US20090175748A1 - Multi-stage compressor unit for refrigeration system - Google Patents

Multi-stage compressor unit for refrigeration system Download PDF

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Publication number
US20090175748A1
US20090175748A1 US12/308,016 US30801608A US2009175748A1 US 20090175748 A1 US20090175748 A1 US 20090175748A1 US 30801608 A US30801608 A US 30801608A US 2009175748 A1 US2009175748 A1 US 2009175748A1
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unit
refrigerant
stage
compressor
sub
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James W. Bush
Wayne P. Beagle
Biswajit Mitra
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Carrier Corp
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Carrier Corp
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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers

Definitions

  • the present invention relates generally to compressors used in refrigeration systems. More particularly, the present invention relates to a multi-stage compressor unit for a refrigeration system that includes at least one two-stage compressor sub-unit.
  • a typical refrigeration system includes an evaporator, a compressor, a condenser, and a throttle valve.
  • a refrigerant such as a hydrofluorocarbon (HFC) typically enters the evaporator as a two-phase liquid-vapor mixture.
  • HFC hydrofluorocarbon
  • the liquid portion of the refrigerant changes phase from liquid to vapor as a result of heat transfer into the refrigerant.
  • the refrigerant is then compressed within the compressor, thereby increasing the pressure of the refrigerant.
  • the refrigerant passes through the condenser, where it changes phase from a vapor to a liquid as it cools within the condenser.
  • the refrigerant expands as it flows through the throttle valve, which results in a decrease in pressure and a change in phase from a liquid to a two-phase liquid-vapor mixture.
  • the present invention is a multi-stage compressor unit for a refrigeration system configured to circulate a refrigerant.
  • the multi-stage compressor unit comprises a first compressor sub-unit having a first stage and a second stage, and a second compressor sub-unit in parallel with the first compressor sub-unit and having a first stage.
  • the first and second stages of the first compressor sub-unit each have a suction port and a discharge port.
  • the first compressor sub-unit is configured to receive and compress a first portion of the refrigerant from an evaporator.
  • the first stage of the second compressor sub-unit has a suction port and a discharge port.
  • the second compressor sub-unit is configured to compress a second portion of the refrigerant
  • FIG. 1A illustrates a schematic diagram of a first alternative embodiment of a multi-stage compressor unit connected to a refrigeration system.
  • FIG. 1B illustrates a graph relating enthalpy to pressure for the refrigeration system of FIG. 1A .
  • FIG. 2A illustrates a schematic diagram of a second alternative embodiment of a multi-stage compressor unit connected to a refrigeration system.
  • FIG. 2B illustrates a graph relating enthalpy to pressure for the refrigeration system of FIG. 2A .
  • FIG. 3A illustrates a schematic diagram of a third alternative embodiment of a multi-stage compressor unit connected to a refrigeration system.
  • FIG. 3B illustrates a graph relating enthalpy to pressure for the refrigeration system of FIG. 3A .
  • FIG. 4A illustrates a schematic diagram of a fourth alternative embodiment of a multi-stage compressor unit connected to a refrigeration system.
  • FIG. 4B illustrates a graph relating enthalpy to pressure for the refrigeration system of FIG. 4A .
  • FIG. 5A illustrates a schematic diagram of a fifth alternative embodiment of a multi-stage compressor unit connected to a refrigeration system.
  • FIG. 5B illustrates a graph relating enthalpy to pressure for the refrigeration system of FIG. 5A .
  • FIG. 6A illustrates a schematic diagram of a sixth alternative embodiment of a multi-stage compressor unit connected to a refrigeration system.
  • FIG. 6B illustrates a graph relating enthalpy to pressure for the refrigeration system of FIG. 6A .
  • FIG. 1A illustrates a schematic diagram of multi-stage compressor unit 10 A connected to refrigeration system 20 A, which includes heat rejecting heat exchanger 24 , first economizer circuit 25 A, main expansion valve 26 , evaporator 27 , and sensor 31 .
  • First economizer circuit 25 A includes first economizer heat exchanger 28 A, expansion valve 30 A, and sensor 31 A.
  • first economizer heat exchanger 28 A is depicted as a parallel flow tube-in-tube heat exchanger
  • multi-stage compressor unit 10 A is useful in refrigeration systems utilizing other types of economizer heat exchangers including, but not limited to, counter flow tube-in-tube heat exchangers, shell-in-tube heat exchangers, flash tanks, and brazed plate heat exchangers.
