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EP4540559A1 - Système de compresseur pour système de chauffage, de ventilation, de climatisation et/ou de réfrigération - Google Patents

Système de compresseur pour système de chauffage, de ventilation, de climatisation et/ou de réfrigération

Info

Publication number
EP4540559A1
EP4540559A1 EP23824668.0A EP23824668A EP4540559A1 EP 4540559 A1 EP4540559 A1 EP 4540559A1 EP 23824668 A EP23824668 A EP 23824668A EP 4540559 A1 EP4540559 A1 EP 4540559A1
Authority
EP
European Patent Office
Prior art keywords
auxiliary compressor
refrigerant flow
economizer
vapor refrigerant
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23824668.0A
Other languages
German (de)
English (en)
Inventor
Paul Eric LE SAUSSE
Damien Jean Daniel Arnou
Francois Charles André CLUNET
Jeb William SCHREIBER
Abdel Kader JANNOUN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tyco Fire and Security GmbH
Original Assignee
Tyco Fire and Security GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tyco Fire and Security GmbH filed Critical Tyco Fire and Security GmbH
Publication of EP4540559A1 publication Critical patent/EP4540559A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/024—Compressor control by controlling the electric parameters, e.g. current or voltage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • Chiller systems utilize a working fluid (e.g., a refrigerant) that changes phases between vapor, liquid, and combinations thereof in response to exposure to different temperatures and pressures within components of the chiller system.
  • the chiller system may place the working fluid in a heat exchange relationship with a cooling fluid (e.g., water) and may deliver the cooling fluid to conditioning equipment and/or a conditioned environment serviced by the chiller system.
  • the chiller system may include an economizer configured to improve an efficiency of the chiller system.
  • a first heat exchanger e.g., a condenser
  • the economizer may reduce a pressure of the working fluid to further cool the working fluid and separate the working fluid into liquid phase working fluid and vapor phase working fluid.
  • the economizer may direct the liquid phase working fluid to a second heat exchanger (e.g., an evaporator) configured to place the working fluid in the heat exchange relationship with the cooling fluid.
  • the economizer may direct the vapor phase working fluid to a compressor for pressurization.
  • existing chiller systems that include economizers may operate inefficiently.
  • a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system includes an economizer system configured to reduce a pressure of a first portion of a refrigerant, an auxiliary compressor system configured to receive the first portion of the refrigerant from the economizer system, where the auxiliary compressor system comprises a first auxiliary compressor and a second auxiliary compressor, and a primary compressor.
  • the HVAC&R system also includes a condenser configured to receive the first portion of the refrigerant from the auxiliary compressor system and a second portion of the refrigerant from the primary compressor.
  • HVAC&R heating, ventilation, air conditioning, and/or refrigeration
  • FIG. 1 is a perspective view of a building that may utilize an embodiment of a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;
  • HVAC&R heating, ventilation, air conditioning, and/or refrigeration
  • FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure
  • FIG. 3 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 4 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 5 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 6 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 7 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 8 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 9 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 10 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 11 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 12 is a schematic of an embodiment of a vapor compression system that includes an economizer system and an auxiliary compressor system configured to receive working fluid from the economizer system, in accordance with an aspect of the present disclosure
  • FIG. 13 is a graphical illustration of a vapor compression cycle, in accordance with an aspect of the present disclosure.
  • FIG. 14 is a graphical illustration of a vapor compression cycle, in accordance with an aspect of the present disclosure.
  • FIG. 15 is a graphical illustration of a vapor compression cycle, in accordance with an aspect of the present disclosure.
  • FIG. 16 is a graphical illustration of a vapor compression cycle, in accordance with an aspect of the present disclosure.
  • Embodiments of the present disclosure relate to a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system having a vapor compression system (e g., a vapor compression circuit).
  • the vapor compression system may include a compressor (e.g., a primary compressor) configured to pressurize a working fluid within the vapor compression system and direct the working fluid to a condenser, which may cool and condense the working fluid.
  • the condensed working fluid may be directed toward an expansion device, which may reduce a pressure of the working fluid, further cooling the working fluid.
  • the cooled working fluid may be directed to an evaporator, where the working fluid may be placed in a heat exchange relationship with a cooling fluid to cool the cooling fluid.
  • the compressor may then receive the working fluid from the evaporator for pressurization to restart the vapor compression cycle.
  • the vapor compression system may include an economizer system configured to receive the working fluid from the condenser.
  • the economizer system may be configured to reduce a pressure of the working fluid to further cool the working fluid and separate the working fluid into liquid working fluid and vapor working fluid.
  • the economizer system may direct the liquid working fluid to the evaporator to enable the evaporator to place the liquid working fluid in a heat exchange relationship with the cooling fluid.
  • the vapor working fluid may be directed from the economizer system toward the condenser. However, the vapor working fluid directed from the economizer system may not readily flow toward the condenser in some circumstances.
  • the working fluid pressurized by the compressor may also be directed toward the condenser to mix with the working fluid directed from the economizer system, but the working fluid from the compressor and the working fluid from the economizer system may be at different pressures.
  • Such a pressure differential may disrupt flow of the working fluid to the condenser, such as by causing back flow of working fluid toward the compressor and/or toward the economizer.
  • the working fluid may not efficiently flow toward the condenser from the economizer.
  • a element e.g., a system, component, or the like
  • a fluid e.g., refrigerant in a vapor or liquid phase
  • the element pressurizes, forces, guides (e.g., via piping, valves, mechanical operation), or the like the fluid directly or indirectly to the other element.
  • the present disclosure is directed to incorporating an additional, auxiliary compressor system configured to receive vapor working fluid from an economizer system, pressurize the vapor working fluid, and direct the pressurized vapor working fluid toward the condenser.
  • the auxiliary compressor system may pressurize the vapor working fluid toward the pressure of the working fluid pressurized by the compressor (e g., the primary compressor) to reduce a pressure differential between the respective working fluid flows directed toward the condenser, thereby facilitating efficient flow of the working fluid through the HVAC&R system.
  • the auxiliary compressor system may include multiple auxiliary compressors that may be less costly than a single compressor that can handle the same load.
  • each auxiliary compressor may occupy a smaller physical footprint than would be occupied by a single compressor to enable efficient usage of space via the HVAC&R system.
  • the auxiliary compressors may be configured in any suitable series flow arrangement and/or a parallel flow arrangement with respect to flow of the working fluid through the auxiliary compressor system to provide desirable pressurization of the vapor working fluid for flow toward the condenser.
  • the auxiliary compressor system may improve operation of the HVAC&R system having the economizer without significantly increasing a manufacturing cost of and/or footprint occupied by the HVAC&R system.
  • FIG. l is a perspective view of an embodiment of an environment for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system 10 in a building 12 for atypical commercial setting.
  • the HVAC&R system 10 may include a vapor compression system 14 (e.g., a chiller) that supplies a chilled liquid, which may be used to cool the building 12.
  • the HVAC&R system 10 may also include a boiler 16 to supply warm liquid to heat the building 12 and an air distribution system which circulates air through the building 12.
  • the air distribution system can also include an air return duct 18, an air supply duct 20, and/or an air handler 22.
