH04268178A (ja) 1992-09-24
CA2053929C (en) 1994-05-03
KR950014471B1 (ko) 1995-11-28
EP0485873A1 (de) 1992-05-20
AU650919B2 (en) 1994-07-07
KR920010231A (ko) 1992-06-26
AU8778691A (en) 1992-05-14
ES2053261T3 (es) 1994-07-16
CA2053929A1 (en) 1992-05-14
DE69101964T2 (de) 1994-12-15

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