  • Multi-stage compressor unit 10 A includes two-stage compressor sub-unit 32 and single-stage compressor sub-unit 34 .
  • two-stage compressor sub-unit 32 is a reciprocating compressor and includes cylinders 36 A and 36 B connected in series.
  • single-stage compressor sub-unit 34 is also a reciprocating compressor and includes cylinder 36 C.
  • two-stage compressor sub-unit 32 and single-stage compressor sub-unit 34 are shown as reciprocating compressors, other types of compressors (in various combinations) may be used including, but not limited to, scroll, screw, rotary vane, standing vane, variable speed, hermetically sealed, and open drive compressors.
  • embodiments of the present invention will be described as including reciprocating-type compressor units having multiple stages represented by compression cylinders.
  • a main refrigerant path is created by a loop defined by the points 1 , 2 , 3 , 4 , and 5 .
  • a first economized refrigerant path is created by a loop defined by the points 4 A, 5 A, 6 A, and 7 A. It should be understood that the paths are all closed paths that allow for continuous flow of refrigerant through refrigeration system 20 A.
  • Refrigerant from path 40 A is then throttled in main expansion valve 26 .
  • Main expansion valve 26 along with economizer expansion valve 30 A, is preferably a thermal expansion valve (TXV) or an electronic expansion valve (EXV).
  • TXV thermal expansion valve
  • EXV electronic expansion valve
  • the refrigerant is a two-phase liquid-vapor mixture and is directed toward evaporator 27 .
  • the refrigerant enters two-stage compressor sub-unit 32 through suction port 37 .
  • the refrigerant is compressed within cylinder 36 A, which is the first stage of two-stage compressor sub-unit 32 , and is then directed out discharge port 50 (point 2 ).
  • the refrigerant is discharged through discharge port 39 (point 3 ).
  • the first economized path continues along path 42 A.
  • the refrigerant is throttled to a lower pressure by economizer expansion valve 30 A (point 5 A) prior to flowing through first economizer heat exchanger 28 A.
  • the refrigerant from path 42 A that flowed through first economizer heat exchanger 28 A (point 6 A) is then directed along economizer return path 46 A and injected into suction port 52 of single-stage compressor sub-unit 34 for compression in single-stage compressor sub-unit 34 .
  • refrigerant is discharged through discharge port 54 (point 7 A) where it merges with the refrigerant discharged from two-stage compressor sub-unit 32 .
  • Refrigeration system 20 A also includes sensor 31 disposed between evaporator 27 and multi-stage compressor unit 10 A along the main refrigerant path.
  • sensor 31 acts with expansion valve 26 to sense the temperature of the refrigerant leaving evaporator 27 and the pressure of the refrigerant in evaporator 27 to regulate the flow of refrigerant into evaporator 27 to keep the combination of temperature and pressure within some specified bounds.
  • expansion valve 26 is an electronic expansion valve and sensor 31 is a temperature transducer such as a thermocouple or thermistor.
  • expansion valve 26 is a mechanical thermal expansion valve and sensor 31 includes a small tube that terminates in a pressure vessel filled with a refrigerant that differs from the refrigerant running through refrigeration system 20 A.
  • refrigerant from evaporator 27 flows past sensor 31 on its way toward multi-stage compressor unit 10 A, the pressure vessel will either heat up or cool down, thereby changing the pressure within the pressure vessel.
  • sensor 31 sends a signal to expansion valve 26 to modify the pressure drop caused by the valve.
  • sensor 31 sends an electrical signal to expansion valve 26 which responds in a similar manner to regulate refrigerant flow.
  • sensor 31 will then heat up and send a signal to expansion valve 26 , causing the valve to open further and allow more refrigerant per unit time to flow through evaporator 27 , thereby reducing the heat of the refrigerant exiting evaporator 27 .
  • Economizer circuit 25 A also includes sensor 31 A that operates in a similar manner to sensor 31 .
  • sensor 31 A senses temperature along economizer return path 46 A and acts with expansion valve 30 A to control the pressure drop within expansion valve 30 A instead. It should also be noted that sensors other than the ones previously described may be substituted for sensors 31 and 31 A.
  • the operation of refrigeration system 20 A can be adjusted to meet the cooling demands and achieve optimum efficiency.
  • the displacements of cylinders 36 A, 36 B, and 36 C may also be adjusted to help achieve optimum efficiency of refrigeration system 20 A.
  • FIG. 1B illustrates a graph relating enthalpy to pressure for the refrigeration system 20 A of FIG. 1A .