  • the air handler 22 may include a heat exchanger that is connected to the boiler 16 and the vapor compression system 14 by conduits 24.
  • the heat exchanger in the air handler 22 may receive either heated liquid from the boiler 16 or chilled liquid from the vapor compression system 14, depending on the mode of operation of the HVAC&R system 10.
  • the HVAC&R system 10 is shown with a separate air handler on each floor of building 12, but in other embodiments, the HVAC&R system 10 may include air handlers 22 and/or other components that may be shared between or among floors.
  • FIGS. 2 and 3 are embodiments of the vapor compression system 14 that can be used in the HVAC&R system 10.
  • the vapor compression system 14 may circulate a refrigerant through a circuit starting with a compressor 32.
  • the circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and a liquid chiller or an evaporator 38.
  • the vapor compression system 14 may further include a control panel 40 that has an analog to digital (A/D) converter 42, a microprocessor 44, a non-volatile memory 46, and/or an interface board 48.
  • A/D analog to digital
  • HFC hydrofluorocarbon
  • R- 410A, R-407, R-134a, R-1234ze, R1233zd hydrofluoro olefin
  • HFO hydrofluoro olefin
  • "natural" refrigerants like ammonia (NH3), R-717, carbon dioxide (CO2), R-744, or hydrocarbon based refrigerants, water vapor, or any other suitable refrigerant.
  • the vapor compression system 14 may be configured to efficiently utilize refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure, also referred to as low pressure refrigerants, versus a medium pressure refrigerant, such as R-134a.
  • refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure also referred to as low pressure refrigerants
  • medium pressure refrigerant such as R-134a.
  • "normal boiling point” may refer to a boiling point temperature measured at one atmosphere of pressure.
  • the vapor compression system 14 may use one or more of a variable speed drive (VSDs) 52, a motor 50, the compressor 32, the condenser 34, the expansion valve or device 36, and/or the evaporator 38.
  • the motor 50 may drive the compressor 32 and may be powered by a variable speed drive (VSD) 52.
  • the VSD 52 receives alternating current (AC) power having a particular fixed line voltage and fixed line frequency from an AC power source, and provides power having a variable voltage and frequency to the motor 50.
  • the motor 50 may be powered directly from an AC or direct current (DC) power source.
  • the motor 50 may include any type of motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.
  • the compressor 32 compresses a refrigerant vapor and delivers the vapor to the condenser 34 through a discharge passage.
  • the compressor 32 may be a centrifugal compressor.
  • the refrigerant vapor delivered by the compressor 32 to the condenser 34 may transfer heat to a cooling fluid (e.g., water or air) in the condenser 34.
  • the refrigerant vapor may condense to a refrigerant liquid in the condenser 34 as a result of thermal heat transfer with the cooling fluid.
  • the liquid refrigerant from the condenser 34 may flow through the expansion device 36 to the evaporator 38.
  • the condenser 34 is water cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies the cooling fluid to the condenser 34.
  • the liquid refrigerant delivered to the evaporator 38 may absorb heat from another cooling fluid, which may or may not be the same cooling fluid used in the condenser 34.
  • the liquid refrigerant in the evaporator 38 may undergo a phase change from the liquid refrigerant to a refrigerant vapor.
  • the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to a cooling load 62.
  • the cooling fluid of the evaporator 38 enters the evaporator 38 via return line 60R and exits the evaporator 38 via supply line 60S.
  • the evaporator 38 may reduce the temperature of the cooling fluid in the tube bundle 58 via thermal heat transfer with the refrigerant.
  • the tube bundle 58 in the evaporator 38 can include a plurality of tubes and/or a plurality of tube bundles. In any case, the vapor refrigerant exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.
  • FIG. 4 is a schematic of the vapor compression system 14 with an intermediate circuit 64 incorporated between condenser 34 and the expansion device 36.
  • the intermediate circuit 64 may have an inlet line 68 that is directly fluidly connected to the condenser 34.
  • the inlet line 68 may be indirectly fluidly coupled to the condenser 34.
  • the inlet line 68 includes a first expansion device 66 positioned upstream of an intermediate vessel 70.
  • the intermediate vessel 70 may be a flash tank (e.g., a flash intercooler, an economizer).
  • the intermediate vessel 70 may be configured as a heat exchanger or a “surface economizer.” In the illustrated embodiment of FIG.
  • the intermediate vessel 70 is used as a flash tank, and the first expansion device 66 is configured to lower the pressure of (e.g., expand) the liquid refrigerant received from the condenser 34. During the expansion process, a portion of the liquid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor from the liquid received from the first expansion device 66.
  • the intermediate vessel 70 may provide for further expansion of the liquid refrigerant because of a pressure drop experienced by the liquid refrigerant when entering the intermediate vessel 70 (e.g., due to a rapid increase in volume experienced when entering the intermediate vessel 70).
  • the vapor in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32. In other embodiments, the vapor in the intermediate vessel may be drawn to an intermediate stage of the compressor 32 (e.g., not the suction stage).
  • the liquid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid refrigerant exiting the condenser 34 because of the expansion in the expansion device 66 and/or the intermediate vessel 70.
  • the liquid from intermediate vessel 70 may then flow in line 72 through a second expansion device 36 to the evaporator 38.
  • any of the features described herein may be incorporated with the vapor compression system 14 or any other suitable HVAC&R systems.
  • the present techniques may be incorporated with any HVAC&R system having an economizer, such as the intermediate vessel 70, and a compressor, such as the compressor 32.
  • the discussion below describes the present techniques incorporated with embodiments of the compressor 32 configured as a single stage compressor.
  • the systems and methods described herein may be incorporated with other embodiments of the compressor 32 and HVAC&R system 10.
  • the present disclosure is directed to a vapor compression system that includes an economizer system (e.g., an intermediate vessel) configured to receive refrigerant from a condenser and to separate the refrigerant into liquid refrigerant and vapor refrigerant.
  • the economizer system may direct the liquid refrigerant to an evaporator of the vapor compression system to enable the evaporator to place the liquid refrigerant in a heat exchange relationship with a cooling fluid to cool the cooling fluid.
  • the vapor compression system may include an auxiliary compressor system that has multiple auxiliary compressors configured to receive and pressurize the vapor refrigerant directed from the economizer system.
  • the auxiliary compressor system may direct the pressurized vapor refrigerant to a condenser, which may cool the vapor refrigerant.
  • the auxiliary compressors of the auxiliary compressor system may be in a series flow arrangement and/or a parallel flow arrangement suitable for increasing the pressure of the vapor refrigerant to a desirable level for discharge toward the condenser.
  • the auxiliary compressors may be less costly and/or may occupy a smaller physical footprint as compared to conventional compressor embodiments, such as that of a primary compressor of the vapor compression system.
  • the auxiliary compressor system may provide desirable operations without significantly increasing a manufacturing cost of and/or a physical footprint occupied by the HVAC&R system.
  • FIG. 5 is a schematic of an embodiment of a vapor compression system 100 that includes a primary compressor 102 (e.g., the compressor 32, a single stage compressor, a multistage compressor), the condenser 34, the evaporator 38, and an economizer system 104 (e.g., the intermediate vessel 70, an intercooler).
