WO2019178641A1 - Système de banc de réfrigération transcritique à compression parallèle et intégré à une climatisation et procédés de commande associés - Google Patents

Système de banc de réfrigération transcritique à compression parallèle et intégré à une climatisation et procédés de commande associés Download PDF

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Publication number
WO2019178641A1
WO2019178641A1 PCT/AU2019/050245 AU2019050245W WO2019178641A1 WO 2019178641 A1 WO2019178641 A1 WO 2019178641A1 AU 2019050245 W AU2019050245 W AU 2019050245W WO 2019178641 A1 WO2019178641 A1 WO 2019178641A1
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WO
WIPO (PCT)
Prior art keywords
temperature
feeding
group
control valve
pressure
Prior art date
Application number
PCT/AU2019/050245
Other languages
English (en)
Inventor
Jean TUYAU
Original Assignee
Avance Energy Solutions Pty Ltd
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
Priority claimed from AU2018900957A external-priority patent/AU2018900957A0/en
Application filed by Avance Energy Solutions Pty Ltd filed Critical Avance Energy Solutions Pty Ltd
Priority to AU2019238571A priority Critical patent/AU2019238571A1/en
Publication of WO2019178641A1 publication Critical patent/WO2019178641A1/fr

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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • This invention relates generally to an air-conditioning integrated parallel compression transcritical refrigeration rack system. More particularly, this invention relates to a particular air- conditioning integration configuration and, in embodiments, control methodology thereof, which eliminates the need for a separate suction group, associated componentry and controllers therefor which reduces capital expenditure and installation cost.
  • Figure 1 illustrates a prior art CO2 parallel compression refrigeration rack system 100 with optional heat recovery.
  • the standard refrigeration cycle requires that refrigerant be condensed into a liquid at section 102 to pool in a liquid receiver 103 for distribution to the various electronically controlled expansion devices (EXV) 104, 105, 106 at the actual point of cooling, such as cooling coils of the refrigeration cases 107, 108, air conditioning coils and the like.
  • EXV electronically controlled expansion devices
  • An EXV requires liquid coolant input for expansion.
  • Any flash gas within the reservoir 103 is recycled using a flash gas bypass system which may comprise a flash gash bypass valve (FGBV) 109 and/or parallel compression (PC) group 110.
  • FGBV flash gash bypass valve
  • PC parallel compression
  • the system 100 comprises two suction groups comprising a medium temperature (MT) and low-temperature (LT) suction groups.
  • MT medium temperature
  • LT low-temperature
  • Evaporated refrigerant from the EXVs 105, 106 is re-compressed utilising dedicated compressor groups 111, 112 for each suction group.
  • the system 100 comprises MT compressor group 111 for MT suction line 114.
  • the MT suction line may operate at -6°C, for example.
  • the system 100 comprises LT compressor group 112 for LT suction line 113.
  • the LT suction line 113 may operate at -27°C, for example.
  • the LT compressors 112 "boosts" into the MT suction line 114, hence the name “booster system”.
  • Boosting allows the LT suction group to achieve very low SSTs at very high efficiencies since the LT compressors 112 rejects heat into an already relatively cool MT suction line 114.
  • the parallel and MT compressor groups 110, 111 feed into high-temperature (HT) line 119 from which heat may be scavenged utilising a water heat exchanger 120.
  • HT high-temperature
  • the HT line feeds back into a condenser/gas cooler 116 which outputs cooled refrigerant.
  • the condenser 116 condenses the refrigerant into a liquid which is fed directly into the liquid receiver 103.
  • the CO2 output from the gas cooler 116 may be in supercritical state (being above critical temperature 31.10 °C and critical pressure 7.39 MPa).
  • supercritical CO2 refrigerant acts like a gas in that it expands to fill containers but exhibits a density typical of a liquid.
  • transcritical CO2 refrigeration systems utilise an expansion/metering device between the gas cooler 116 and the liquid receiver 103 referred to as the electronically controlled high-pressure control valve (HPCV) 115.