  • Vapor dome V is formed by a saturated liquid line and a saturated vapor line, and defines the state of the refrigerant at various points along the refrigeration cycle. Underneath vapor dome V, all states involve both liquid and vapor coexisting at the same time. At the very top of vapor dome V is the critical point. The critical point is defined by the highest pressure where saturated liquid and saturated vapor coexist. In general, compressed liquids are located to the left of vapor dome V, while superheated vapors are located to the right of vapor dome V.
  • the main refrigerant path is the loop defined by the points 1 , 2 , 3 , 4 , and 5
  • the first economized path is the loop defined by the points 4 A, 5 A, 6 A, and 7 A.
  • the cycle begins in the main path at point 1 , where the refrigerant is at a low pressure and high enthalpy prior to entering multi-stage compressor unit 10 A. After a first stage of compression within cylinder 36 A of two-stage compressor sub-unit 32 , both the enthalpy and pressure increase as shown by point 2 .
  • the refrigerant After a second stage of compression within cylinder 36 B, the refrigerant exits multi-stage compressor unit 10 A at high pressure and even higher enthalpy, as shown by point 3 . Then, as the refrigerant flows through heat rejecting heat exchanger 24 , enthalpy decreases while pressure remains constant. Prior to entering first economizer heat exchanger 28 A, the refrigerant splits into a main portion and a first economized portion as shown by point 4 A. The main portion is then throttled in main expansion valve 26 , decreasing pressure as shown by point 5 . Finally, the main portion of the refrigerant is evaporated, exiting evaporator 27 at a higher enthalpy as shown by point 1 .
  • the first economized portion splits off of the main portion as indicated by point 4 A.
  • the first economized portion is throttled to a lower pressure in expansion valve 30 A as shown by point 5 A.
  • the first economized portion of the refrigerant then exchanges heat with the main portion in first economizer heat exchanger 28 A, cooling down the main portion of the refrigerant as indicated by point 4 , and heating up the first economized portion of the refrigerant as indicated by point 6 A.
  • the first economized portion is then compressed within single-stage compressor sub-unit 34 and merged with the main portion of the refrigerant discharged from two-stage compressor sub-unit 32 , as shown by point 7 A.
  • cylinders 36 A, 36 B, and 36 C of multi-stage compressor unit 10 A are configured to receive and compress refrigerant to different pressures.
  • cylinder 36 A receives and compresses refrigerant from the main refrigerant path to an intermediate pressure, as indicated by point 2 .
  • cylinder 36 B receives and compresses the refrigerant from an intermediate pressure to an exit pressure, as indicated by point 3 .
  • cylinder 36 C receives and compresses refrigerant from the first economized refrigerant path to an exit pressure, as indicated by point 7 A.
  • the exit pressure of cylinder 36 C is substantially equivalent to the exit pressure of cylinder 36 B.
  • the exit pressures are determined by the inlet pressure required by heat rejecting heat exchanger 24 .
  • FIG. 2A illustrates a schematic diagram of multi-stage compressor unit 10 B connected to refrigeration system 20 B.
  • Multi-stage compressor unit 10 B is similar to multi-stage compressor unit 10 A.
  • two-stage compressor sub-unit 32 further includes interstage port 48 configured to receive refrigerant from an economizer circuit to cool down the refrigerant in the main refrigerant path prior to a second stage of compression.
  • Refrigeration system 20 B is similar to refrigeration system 20 A, but further includes second economizer circuit 25 B.
  • Second economizer circuit 25 B includes second economizer heat exchanger 28 B, expansion valve 30 B, and sensor 31 B.
  • a main refrigerant path is created by a loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 .
  • a first economized refrigerant path is created by a loop defined by the points 5 A, 6 A, 7 A, 3 , and 4 .
  • a second economized refrigerant path is created by a loop defined by the points 5 B, 6 B, 7 B, and 8 B.
  • Refrigerant from path 40 B is then throttled in main expansion valve 26 .
  • the refrigerant is a two-phase liquid-vapor mixture and is directed toward evaporator 27 .
  • the refrigerant enters two-stage compressor sub-unit 32 through suction port 37 .
  • the refrigerant is compressed within cylinder 36 A, which is the first stage of two-stage compressor sub-unit 32 , and is then directed out of discharge port 50 (point 2 ), where it merges with the cooler refrigerant from economizer return path 46 A that is injected into interstage port 48 (point 3 ).