  • the primary compressor 102 may include any suitable number of compressor stages, such as one compressor stage or two or more compressor stages.
  • the vapor compression system 100 also includes an auxiliary compressor system 106 (e.g., a secondary compressor system, a parallel compressor system) fluidly coupled to the economizer system 104.
  • auxiliary compressor system 106 e.g., a secondary compressor system, a parallel compressor system
  • the auxiliary compressor system 106 may draw vapor refrigerant from the economizer system 104, compress the vapor refrigerant, and discharge the compressed vapor refrigerant toward the condenser 34.
  • the auxiliary compressor system 106 instead of the primary compressor 102, may receive the vapor refrigerant from economizer system 104.
  • the auxiliary compressor system 106 may pressurize the received vapor refrigerant and direct the pressurized vapor refrigerant toward the condenser 34 and bypass the primary compressor 102.
  • the auxiliary compressor system 106 may increase the pressure of the vapor refrigerant toward that of the vapor refrigerant pressurized by the primary compressor 102.
  • a first pressure of the vapor refrigerant directed from the primary compressor 102 into the condenser 34 may be similar or substantially the same as a second pressure of the vapor refrigerant directed from the auxiliary compressor system 106 into the condenser 34 (e.g., via a second condenser inlet 110).
  • Pressurization of the refrigerant flows to approximately the same pressure may reduce disruptions to refrigerant flow toward the condenser 34 (e.g., by blocking back flow of refrigerant through the first condenser inlet 108 and/or through the second condenser inlet 110) that may otherwise occur because of a pressure differential between the respective refrigerant flows from the primary compressor 102 and from the economizer system 104.
  • the refrigerant may more readily flow through the condenser 34.
  • a desirable flow e.g., a target flow rate
  • a desirable cooling of the refrigerant provided via the condenser 34 may be achieved.
  • the primary compressor 102 provides substantially all of the compression head from an outlet 112 of the evaporator 38 to an outlet 114 of the primary compressor 102 (and the inlet 108 to the condenser 34 from the primary compressor 102).
  • the auxiliary compressor system 106 provides a pressure boost to the refrigerant entering the condenser 34 from the economizer system 104.
  • An amount of pressurization provided by the auxiliary compressor system 106 may be less than that provided by the primary compressor 102.
  • the pressure of the vapor refrigerant directed from the economizer system 104 to the auxiliary compressor system 106 may be greater than the pressure of the refrigerant directed from the evaporator 38 to the primary compressor 102.
  • a first pressure differential between the pressure of the refrigerant received by the auxiliary compressor system 106 and a corresponding target pressure for pressurization by the auxiliary compressor system 106 may be less than a second pressure differential between the pressure of the refrigerant received by the primary compressor 102 and a corresponding target pressure for pressurization by the primary compressor 102.
  • a selected embodiment of a compressor utilized by the auxiliary compressor system 106 may be different than the embodiment of the primary compressor 102 to provide the desirable pressurization of the refrigerant flow from the economizer system 104.
  • a design specification and/or operation of the auxiliary compressor system 106 may be different than that of the primary compressor 102.
  • the auxiliary compressor system 106 may include auxiliary compressors that are associated with a reduced cost, a reduced size, an increased configurability, and so forth.
  • the auxiliary compressor system 106 may provide desirable operation, reduced cost of manufacture, improved ease of installation, and so forth associated with the vapor compression system 100.
  • the economizer system 104 may include a plurality of economizers (e.g., economizer stages) that are each configured to reduce a pressure of a refrigerant flow.
  • a first economizer 140 e.g., a first economizer stage
  • the first economizer 140 may direct the vapor refrigerant as a first vapor refrigerant flow 142 toward the auxiliary compressor system 106, and the first economizer 140 may direct the liquid refrigerant as a first liquid refrigerant flow 144 to a second economizer 146.
  • the second economizer 146 may reduce the pressure of the first liquid refrigerant flow 144 received from the first economizer 140 to vaporize a portion of the refrigerant and separate the refrigerant into liquid refrigerant and vapor refrigerant.
  • the second economizer 146 may direct the vapor refrigerant as a second vapor refrigerant flow 148 toward the auxiliary compressor system 106, and the second economizer 146 may direct the liquid refrigerant as a second liquid refrigerant flow 150 to a third economizer 152.
  • the third economizer 152 may further reduce a pressure of the second liquid refrigerant flow 150 received from the second economizer 146 to vaporize a portion of the refrigerant and separate the refrigerant into liquid refrigerant and vapor refrigerant.
  • the third economizer 152 may direct the vapor refrigerant as a third vapor refrigerant flow 154 toward the auxiliary compressor system 106, and the third economizer 152 may direct the liquid refrigerant as a third liquid refrigerant flow 156 to the evaporator 38.
  • the second economizer 146 and/or the third economizer 152 may increase cooling of the refrigerant prior to discharge toward the evaporator 38, thereby increasing an amount of cooling provided by the refrigerant flow in evaporator 38 to the cooling fluid and increasing efficient operation of the vapor compression system 100 to condition the cooling fluid.
  • each economizer 140, 146, 152 may be separate chambers, compartments, volumes, or spaces of a common or the same economizer enclosure, housing, or shell 158. That is, the economizer system 104 may include a single economizer enclosure 158 that may enclose multiple economizers 140, 146, 152 configured to reduce the pressure of the refrigerant (e.g., via stages). For instance, each economizer 140, 146, 152 may be separated from one another within the economizer enclosure 158 via a partition, a divider, a wall, a plate, and the like.
  • each economizer 140, 146, 152 may have a respective enclosure, and the economizers 140, 146, 152 may therefore be separate components of one another. Further, each of the economizers 140, 146, 152 may include or be associated with one or more valves (e.g., expansion valves) to facilitate pressure drop relative to the respective economizer.
  • valves e.g., expansion valves
  • the auxiliary compressor system 106 may receive each of the vapor refrigerant flows 142, 148, 154 and pressurize the vapor refrigerant flows 142, 148, 154 for discharge toward the condenser 34 (e.g., via the second condenser inlet 110). For example, the auxiliary compressor system 106 may increase a respective pressure of each vapor refrigerant flow 142, 148, 154 toward the pressure of a primary refrigerant flow 159 directed from the primary compressor 102 to reduce a pressure differential between the primary refrigerant flow 159 directed from the primary compressor 102 to the condenser 34 and the pressurized vapor refrigerant flows directed from the auxiliary compressor system 106 to the condenser 34.
  • the auxiliary compressor system 106 may facilitate flow of refrigerant to and/or through the condenser 34. Because the auxiliary compressor system 106 receives input from each of the economizers 140, 146, 152, the auxiliary compressor system 106 operates to increase differently pressurized flows (the vapor refrigerant flows 142, 148, 154) toward the pressure of the primary refrigerant flow 159.
  • the auxiliary compressor system 106 may include a plurality of auxiliary compressors that are in a parallel flow arrangement. That is, each auxiliary compressor may receive a respective one of the vapor refrigerant flows 142, 148, 154 from the economizer system 104.