  • HPCV electronically controlled high-pressure control valve
  • the HPCV 115 receives the high-pressure supercritical CC from the gas cooler 116 and rapidly expands the CC as it passes, creating a substantial pressure/temperature drop such that a portion of the CO2 condenses into useful liquid for the liquid receiver 103.
  • Flash gas associated therewith which is useless for refrigeration, is recycled from the liquid receiver 103 either through the FGBV 109 into the MT line 114 for recompression and reuse, or for larger flash gas loads, through the PC group 110 into the HT line 119.
  • the HPCV 115 is controlled utilising an HPCV controller (not shown) to maintain the requisite gas cooler pressure at section 102 and liquid levels of the liquid receiver 103.
  • the HPCV controller may derive efficiencies by "floating" (i.e. increasing) the pressure within the liquid receiver 103.
  • AC integration 101 typically entails the creation of a further AC suction group by the addition of a braised plate heat exchanger (AC BHPE) 117 for chilling water of the air-conditioning integration 101 and an electronically controlled AC EXV 104 feeding the AC BHPE 117.
  • AC BHPE braised plate heat exchanger
  • AC integration 101 may therefore involve three suction groups, comprising the LT suction group, MT suction group and the flash gas management and air-conditioning suction group (AC suction group).
  • the LT suction group evaporates at -27°C
  • the MT suction group at -6°C
  • the AC suction group at 3.3°C.
  • the AC EXV 104 for the AC BPHE 117 similarly requires liquid coolant from the liquid receiver 103 which is why the AC EXV 104 must be located downstream from the liquid receiver 103.
  • an electronic pressure regulator (EPR) 118 is required to regulate any pressure/temperature differential of greater than approx. 1-2°C therebetween.
  • the capacity of the PC compressor group 110 is increased to account for the additional load of the air-conditioning system 101.
  • the present invention seeks to provide a refrigeration system, which will overcome or substantially ameliorate at least some of the deficiencies of the prior art, or to at least provide an alternative.
  • an air-conditioning integrated parallel compression transcritical refrigeration rack system having the characterising configuration of an air-conditioning heat exchanger (AC BPHE) upstream of the liquid receiver as is shown in Figure 2.
  • AC BPHE air-conditioning heat exchanger
  • the upstream AC BPHE is inserted between the HPCV 115 and the liquid receiver 103.
  • Such a configuration advantageously dual-purposes the HPCV 115 in acting both as the supercritical CO2 high pressure control valve and the AC expansion device, thereby reducing system componentry.
  • the upstream AC BHPE may be inserted/retrofitted into an existing refrigeration plant more easily as compared to the installation of a further dedicated AC suction group
  • the HPCV controller for the present configuration may be controlled according to a lower control bound such that the AC BHPE input pressure/temperature does not drop below approximately 1°C so as to avoid physical damage of the AC BPHE via freezing of the water-side of the cooling circuit 101.
  • the HPCV controller may be controlled at an upper control bound such that floating of the liquid receiver 103 does not retard efficient operation of the air-conditioning integration 101.
  • the chilled water circuit of the air-conditioning integration 101 may enter the AC BPHE at approximately 13°C and exit at approximately 7°C.
  • the chilled water circuit may comprise an input valve/pump and an output temperature sensor to control the flow rate of water through the AC BPHE which may therefore be adjusted according to AC load using an AC integration controller.
  • the AC integration controller may signal the HPCV controller to reduce floating by reducing the liquid reservoir input temperature/pressure. For example, should the flowrate/low control have increased the flowrate of water through the upstream AC BPHE to substantially a maximum flowrate amount yet be unable to efficiently achieve cooling required for the present AC demand, the AC integration controller may signal the HPCV controller to drop the AC BPHE pressure/temperature until such time that AC demand can be met. As reduction of AC BPHE pressure/temperature hinders reservoir floating, the HPCV controller may be configured for maximising floating while meeting a dynamic maximum AC BPHE pressure/temperature.