  • the refrigerant from economizer return path 46 A functions to cool down the refrigerant discharged from cylinder 36 A prior to the second stage of compression within cylinder 36 B. After the second stage of compression, the refrigerant is discharged through discharge port 39 (point 4 ).
  • the first economized path continues along path 42 A.
  • the refrigerant is throttled to a lower pressure by economizer expansion valve 30 A (point 6 A) prior to flowing through first economizer heat exchanger 28 A.
  • the refrigerant from path 42 A that flowed through first economizer heat exchanger 28 A (point 7 A) is then directed along economizer return path 46 A and injected into interstage port 48 of two-stage compressor sub-unit 32 where it merges with refrigerant flowing through the main path to cool down the refrigerant (point 3 ) prior to a second stage of compression in cylinder 36 B.
  • the refrigerant in path 40 A splits into two flow paths 40 B and 42 B.
  • the second economized path continues along flow path 42 B where the refrigerant is throttled to a lower pressure by economizer expansion valve 30 B (point 6 B) prior to flowing through second economizer heat exchanger 28 B.
  • the refrigerant from path 42 B that flowed through second economizer heat exchanger 28 B (point 7 B) is then directed along economizer return path 46 B and injected into suction port 52 of single-stage compressor sub-unit 34 for compression in single-stage compressor sub-unit 34 .
  • refrigerant is discharged through discharge port 54 (point 8 B) where it merges with the refrigerant discharged from two-stage compressor sub-unit 32 .
  • FIG. 2B illustrates a graph relating enthalpy to pressure for the refrigeration system 20 B of FIG. 2A .
  • the main refrigerant path is the loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 ;
  • the first economized path is the loop defined by the points 5 A, 6 A, 7 A, 3 , and 4 ;
  • the second economized path is the loop defined by the points 5 B, 6 B, 7 B, and 8 B.
  • cylinders 36 A, 36 B, and 36 C of multi-stage compressor unit 10 B are configured to receive and compress refrigerant to different pressures.
  • cylinder 36 A receives and compresses refrigerant from the main refrigerant path to an intermediate pressure, as indicated by point 2 .
  • cylinder 36 B receives and compresses refrigerant from the main refrigerant path and the first economized path from an intermediate pressure to an exit pressure, as indicated by point 4 .
  • cylinder 36 C receives and compresses refrigerant from the second economized refrigerant path to an exit pressure, as indicated by point 8 B.
  • the exit pressure of cylinder 36 C is substantially equivalent to the exit pressure of cylinder 36 B.
  • FIG. 3A illustrates a schematic diagram of multi-stage compressor unit 10 C connected to refrigeration system 20 C.
  • Multi-stage compressor unit 10 C is similar to multi-stage compressor unit 10 B.
  • single-stage compressor sub-unit 34 is configured to discharge into first economizer return path 46 A instead of into heat rejecting heat exchanger 24 , as depicted by multi-stage compressor unit 10 B of FIG. 2A .
  • a main refrigerant path is created by a loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 .
  • a first economized refrigerant path is created by a loop defined by the points 5 A, 6 A, 7 A, 3 , and 4 .
  • a second economized refrigerant path is created by a loop defined by the points 5 B, 6 B, 7 B, 8 B, 3 , and 4 .
  • Refrigerant from path 40 B is then throttled in main expansion valve 26 .
  • the refrigerant is a two-phase liquid-vapor mixture and is directed toward evaporator 27 .
  • the refrigerant enters two-stage compressor sub-unit 32 through suction port 37 .
  • the refrigerant is compressed within cylinder 36 A, which is the first stage of two-stage compressor sub-unit 32 , and is then directed out discharge port 50 (point 2 ), where it merges with the cooler refrigerant from economizer return path 46 A that is injected into interstage port 48 (point 3 ).
  • the refrigerant from economizer return path 46 A functions to cool down the refrigerant discharged from cylinder 36 A prior to the second stage of compression within cylinder 36 B. After the second stage of compression, the refrigerant is discharged through discharge port 39 (point 4 ).
  • the first economized path continues along path 42 A.
  • the refrigerant is throttled to a lower pressure by economizer expansion valve 30 A (point 6 A) prior to flowing through first economizer heat exchanger 28 A.
  • the refrigerant from path 42 A that flowed through first economizer heat exchanger 28 A (point 7 A) is then directed along economizer return path 46 A and injected into interstage port 48 of two-stage compressor sub-unit 32 where it merges with refrigerant flowing through the main path to cool down the refrigerant (point 3 ) prior to a second stage of compression in cylinder 36 B.