  • a first auxiliary compressor 160 may receive the first vapor refrigerant flow 142 from the first economizer 140
  • a second auxiliary compressor 162 may receive the second vapor refrigerant flow 148 from the second economizer 146
  • a third auxiliary compressor 164 may receive the third vapor refrigerant flow 154 from the third economizer 152.
  • the auxiliary compressors 160, 162, 164 may pressurize the vapor refrigerant flows 142, 148, 154, respectively, for discharge toward the condenser 110. That is, the first auxiliary compressor 160 may pressurize the first vapor refrigerant flow 142 to provide a first pressurized vapor refrigerant flow 166 for discharge toward the condenser 110, the second auxiliary compressor 162 may pressurize the second vapor refrigerant flow 148 to provide a second pressurized vapor refrigerant flow 168 for discharge toward the condenser 110, and the third auxiliary compressor 164 may pressurize the third vapor refrigerant flow 154 to provide a third pressurized vapor refrigerant flow 170 for discharge toward the condenser 110.
  • the pressurized vapor refrigerant flows 166, 168, 170 may combine to provide a combined pressurized vapor refrigerant flow 172 that may be received by the condenser 34.
  • the respective amounts of pressurization provided by the auxiliary compressors 160 may be different from one another.
  • each auxiliary compressor 160, 162, 164 may pressurize the respective vapor refrigerant flows 142, 148, 154 to approximately the same target pressure (e.g., substantially equal to the pressure of the primary refrigerant flow 159).
  • the respective pressures of the vapor refrigerant flows 142, 148, 154 received by the auxiliary compressors 160, 162, 164 may initially have different pressures.
  • the third economizer 152 provides additional pressure reduction of the second liquid refrigerant flow 150 from the second economizer 146
  • the pressure of the third vapor refrigerant flow 154 may be less than the pressure of the second vapor refrigerant flow 148.
  • a pressure differential between the pressure of the third vapor refrigerant flow 154 and the target pressure may be greater than a pressure differential between the pressure of the second vapor refrigerant flow 148 and the target pressure.
  • the second economizer 146 provides additional pressure reduction of the first liquid refrigerant flow 144 from the first economizer 140
  • the pressure of the second vapor refrigerant flow 148 may be less than the pressure of the first vapor refrigerant flow 142.
  • the pressure differential between the pressure of the second vapor refrigerant flow 148 and the target pressure may be greater than a pressure differential between the pressure of the first vapor refrigerant flow 142 and the target pressure.
  • an amount of pressurization provided by the third auxiliary compressor 164 for the third vapor refrigerant flow 154 may be greater than an amount of pressurization provided by the second auxiliary compressor 162 for the second vapor refrigerant flow 148
  • the amount of pressurization provided by the second auxiliary compressor 162 for the second vapor refrigerant flow 148 may be greater than an amount of pressurization provided by the first auxiliary compressor 160 for the first vapor refrigerant flow 142.
  • an amount of the vapor refrigerant flows 142, 148, 154 provided by the economizer system 104 may be different from one another.
  • the mass flow of the vapor refrigerant flows 142, 148, 154 may be based on the pressure within the condenser 34 and/or within each of the economizers 140, 146, 152, and the volume flow of the vapor refrigerant flows 142, 148, 154 may be based on the vapor density of the vapor density at the respective pressures within the economizers 140, 146, 152.
  • the amount of the first vapor refrigerant flow 142 provided by the first economizer 140 may be greater or smaller than the amount of the second vapor refrigerant flow 148 provided by the second economizer 146, and the amount of the second vapor refrigerant 148 provided by the second economizer 146 may be greater or smaller than the amount of the third vapor refrigerant flow 154 provided by the third economizer 152.
  • the amount of vapor refrigerant flows 142, 148, 154 provided by the economizer system 104 may be substantially similar to one another.
  • Embodiments or specifications of the auxiliary compressors 160, 162, 164 may be selected based on the respective amounts of pressurization to be provided by the auxiliary compressors 160, 162, 164 and/or the respective amounts of the vapor refrigerant flows 142, 148, 154 received by the auxiliary compressors 160, 162, 164.
  • each auxiliary compressor 160, 162, 164 may have a different embodiment (e g., a different size, a different type).
  • the first auxiliary compressor 160 may be relatively larger or smaller than the second auxiliary compressor 162 and/or the third auxiliary compressor 164 to enable receipt and pressurization of the relatively larger or smaller amount, respectively, of the first vapor refrigerant flow 142
  • the third auxiliary compressor 164 may be relatively larger or smaller than the first auxiliary compressor 160 and/or the second auxiliary compressor 162 to enable receipt and pressurization of the relatively larger or smaller amount, respectively, of the third vapor refrigerant flow 154.
  • the auxiliary compressors 160, 162, 164 may be of the same or similar embodiments.
  • Each auxiliary compressor 160, 162, 164 may, for instance, include an oil-free compressor to avoid increasing a cost and/or complexity associated with management of oil and/or lubricant circulated through the vapor compression system 100 (e.g., for cooling of the auxiliary compressors 160, 162, 164). Additionally or alternatively, the auxiliary compressors 160, 162, 164 may include a scroll compressor, a centrifugal compressor, a reciprocating compressor, or any other suitable compressor type. In any case, each auxiliary compressor 160, 162, 164 may be less costly and/or may occupy a smaller physical footprint as compared to the primary compressor 102.
  • the vapor compression system 100 may include a conduit system 174 configured to control flow of the vapor refrigerant flows 142, 148, 154 to the auxiliary compressor system 106.
  • the conduit system 174 may be operated to enable a desirable or suitable flow (e.g., a target flow rate, a target flow velocity) of the vapor refrigerant flows 142, 148, 154 to the auxiliary compressors 160, 162, 164.
  • a first valve 176 of the conduit system 174 may control a flow rate of the first vapor refrigerant flow 142 from the first economizer 140 to the first auxiliary compressor 160
  • a second valve 178 of the conduit system 174 may control a flow rate of the second vapor refrigerant flow 148 from the second economizer 146 to the second auxiliary compressor 162
  • a third valve 180 of the conduit system 174 may control a flow rate of the third vapor refrigerant flow 154 from the third economizer 152 to the third auxiliary compressor 164.
  • the opening of the valves 176, 178, 180 may be adjusted to direct the vapor refrigerant flows 142, 148, 154 in a suitable manner to the auxiliary compressors 160, 162, 164 (e.g., at flows based on design specifications of the auxiliary compressors 160, 162, 164), respectively, to enable efficient and/or desirable operation of the auxiliary compressors 160, 162, 164.
  • the vapor compression system 100 may also include a control system 182 (e.g., the control panel 40 configured to operate the primary compressor 102, a control system separate from the control panel 40), which may be an automation controller and/or an electronic controller.
  • the control system 182 may be configured to control operation of various components of the vapor compression system 100, such as the economizer system 104, the auxiliary compressor system 106, and/or the conduit system 174.
  • the control system 182 may include a memory 184 and processing circuitry 186.