  • the refrigerant in path 40 A splits into two flow paths 40 B and 42 B.
  • the second economized path continues along flow path 42 B where the refrigerant is throttled to a lower pressure by economizer expansion valve 30 B (point 6 B) prior to flowing through second economizer heat exchanger 28 B.
  • the refrigerant from path 42 B that flowed through second economizer heat exchanger 28 B (point 7 B) is then directed along economizer return path 46 B and injected into suction port 52 of single-stage compressor sub-unit 34 for compression in single-stage compressor sub-unit 34 .
  • the refrigerant After compression within single-stage compressor sub-unit 34 , the refrigerant is discharged through discharge port 54 where it is mixed with the refrigerant in economizer return path 46 A (point 8 B) prior to injection into interstage port 48 of two-stage compressor sub-unit 32 (point 3 ).
  • FIG. 3B illustrates a graph relating enthalpy to pressure for the refrigeration system 20 C of FIG. 3A .
  • the main refrigerant path is the loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 ;
  • the first economized path is the loop defined by the points 5 A, 6 A, 7 A, 3 , and 4 ;
  • the second economized path is the loop defined by the points 5 B, 6 B, 7 B, 8 B, 3 , and 4 .
  • cylinders 36 A, 36 B, and 36 C of multi-stage compressor unit 10 C are configured to receive and compress refrigerant to different pressures.
  • cylinder 36 A receives and compresses refrigerant from the main refrigerant path to an intermediate pressure, as indicated by point 2 .
  • cylinder 36 C receives and compresses refrigerant from the second economized refrigerant path to an exit pressure, as indicated by point 8 B.
  • cylinder 36 B receives and compresses refrigerant from the main refrigerant path, the first economized path, and the second economized path to an exit pressure, as indicated by point 4 .
  • the exit pressure of cylinder 36 C is substantially equivalent to the intermediate pressure of cylinder 36 A.
  • FIG. 4A illustrates a schematic diagram of multi-stage compressor unit 10 D connected to refrigeration system 20 D.
  • Multi-stage compressor unit 10 D is similar to multi-stage compressor unit 10 A. However, multi-stage compressor unit 10 D further includes single-stage compressor sub-unit 35 having cylinder 36 D.
  • Refrigeration system 20 D is similar to refrigeration system 20 C, except that interstage port 48 is replaced by intercooler 49 , which is configured to cool the main portion of the refrigerant between the first and second stages of compression in two-stage compressor sub-unit 32 .
  • a main refrigerant path is created by a loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 .
  • a first economized refrigerant path is created by a loop defined by the points 5 A, 6 A, 7 A, and 8 A.
  • a second economized refrigerant path is created by a loop defined by the points 5 B, 6 B, 7 B, and 8 B.
  • Refrigerant from path 40 B is then throttled in main expansion valve 26 .
  • the refrigerant is a two-phase liquid-vapor mixture and is directed toward evaporator 27 .
  • the refrigerant enters two-stage compressor sub-unit 32 through suction port 37 .
  • the refrigerant is compressed within cylinder 36 A, which is the first stage of two-stage compressor sub-unit 32 , and is then directed out discharge port 50 (point 2 ), where it flows through intercooler 49 prior to a second stage of compression in cylinder 36 B.
  • Intercooler 49 is configured to cool down the refrigerant discharged from cylinder 36 A prior to the second stage of compression within cylinder 36 B.
  • the refrigerant is discharged through discharge port 39 (point 4 ).
  • the first economized path continues along path 42 A.
  • the refrigerant is throttled to a lower pressure by economizer expansion valve 30 A (point 6 A) prior to flowing through first economizer heat exchanger 28 A.
  • the refrigerant from path 42 A that flowed through first economizer heat exchanger 28 A (point 7 A) is then directed along economizer return path 46 A and injected into suction port 52 of single-stage compressor sub-unit 34 for compression in single-stage compressor sub-unit 34 .
  • the refrigerant is discharged through discharge port 54 (point 8 A) where it merges with the refrigerant discharged from two-stage compressor sub-unit 32 and single-stage compressor sub-unit 35 .
  • the refrigerant in path 40 A splits into two flow paths 40 B and 42 B.
  • the second economized path continues along flow path 42 B where the refrigerant is throttled to a lower pressure by economizer expansion valve 30 B (point 6 B) prior to flowing through second economizer heat exchanger 28 B.
  • the refrigerant from path 42 B that flowed through second economizer heat exchanger 28 B (point 7 B) is then directed along economizer return path 46 B and injected into suction port 56 of single-stage compressor sub-unit 35 for compression in single-stage compressor sub-unit 35 .
  • the refrigerant is discharged through discharge port 58 (point 8 B) where it merges with the refrigerant discharged from two-stage compressor sub-unit 32 and single-stage compressor sub-unit 34 .
  • FIG. 4B illustrates a graph relating enthalpy to pressure for the refrigeration system 20 D of FIG. 4A .
  • the main refrigerant path is the loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 ;
  • the first economized path is the loop defined by the points 5 A, 6 A, 7 A, and 8 A;
  • the second economized path is the loop defined by the points 5 B, 6 B, 7 B, and 8 B.
  • cylinders 36 A, 36 B, 36 C, and 36 D of multi-stage compressor unit 10 D are configured to receive and compress refrigerant to different pressures.
  • cylinder 36 A receives and compresses refrigerant from the main refrigerant path to an intermediate pressure, as indicated by point 2 .
  • cylinder 36 B receives and compresses refrigerant from the main refrigerant path from an intermediate pressure to an exit pressure, as indicated by point 4 .
  • Cylinder 36 C receives and compresses refrigerant from the first economized refrigerant path to an exit pressure, as indicated by point 8 A.
  • cylinder 36 D receives and compresses refrigerant from the second economized refrigerant path to an exit pressure, as indicated by point 8 B.
  • exit pressures of cylinders 36 C and 36 D are substantially equivalent to the exit pressure of cylinder 36 B.
  • FIG. 5A illustrates a schematic diagram of multi-stage compressor unit 10 E connected to refrigeration system 20 E.
  • multi-stage compressor unit 10 E further includes two-stage compressor sub-unit 70 .
  • Two-stage compressor sub-unit 70 includes cylinders 36 E and 36 F connected in series.
  • Refrigeration system 20 E is similar to refrigeration system 20 D, except that third economizer circuit 25 C is added to the system.
  • a main refrigerant path is created by a loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 .
  • a first economized refrigerant path is created by a loop defined by the points 5 A, 6 A, 7 A, 3 , and 4 .
  • a second economized refrigerant path is created by a loop defined by the points 5 B, 6 B, 7 B, 9 , and 10 .
  • a third economized refrigerant path is created by a loop defined by the points 5 C, 6 C, 7 C, 8 C, 9 , and 10 .
  • Refrigerant from path 40 C is then throttled in main expansion valve 26 .
  • the refrigerant is a two-phase liquid-vapor mixture and is directed toward evaporator 27 .
  • the refrigerant enters two-stage compressor sub-unit 32 through suction port 37 .
  • the refrigerant is compressed within cylinder 36 A, which is the first stage of two-stage compressor sub-unit 32 , and is then directed out discharge port 50 (point 2 ), where it merges with the cooler refrigerant from economizer return path 46 A that is injected into interstage port 48 (point 3 ).
  • the refrigerant from economizer return path 46 A functions to cool down the refrigerant discharged from cylinder 36 A prior to the second stage of compression within cylinder 36 B. After the second stage of compression, the refrigerant is discharged through discharge port 39 (point 4 ).
  • the first economized path continues along path 42 A.
  • the refrigerant is throttled to a lower pressure by economizer expansion valve 30 A (point 6 A) prior to flowing through first economizer heat exchanger 28 A.
  • the refrigerant from path 42 A that flowed through first economizer heat exchanger 28 A (point 7 A) is then directed along economizer return path 46 A and injected into interstage port 48 of two-stage compressor sub-unit 32 where it merges with refrigerant flowing through the main path to cool down the refrigerant (point 3 ) prior to a second stage of compression in cylinder 36 B.
  • the refrigerant in path 40 A splits into two flow paths 40 B and 42 B (point 5 B).
  • the second economized path continues along flow path 42 B where the refrigerant is throttled to a lower pressure by economizer expansion valve 30 B prior to flowing through second economizer heat exchanger 28 B (point 6 B).
  • the refrigerant from path 42 B that flowed through second economizer heat exchanger 28 B (point 7 B) is then directed along economizer return path 46 B and injected into interstage port 72 of two-stage compressor sub-unit 70 where it mixes with refrigerant exiting discharge port 74 (point 9 ) to cool down the refrigerant prior to a second stage of compression in cylinder 36 F.