  • the memory 184 may include volatile memory, such as random-access memory (RAM), and/or non-volatile memory, such as read-only memory (ROM), optical drives, hard disc drives, solid-state drives, or any other non-transitory computer-readable medium storing instructions that, when executed, control operation of the vapor compression system 100.
  • the processing circuitry 186 may be configured to execute such instructions stored in the memory 184.
  • the processing circuitry 186 may include one or more application specific integrated circuits (ASICs), one or more field programmable gate arrays (FPGAs), one or more general purpose processors, or any combination thereof.
  • ASICs application specific integrated circuits
  • FPGAs field programmable gate arrays
  • general purpose processors or any combination thereof.
  • control system 182 may be configured to operate each of the economizers 140, 146, 152 to adjust the respective pressure reductions provided by the economizers 140, 146, 152.
  • control system 182 may be configured to operate each of the auxiliary compressors 160, 162, 164, such as by adjusting a stage, a speed, a frequency, and/or any other regulation system (e.g., mechanical system) to provide desirable pressurization of the respective vapor refrigerant flows 142, 148, 154, such as to the target pressure.
  • any other regulation system e.g., mechanical system
  • control system 182 may be configured to operate each of the valves 176, 178, 180, such as by adjusting the respective openings of the valves 176, 178, 180, to adjust the flow rates of the vapor refrigerant flows 142, 148, 154 to the respective auxiliary compressors 160, 162, 164.
  • control system 182 may adjust operation of various components of the vapor compression system 100.
  • the economizer system 104 of the illustrated vapor compression system 100 includes three economizers 140, 146, 152
  • the auxiliary compressor system 106 of the illustrated vapor compression system 100 includes three auxiliary compressors 160, 162, 164
  • the conduit system 174 of the illustrated vapor compression system 100 includes three valves 176, 178, 180
  • the economizer system 104 may include any suitable number of economizers 140, 146, 152
  • the auxiliary compressor system 106 may include any suitable number of auxiliary compressors 160, 162, 164
  • the conduit system 174 may include any suitable number of valves 176, 178, 180.
  • the quantity of economizers 140, 146, 152, the quantity of auxiliary compressors 160, 162, 164, and/or the quantity of valves 176, 178, 180 may correspond to or be equal to one another in some embodiments.
  • the vapor compression system 100 may include two economizers 140, 146, 152, two auxiliary compressors 160, 162, 164, and two valves 176, 178, 180
  • the vapor compression system 100 may include four economizers 140, 146, 152, four auxiliary compressors 160, 162, 164, and four valves 176, 178, 180, and so forth.
  • FIG. 7 is a schematic of an embodiment of the vapor compression system 100 that includes the economizer system 104 and the auxiliary compressor system 106.
  • the economizer system 104 includes the first economizer 140 configured to direct the first vapor refrigerant flow 142 to the auxiliary compressor system 106 and the first liquid refrigerant flow 144 to the second economizer 146, as well as the second economizer 146 configured to direct the second vapor refrigerant flow 148 to the auxiliary compressor system 106 and the second liquid refrigerant flow 150 to the evaporator 38.
  • the auxiliary compressor system 106 includes the first auxiliary compressor 160 configured to receive the first vapor refrigerant flow 142 from the first economizer 140, as well as the second auxiliary compressor configured to receive the second vapor refrigerant flow 148 from the second economizer 146.
  • the conduit system 174 of the vapor compression system 100 includes the first valve 176 configured to control flow of the first vapor refrigerant flow 142 to the first auxiliary compressor 160, as well as the second valve 178 configured to control flow of the second vapor refrigerant flow 148 to the second auxiliary compressor 162.
  • the auxiliary compressors 160, 162 may be in a series flow arrangement.
  • the second auxiliary compressor 162 may pressurize the second vapor refrigerant flow 148 received from the second economizer 146 to provide the second pressurized vapor refrigerant flow 168 as discharge toward the first auxiliary compressor 160.
  • the second pressurized vapor refrigerant flow 168 may combine with the first vapor refrigerant flow 142 directed from the first economizer 140 for intake by the first auxiliary compressor 160.
  • the second auxiliary compressor 162 may increase the pressure of the second vapor refrigerant flow 148 toward the pressure of the first vapor refrigerant flow 142 directed from the first economizer 140 to enable the second pressurized vapor refrigerant flow 168 from the second auxiliary compressor 162 and the first vapor refrigerant flow 142 from the first economizer 140 to flow more readily to the first auxiliary compressor 160.
  • the second pressurized vapor refrigerant flow 168 and the first vapor refrigerant flow 142 that are at substantially the same pressure may flow toward the first auxiliary compressor 160 instead of, for example, back flowing toward the first economizer 140 and/or toward the second auxiliary compressor 162.
  • the first auxiliary compressor 160 may pressurize the second pressurized vapor refrigerant flow 168 and the first vapor refrigerant flow 142 to provide a combined pressurized vapor refrigerant flow 220 for discharge toward the condenser 34.
  • the second vapor refrigerant flow 148 may be pressurized by the second auxiliary compressor 162 and further pressurized by the first auxiliary compressor 160.
  • the auxiliary compressor system 106 may provide multi-stage compression of the second vapor refrigerant flow 148 (e.g., the second auxiliary compressor 162 may be a first compressor stage providing initial pressurization, and the first auxiliary compressor 160 may be a second compressor stage providing further pressurization).
  • the first auxiliary compressor 160 may increase the pressure of the second pressurized vapor refrigerant flow 168 and the first vapor refrigerant flow 142 toward that of the primary refrigerant flow 159 to facilitate flow of the combined pressurized vapor refrigerant flow 220 from the auxiliary compressor system 106 and the primary refrigerant flow 159 from the primary compressor 102 to and/or through the condenser 34.
  • the first auxiliary compressor 160 and the second auxiliary compressor 162 may be of different embodiments.
  • the embodiment of the first auxiliary compressor 160 may be selected to enable receipt and pressurization of both the first vapor refrigerant flow 142 and the second pressurized vapor refrigerant flow 168.
  • the embodiment of the first auxiliary compressor 160 may enable increased refrigerant capacity or flow therethrough as compared to the embodiment of the second auxiliary compressor 162, which may pressurize the second vapor refrigerant flow 148 and not the first vapor refrigerant flow 142.
  • the auxiliary compressor system 106 may include more than two auxiliary compressors 160, 162 in series with one another.
  • the auxiliary compressor system 106 may include the third auxiliary compressor 164 configured to receive and pressurize the third vapor refrigerant flow 154 from the third economizer 152 to provide the third pressurized vapor refrigerant flow 170.
  • the third pressurized vapor refrigerant flow 170 may be discharged toward the second auxiliary compressor 162 and then toward the first auxiliary compressor 160 for further staged pressurization.
  • certain vapor refrigerant flows from the economizer system 104 may be pressurized by multiple auxiliary compressors.
  • FIG. 8 is a schematic of an embodiment of the vapor compression system 100 that includes the economizer system 104 and the auxiliary compressor system 106.
  • the economizer system 104 includes the first economizer 140, which may direct the first liquid refrigerant flow 144 to the evaporator 38.
  • the first economizer 140 may also direct a first vapor refrigerant flow 250 and a second vapor refrigerant flow 252 toward the auxiliary compressor system 106, which may include the first auxiliary compressor 160 and the second auxiliary compressor 162.
  • the first economizer 140 may produce vapor refrigerant by reducing the pressure of the refrigerant received from the condenser 34, and the first economizer 140 may apportion the produced vapor refrigerant to direct the first vapor refrigerant flow 250 toward the first auxiliary compressor 160 and the second vapor refrigerant flow 252 toward the second auxiliary compressor 162.
  • the conduit system 174 may include the first valve 176 configured to control flow of the first vapor refrigerant flow 250 to the first auxiliary compressor 160, as well as the second valve 178 configured to control flow of the second vapor refrigerant flow 252 to the second auxiliary compressor 162.
  • the control system 182 may adjust the openings of the valves 176, 178 to control flow of the vapor refrigerant flows 250, 252 to the auxiliary compressors 160, 162.
  • the auxiliary compressors 160, 162 may be in a parallel flow arrangement. That is, the auxiliary compressors 160, 162 may pressurize the respective vapor refrigerant flows 250, 252 for discharge toward the condenser 34.
  • the first auxiliary compressor 160 may pressurize the first vapor refrigerant flow 250 to provide a first pressurized vapor refrigerant flow 254 and discharge the first pressurized vapor refrigerant flow 254 toward the condenser 34.
  • the second auxiliary compressor 162 may pressurize the second vapor refrigerant flow 252 to provide a second pressurized vapor refrigerant flow 256 and discharge the second pressurized vapor refrigerant flow 256 toward the condenser 34.
  • the first pressurized vapor refrigerant flow 254 and the second pressurized vapor refrigerant flow 256 may combine as a combined pressurized vapor refrigerant flow 258 for intake by the condenser 34.
  • the first pressurized vapor refrigerant flow 254 may bypass flow through the second auxiliary compressor 162, and/or the second pressurized vapor refrigerant flow 256 may bypass flow through the first auxiliary compressor 160.
  • the auxiliary compressors 160, 162 may increase the pressure of the respective vapor refrigerant flows 250, 252 toward the pressure of the primary refrigerant flow 159 discharged by the primary compressor 102 to facilitate directing the primary refrigerant flow 159, the first pressurized vapor refrigerant flow 254, and the second pressurized vapor refrigerant flow 256 to and/or through the condenser 34.
  • the vapor refrigerant provided by the first economizer 140 may be apportioned to more than two auxiliary compressors 160, 162.
  • a third vapor refrigerant flow may be directed from the first economizer 140 toward a third auxiliary compressor for pressurization and discharge toward the condenser 34.
  • FIG. 9 is a schematic of an embodiment of the vapor compression system 100 that includes the economizer system 104 and the auxiliary compressor system 106.
  • the economizer system 104 includes the first economizer 140 and the second economizer 146.
  • the first economizer 140 may be configured to direct the first vapor refrigerant flow 142 to the auxiliary compressor system 106 and the first liquid refrigerant flow 144 to the second economizer 146.
  • the second economizer 146 may be configured to direct the second vapor refrigerant flow 148 to the auxiliary compressor system 106 and the second liquid refrigerant flow 150 to the evaporator 38.
  • the auxiliary compressor system 106 includes the first auxiliary compressor 160, the second auxiliary compressor 162, and the third auxiliary compressor 164.
  • the first auxiliary compressor 160 may be configured to receive the first vapor refrigerant flow 142 from the first economizer 140
  • the second auxiliary compressor 162 may be configured to receive the second vapor refrigerant flow 148 from the second economizer 146.
  • the conduit system 174 includes the first valve 176 configured to control flow of the first vapor refrigerant flow 142 to the first auxiliary compressor 160, as well as the second valve 178 configured to control flow of the second vapor refrigerant flow 148 to the second auxiliary compressor 162.
  • the first auxiliary compressor 160 may pressurize the first vapor refrigerant flow 142 to provide the first pressurized vapor refrigerant flow 166 for discharge toward the condenser 34.
  • the first vapor refrigerant flow 142 may bypass flow through the second auxiliary compressor 162 and the third auxiliary compressor 164.
  • the second auxiliary compressor 162 may pressurize the second vapor refrigerant flow 148 to provide the second pressurized vapor refrigerant flow 168, and the second auxiliary compressor 162 may discharge the second pressurized vapor refrigerant flow 168 toward the third auxiliary compressor 164.
  • the third auxiliary compressor 164 may further pressurize the second pressurized vapor refrigerant flow 168 to provide a third pressurized vapor refrigerant flow 280 for discharge toward the condenser 34.
  • the third pressurized vapor refrigerant flow 280 may bypass flow through the first auxiliary compressor 160.
  • the first pressurized vapor refrigerant flow 166 discharged by the first auxiliary compressor 160 and the third pressurized vapor refrigerant flow 280 discharged by the third auxiliary compressor 164 may combine to form a combined pressurized vapor refrigerant flow 282 for intake by the condenser 34.
  • the first auxiliary compressor 160 may increase the pressure of the first vapor refrigerant flow 142 and the third auxiliary compressor 164 may increase the pressure of the second vapor refrigerant flow 168 to approximately the same pressure, such as a pressure substantially equal to the pressure of the primary refrigerant flow 159.
  • the second auxiliary compressor 162 and the third auxiliary compressor 164 may be in a series flow arrangement with one another, and the first auxiliary compressor 160 may be in a parallel flow arrangement with respect to the second auxiliary compressor 162 and the third auxiliary compressor 164.
  • the second auxiliary compressor 162 and the third auxiliary compressor 164 may operate as a multistage compressor for the second vapor refrigerant flow 148 in which the second vapor refrigerant flow 148 may be pressurized by the second auxiliary compressor 162 and further pressurized by the third auxiliary compressor 164 to achieve a desirable pressure of the third pressurized vapor refrigerant flow 280 for discharge toward the condenser 34.
  • the illustrated auxiliary compressor system 106 includes the second auxiliary compressor 162 and the third auxiliary compressor 164 in a series flow arrangement
  • the first auxiliary compressor 160 may be in a series flow arrangement with an additional auxiliary compressor (e.g., a fourth auxiliary compressor).
  • more than two auxiliary compressors e.g., the second auxiliary compressor 162, the third auxiliary compressor 164, and a fourth auxiliary compressor
  • FIG. 10 is a schematic of an embodiment of the vapor compression system 100 that includes the economizer system 104 and the auxiliary compressor system 106.
  • the economizer system 104 includes the first economizer 140 configured to direct the first vapor refrigerant flow 142 to the auxiliary compressor system 106 and the first liquid refrigerant flow 144 to the second economizer 146, as well as the second economizer 146 configured to direct the second vapor refrigerant flow 148 to the auxiliary compressor system 106 and the second liquid refrigerant flow 150 to the evaporator 38.
  • the auxiliary compressor system 106 may include the first auxiliary compressor 160, the second auxiliary compressor 162, and the third auxiliary compressor 164.