  • the refrigerant in path 40 B splits into two flow paths 40 C and 42 C (point 5 C).
  • the third economized path continues along flow path 42 C where the refrigerant is throttled to a lower pressure by economizer expansion valve 30 C prior to flowing through third economizer heat exchanger 28 C (point 6 C).
  • the refrigerant from path 42 C that flowed through third economizer heat exchanger 28 C (point 7 C) is then directed along economizer return path 46 C and injected into suction port 76 of two-stage compressor sub-unit 70 .
  • the refrigerant After a first stage of compression in cylinder 36 E (point 8 C), the refrigerant is cooled prior to a second stage of compression by the refrigerant from economizer return path 46 B that was injected into interstage port 72 (point 9 ). After the second stage of compression in cylinder 36 F, the refrigerant is discharged through discharge port 78 (point 10 ), where it merges with the compressed refrigerant discharged from two-stage compressor sub-unit 32 .
  • FIG. 5B illustrates a graph relating enthalpy to pressure for the refrigeration system 20 E of FIG. 5A .
  • the main refrigerant path is the loop defined by the points 1 , 2 , 3 , 4 , 5 , and 6 ;
  • the first economized path is the loop defined by the points 5 A, 6 A, 7 A, 3 , and 4 ;
  • the second economized path is the loop defined by the points 5 B, 6 B, 7 B, 9 , and 10 ;
  • the third economized path is the loop defined by the points 5 C, 6 C, 7 C, 8 C, 9 , and 10 .
  • cylinders 36 A, 36 B, 36 E, and 36 F of multi-stage compressor unit 10 E are configured to receive and compress refrigerant to different pressures.
  • cylinder 36 A receives and compresses refrigerant from the main refrigerant path to an intermediate pressure, as indicated by point 2 .
  • cylinder 36 B receives and compresses refrigerant from the main refrigerant path and the first economized path from the intermediate pressure to an exit pressure, as indicated by point 4 .
  • cylinder 36 E receives and compresses refrigerant from the third economized refrigerant path to an intermediate pressure, as indicated by point 8 C.
  • Cylinder 36 F then receives and compresses refrigerant from the second and third economized paths from the intermediate pressure to an exit pressure, as indicated by point 10 .
  • the exit pressure of cylinder 36 B is substantially equivalent to the exit pressure of cylinder 36 F.
  • FIG. 6A illustrates a schematic diagram of multi-stage compressor unit 10 F connected to refrigeration system 20 F, which includes heat rejecting heat exchanger 24 , first expansion valve 26 , first evaporator 27 , first sensor 31 , second expansion valve 126 , second evaporator 127 , and second sensor 131 .
  • Multi-stage compressor unit 10 F includes two-stage compressor sub-unit 32 and single-stage compressor sub-unit 34 .
  • Two-stage compressor sub-unit 32 includes cylinders 36 A and 36 B connected in series, while single-stage compressor sub-unit 34 includes cylinder 36 C.
  • a first main refrigerant path is created by a loop defined by the points 1 , 2 , 3 , 4 , and 5 .
  • a second main refrigerant path is created by a loop defined by the points 4 , 5 A, 6 A, and 7 A.
  • first main refrigerant path After refrigerant exits two-stage compressor sub-unit 32 at high pressure and enthalpy through discharge port 39 (point 3 ), the refrigerant loses heat in heat rejecting heat exchanger 24 , exiting heat rejecting heat exchanger 24 at low enthalpy and high pressure (point 4 ).
  • the refrigerant in the main path is then throttled in first expansion valve 26 .
  • the refrigerant After going through an expansion process within first expansion valve 26 (point 5 ), the refrigerant is a two-phase liquid-vapor mixture and is directed toward first evaporator 27 . After evaporation of the remainder of the liquid (point 1 ), the refrigerant enters two-stage compressor sub-unit 32 through suction port 37 .
  • the refrigerant is compressed within cylinder 36 A, which is the first stage of two-stage compressor sub-unit 32 , and is then directed out discharge port 50 (point 2 ). After the second stage of compression in cylinder 36 B, the refrigerant is discharged through discharge port 39 (point 3 ).
  • the refrigerant is throttled in second expansion valve 126 .
  • the refrigerant is a two-phase liquid-vapor mixture and is directed toward second evaporator 127 .
  • the refrigerant enters single-stage compressor sub-unit 34 through suction port 52 .