  • the first auxiliary compressor 160 may receive and pressurize the first vapor refrigerant flow 142 to provide the first pressurized vapor refrigerant flow 166
  • the second auxiliary compressor 162 may receive and pressurize the second vapor refrigerant flow 148 to provide the second pressurized vapor refrigerant flow 168.
  • the first pressurized vapor refrigerant flow 166 and the second pressurized vapor refrigerant flow 168 may combine for intake by the third auxiliary compressor 164.
  • the pressure of the first pressurized vapor refrigerant flow 166, as effectuated by the first auxiliary compressor 106, and the second pressurized vapor refrigerant flow 168, as effectuated by the second auxiliary compressor 162, may be substantially equal to one another to facilitate flow toward the third auxiliary compressor 164.
  • the third auxiliary compressor 164 may pressurize the first pressurized vapor refrigerant flow 166 and the second pressurized vapor refrigerant flow 168 to provide a combined pressurized vapor refrigerant flow 310 for discharge toward the condenser 34.
  • the third auxiliary compressor 164 may further increase the pressure of the first pressurized vapor refrigerant flow 166 and the second pressurized vapor refrigerant flow 168 toward that of the primary refrigerant flow 159.
  • first auxiliary compressor 160 and the second auxiliary compressor 162 may be in a parallel flow arrangement with one another, while each of the first auxiliary compressor 160 and the second auxiliary compressor 162 may be in a series flow arrangement with respect to the third auxiliary compressor 164
  • each of the auxiliary compressors 160, 162, 164 may operate as one of a plurality of stages for pressurizing the first vapor refrigerant flow 142 and/or the second vapor refrigerant flow 148.
  • the first auxiliary compressor 160 may operate as a first stage for providing initial pressurization of the first vapor refrigerant flow 142
  • the second auxiliary compressor 162 may operate in parallel as a first stage for providing initial pressurization of the second vapor refrigerant flow 148
  • the third auxiliary compressor 164 may operate as a second stage for providing additional pressurization of the first vapor refrigerant flow 142 and the second vapor refrigerant flow 148 to achieve a desirable pressure of the combined pressurized vapor refrigerant flow 310 for discharge toward the condenser 34.
  • the auxiliary compressor system 106 may include an additional auxiliary compressor in a series flow arrangement.
  • a fourth auxiliary compressor may provide further pressurization of the refrigerant discharged by the third auxiliary compressor 164.
  • the fourth auxiliary compressor may pressurize the combined pressurized vapor refrigerant flow 310 discharged by the third auxiliary compressor 164.
  • the auxiliary compressor system 106 may include a fourth auxiliary compressor in a parallel flow arrangement.
  • the economizer system 104 may include the third economizer 152, the fourth auxiliary compressor may receive the third vapor refrigerant flow 154 from the third economizer 152, pressurize the third vapor refrigerant flow 154 to provide the third pressurized vapor refrigerant flow 170, and discharge the third pressurized vapor refrigerant flow 170 toward any of the other auxiliary compressors (e.g., the second auxiliary compressor 162, the third auxiliary compressor 164) that are in the series flow arrangement.
  • the other auxiliary compressors e.g., the second auxiliary compressor 162, the third auxiliary compressor 164
  • FIG. 11 is a schematic of an embodiment of the vapor compression system 100 that includes the economizer system 104 and the auxiliary compressor system 106.
  • the economizer system 104 includes the first economizer 140, which may direct the first liquid refrigerant flow 144 to the evaporator 38 and apportion the first vapor refrigerant flow 250 and the second vapor refrigerant flow 252 toward the auxiliary compressor system 106.
  • the auxiliary compressor system 106 may include the first auxiliary compressor 160, the second auxiliary compressor 162, and the third auxiliary compressor 164.
  • the first auxiliary compressor 160 may receive and pressurize the first vapor refrigerant flow 250 to provide the first pressurized vapor refrigerant flow 254, and the second auxiliary compressor 162 may receive and pressurize the second vapor refrigerant flow 252 to provide the second pressurized vapor refrigerant flow 256.
  • the first auxiliary compressor 160 and the second auxiliary compressor 162 may discharge the first pressurized vapor refrigerant flow 254 and the second vapor refrigerant flow 256, respectively, toward the third auxiliary compressor 164.
  • the first pressurized vapor refrigerant flow 254 and the second vapor refrigerant flow 256 may combine for intake by the third auxiliary compressor 164.
  • the pressure of the first pressurized vapor refrigerant flow 254, as effectuated by the first auxiliary compressor 160, and the pressure of the second vapor refrigerant flow 256, as effectuated by the second auxiliary compressor 162, may be substantially equal to one another to facilitate flow to the third auxiliary compressor 164.
  • the third auxiliary compressor 164 may pressurize the first pressurized vapor refrigerant flow 254 and the second pressurized vapor refrigerant flow 256 to provide a combined pressurized vapor refrigerant flow 340.
  • the third auxiliary compressor 164 may increase the pressure of the first pressurized vapor refrigerant flow 254 and the second pressurized vapor refrigerant flow 256 toward the pressure of the primary refrigerant flow 159 to facilitate flow of the primary refrigerant flow 159 and the combined pressurized vapor refrigerant flow 340 to and/or through the condenser 34.
  • first auxiliary compressor 160 and the second auxiliary compressor 162 may be in a parallel flow arrangement with one another, while each of the first auxiliary compressor 160 and the second auxiliary compressor 162 may be in a series flow arrangement with respect to the third auxiliary compressor 164. That is, each of the first auxiliary compressor 160 and the second auxiliary compressor 162 may operate as a first stage for pressurizing the vapor refrigerant (e.g., the first vapor refrigerant flow 250, the second vapor refrigerant flow 252) from the first economizer 140, and the third auxiliary compressor 164 may operate as a second stage for providing additional pressurization of the vapor refrigerant from the first economizer 140.
  • the vapor refrigerant e.g., the first vapor refrigerant flow 250, the second vapor refrigerant flow 252
  • the auxiliary compressor system 106 may also include any other suitable number of auxiliary compressors in the series flow arrangement (e.g., three or more stages of auxiliary compressors) and/or in the parallel flow arrangement. Indeed, an auxiliary compressor (e.g., the first auxiliary compressor 160) that is a part of the parallel flow arrangement may discharge pressurized refrigerant toward any of the auxiliary compressors in the series flow arrangement.
  • an auxiliary compressor e.g., the first auxiliary compressor 160
  • the parallel flow arrangement may discharge pressurized refrigerant toward any of the auxiliary compressors in the series flow arrangement.
  • FIG. 12 is a schematic of an embodiment of the vapor compression system 100 that includes the economizer system 104 and the auxiliary compressor system 106.
  • the economizer system 104 includes the first economizer 140, which may direct the first liquid refrigerant flow 144 toward the second economizer 146, the first vapor refrigerant flow 250 toward the auxiliary compressor system 106, and the second vapor refrigerant flow 252 toward the auxiliary compressor system 106.
  • the second economizer 146 may direct the second liquid refrigerant flow 150 toward the evaporator 38 and a third vapor refrigerant flow 370 toward the auxiliary compressor system 106.
  • the auxiliary compressor system 106 may include the first auxiliary compressor 160, the second auxiliary compressor 162, and the third auxiliary compressor 164.
  • the first auxiliary compressor 160 may receive and pressurize the first vapor refrigerant flow 250 to provide the first pressurized vapor refrigerant flow 254 for discharge toward the condenser 34
  • the second auxiliary compressor 162 may receive and pressurize the second vapor refrigerant flow 252 to provide the second pressurized vapor refrigerant flow 256 for discharge toward the condenser 34
  • the third auxiliary compressor 164 may receive and pressurize the third vapor refrigerant flow 370 to provide a third pressurized vapor refrigerant flow 372 for discharge toward the condenser 34.
  • the first pressurized vapor refrigerant flow 254, the second pressurized vapor refrigerant flow 256, and/or the third pressurized vapor refrigerant flow 372 may combine to provide a combined pressurized vapor refrigerant flow 374 for intake by the condenser 34.
  • the conduit system 174 may include the first valve 176 configured to control flow of the first vapor refrigerant flow 250 to the first auxiliary compressor 160, the second valve 178 configured to control flow of the second vapor refrigerant flow 252 to the second auxiliary compressor 162, and a third valve 376 configured to control flow of the third vapor refrigerant flow 370 to the third auxiliary compressor 164.
  • the auxiliary compressors 160, 162, 164 may pressurize the vapor refrigerant flows 250, 252, 370 toward the pressure of the primary refrigerant flow 159.
  • the vapor refrigerant flow provided by the economizers 140, 146 may be different from one another.
  • a total amount of overall vapor refrigerant flow e.g., a combination of the first refrigerant flow 250 and the second refrigerant flow 252
  • the first economizer 140 may be greater or smaller than the amount of the third vapor refrigerant flow 370 provided by the second economizer 146.
  • the amount of the first vapor refrigerant flow 250 and/or the second vapor refrigerant flow may be significantly less than the total amount of overall vapor refrigerant flow.
  • the total amount of overall vapor refrigerant flow may be greater than the amount of the third vapor refrigerant flow 370, the amount of the first vapor refrigerant flow 250 and the second vapor refrigerant flow 252 may be approximately equal to one another and/or to the third vapor refrigerant flow 370.
  • first auxiliary compressor 160 and/or the second auxiliary compressor 162 may be selected to enable receipt and pressurization of a relatively smaller first vapor refrigerant flow 250 and a relatively smaller second vapor refrigerant flow 252, respectively, and instead of, as an example, a relatively larger total amount of overall vapor refrigerant flow.
  • FIGS. 13-16 are graphical illustrations of vapor compression cycles for different vapor compression systems, which correspond to various possible configurations of the present disclosure.
  • each of FIGS. 13-16 includes an x-axis 302 corresponding to enthalpy (“H” or “h”) and a y-axis 304 corresponding to log pressure (“p”).
  • the graph 300 of FIG. 13 corresponds to an embodiment in which the cycle includes at least a primary compressor, two economizer stages, and two auxiliary compressor stages corresponding to the two economizer stages and in parallel flow.
  • the cycle includes at least a primary compressor, two economizer stages, and two auxiliary compressor stages corresponding to the two economizer stages, where the two auxiliary compressor stages are in series flow (e g., similar to or the same as the embodiment illustrated in FIG. 7).
  • the graph 500 of FIG. 15 corresponds to an embodiment in which the cycle includes at least a primary compressor, an economizer stage, and two auxiliary compressor stages corresponding to the economizer stage, where the two auxiliary compressor stages are in parallel flow. That is, the graph 500 of FIG. 15 may correspond to the embodiment illustrated in FIG. 8, which includes the above-described features, and/or the embodiment illustrated in FIG. 12, which includes the above-described features in addition to a second economizer stage and a third auxiliary compressor stage corresponding to the second economizer stage, where the first, second, and third auxiliary compressor stages are in parallel flow.
  • the cycles includes at least a primary compressor, first and second economizer stages, first and second auxiliary compressor stages corresponding to the first and second economizer stages and in series flow (e.g., where the first auxiliary compressor stage is connected between the first economizer stage, such as a low pressure economizer, and the second economizer stage, such as a high pressure economizer, and where the second auxiliary compressor stage is connected between the second economizer stage to the condenser), and a third compressor stage in parallel flow connected from the first economizer stage to the condenser.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne un système de chauffage, de ventilation, de climatisation et/ou de réfrigération (CVC&R) (100), comprenant un système d'économiseur (104) conçu pour réduire une pression d'un fluide frigorigène pour fournir un premier écoulement de fluide frigorigène en phase vapeur et un second écoulement de fluide frigorigène en phase vapeur. Le système CVC&R (100) comprend également un système de compresseur auxiliaire (106) qui a un premier compresseur auxiliaire (160) conçu pour recevoir le premier écoulement de fluide frigorigène en phase vapeur provenant du système d'économiseur (104) et mettre sous pression le premier écoulement de fluide frigorigène en phase vapeur pour fournir un premier écoulement de fluide frigorigène en phase vapeur sous pression et un second compresseur auxiliaire (162) conçu pour recevoir le second écoulement de fluide frigorigène en phase vapeur provenant du système d'économiseur (104) et mettre sous pression le second écoulement de fluide frigorigène en phase vapeur pour fournir un second écoulement de fluide frigorigène en phase vapeur sous pression. Le système de compresseur auxiliaire (106) est conçu pour évacuer un écoulement de fluide frigorigène en phase vapeur combiné comprenant le premier écoulement de fluide frigorigène en phase vapeur sous pression et le second écoulement de fluide frigorigène en phase vapeur sous pression vers un condenseur (34) du système CVC&R (100).
EP23824668.0A 2022-06-17 2023-06-16 Système de compresseur pour système de chauffage, de ventilation, de climatisation et/ou de réfrigération Pending EP4540559A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US202263353343P 2022-06-17 2022-06-17
PCT/US2023/025616 WO2023244833A1 (fr) 2022-06-17 2023-06-16 Système de compresseur pour système de chauffage, de ventilation, de climatisation et/ou de réfrigération

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EP4540559A1 true EP4540559A1 (fr) 2025-04-23

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EP (1) EP4540559A1 (fr)
KR (1) KR20250022861A (fr)
CN (1) CN119497809A (fr)
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7096681B2 (en) * 2004-02-27 2006-08-29 York International Corporation System and method for variable speed operation of a screw compressor
JP5400796B2 (ja) * 2007-12-28 2014-01-29 ジョンソン コントロールズ テクノロジー カンパニー 蒸気圧縮システム及び同システムを作動させる方法
WO2021011562A1 (fr) * 2019-07-15 2021-01-21 Johnson Controls Technology Company Système de condenseur à compresseurs multiples
KR102367790B1 (ko) * 2019-12-31 2022-02-24 엘지전자 주식회사 냉각 효율 향상 기능을 갖는 터보 냉동기
CN116399047A (zh) * 2020-03-24 2023-07-07 浙江盾安机电科技有限公司 冷水机组控制方法、装置、可读存储介质及冷水机组

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CN119497809A (zh) 2025-02-21
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