  • the refrigerant is compressed within cylinder 36 C, and is then directed out discharge port 54 point 7 A) where it mixes with the refrigerant discharged through discharge port 39 of two-stage compressor sub-unit 32 .
  • FIG. 6B illustrates a graph relating enthalpy to pressure for the refrigeration system 20 F of FIG. 6A .
  • the first main refrigerant path is the loop defined by the points 1 , 2 , 3 , 4 , and 5
  • the second main refrigerant path is the loop defined by the points 4 , 5 A, 6 A, and 7 A.
  • cylinders 36 A, 36 B, and 36 C of multi-stage compressor unit 10 F are configured to receive and compress refrigerant to different pressures.
  • cylinder 36 A receives and compresses refrigerant from the first main refrigerant path to an intermediate pressure, as indicated by point 2 .
  • cylinder 36 B receives and compresses the refrigerant from the intermediate pressure to an exit pressure, as indicated by point 3 .
  • cylinder 36 C receives and compresses refrigerant from the second main refrigerant path to an exit pressure, as indicated by point 7 A.
  • the exit pressure of cylinder 36 C is substantially equivalent to the exit pressure of cylinder 36 B.
  • the multi-stage compressor unit of the present invention is useful to increase system efficiency in a refrigeration system using any type of refrigerant, it is especially useful in refrigeration systems that utilize transcritical refrigerants, such as carbon dioxide. Because carbon dioxide is such a low critical temperature refrigerant, refrigeration systems using carbon dioxide typically run transcritical. Furthermore, because carbon dioxide is such a high pressure refrigerant, there is more opportunity to provide multiple pressure steps between the high and low pressure portions of the circuit to include multiple economizers and multiple compressor cylinders, each of which contributes to increase the efficiency of the system. Thus, the multi-stage compressor unit of the present invention may be used to increase the efficiency of systems utilizing transcritical refrigerants such as carbon dioxide, making their efficiency comparable to that of typical refrigerants. However, the multi-stage compressor unit of the present invention is useful to increase the efficiency in refrigeration systems using any refrigerant, including those that run subcritical as well as those that run transcritical.

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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)
  • Chemical Kinetics & Catalysis (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/308,016 2006-06-01 2006-06-01 Multi-stage compressor unit for refrigeration system Abandoned US20090175748A1 (en)

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US20140053585A1 (en) * 2011-04-21 2014-02-27 Carrier Corporation Transcritical Refrigerant Vapor System With Capacity Boost
US20140305150A1 (en) * 2013-04-15 2014-10-16 Lg Electronics Inc. Air conditioner and method for controlling the same
US9178405B2 (en) 2011-05-13 2015-11-03 Carrier Corporation Magnetic drive coupling apparatus
DE102014116437B3 (de) * 2014-11-11 2015-12-17 E³Xpert Ug (Haftungsbeschränkt) Wärmepumpen-Vorrichtung
KR101859231B1 (ko) 2012-01-09 2018-05-17 엘지전자 주식회사 냉장 냉동 복합 시스템
US10222078B2 (en) 2009-11-23 2019-03-05 Carrier Corporation Method and device for air conditioning with humidity control
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JP7780122B1 (ja) 2024-09-18 2025-12-04 ダイキン工業株式会社 冷凍サイクル装置
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US20100229582A1 (en) * 2006-03-06 2010-09-16 Masahiro Yamada Refrigeration System
US8973384B2 (en) * 2009-05-26 2015-03-10 Mitsubishi Electric Corporation Heat pump apparatus
US20120060538A1 (en) * 2009-05-26 2012-03-15 Mitsubishi Electric Corporation Heat pump apparatus
US10222078B2 (en) 2009-11-23 2019-03-05 Carrier Corporation Method and device for air conditioning with humidity control
CN102022851A (zh) * 2010-12-22 2011-04-20 天津商业大学 双级压缩制冷系统
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EP4585804A1 (fr) 2024-01-11 2025-07-16 Konvekta Aktiengesellschaft Dispositif de compression flexible et circuit de fluide frigorigène l'utilisant et procédé associé

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EP2021703A4 (fr) 2012-02-15
WO2007142619B1 (fr) 2008-10-09
CN101460789A (zh) 2009-06-17
EP2021703A2 (fr) 2009-02-11
CN101460789B (zh) 2011-01-26
WO2007142619A3 (fr) 2008-08-28
JP2009539058A (ja) 2009-11-12
WO2007142619A2 (fr) 2007-12-13
JP5028481B2 (ja) 2012-09-19

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