  • air- conditioning integrated parallel compression transcritical refrigeration rack system comprising: a high- pressure control valve feeding a liquid receiver; the liquid receiver feeding at least one suction group; the at least one suction group feeding a gas cooler; the gas cooler feeding the high-pressure control valve, wherein the system comprises an AC heat exchanger between the high-pressure control valve and the liquid receiver.
  • the system may further comprise a high-pressure control valve controller for controlling the high-pressure control valve according to the pressure/temperature requirements of the liquid receiver and wherein the high-pressure control valve controller may be further configured for controlling the pressure/temperature of the AC heat exchanger.
  • the controller may be configured for controlling the high-pressure control valve according to a lower operational control bound such that the pressure/temperature of the AC heat exchanger does not decrease below a lower threshold.
  • the lower threshold may be approximately 1°C.
  • the controller may be configured for controlling the high-pressure control valve according to an upper operational control bound such that the pressure/temperature of the AC heat exchanger may be sufficient to meet the dynamic AC load thereon.
  • the system may further comprise an AC integration controller configured for controlling flowrate through the AC heat exchanger according to dynamic AC load.
  • the upper operational control bound corresponds with a flowrate threshold.
  • the at least one suction group feeds into at least one compressor group which feeds into a high-temperature line which feeds into the gas cooler and wherein the system further may comprise a heat exchanger operably coupled to the high-temperature line.
  • the at least one suction group may comprise a medium temperature suction group comprising: a medium temperature compressor group feeding into a high-temperature line which feeds into the gas cooler; a medium temperature suction line feeding into the medium temperature compressor group; and a medium temperature electronically controlled expansion valve feeding into the medium temperature suction line; and a low temperature suction group comprising: a low temperature compressor group feeding into the medium temperature suction line; a low temperature suction line feeding into the low temperature compressor group; and a low temperature electronically controlled expansion valve feeding into the low temperature suction line.
  • the medium temperature suction line may operate at approximately -6°C.
  • the low temperature suction line may operate at approximately -27°C.
  • the system may further comprise a flash gas bypass system feeding from the liquid receiver.
  • the flash gas bypass system may comprise a flash gas bypass valve interfacing the liquid receiver and the medium temperature suction line.
  • the flash gas bypass system may comprise a parallel compressor group interfacing the liquid receiver and the high-temperature suction line.
  • Figure 1 illustrates a typical prior art CO2 parallel compression refrigeration rack system with optional heat recovery
  • Figure 2 illustrates an air-conditioning integrated parallel compression transcritical refrigeration rack system in accordance with an embodiment. Description of Embodiments
  • Figure 2 illustrates an air-conditioning integrated parallel compression transcritical refrigeration rack system 200 in accordance with an embodiment.
  • the system 200 typically employs CO2 but may employ other transcritical refrigerants.
  • the system 200 comprises an HPCV 115 feeding into a liquid reservoir 103.
  • the liquid reservoir 103 feeds at least one suction group which, in turn, feed into a gas cooler 116.
  • the system 200 is characterised in comprising an AC BPHE 121 upstream of the liquid receiver 103 for an AC integration 101.
  • the system 200 comprises the AC BPHE 121 located between the HPCV 115 and the liquid reservoir 103.
  • the HPCV 115 serves dual purpose in 1) condensing the supercritical CO2 from the gas cooler 116 into liquid for the requirements of the liquid receiver 103 and as the expansion device for cooling the AC BPHE 112.
  • the AC integration 101 may utilise a chilled water circuit which may feed the AC BPHE 121 at approximately 13°C for cooling to approximately 7°C.
  • the AC integration 101 may comprise a valve/pump 122 for regulating the flow rate of water through the AC BPHE 121.
  • the AC integration 101 may employ an AC integration controller configured for controlling the flow rate of water through the AC BPHE 121 according to dynamic AC load requirements.
  • the AC integration controller may take readings from a temperature sensor 122 for control purposes.
  • the AC integration controller may increase flowrate through the AC BPHE 121 and vice versa.
  • system 200 may comprise an HPCV controller for controlling the HPCV 115.
  • the HPCV controller primarily controls the HPCV 115 according to the requisite liquid level requirements of the liquid reservoir 103 which dynamically vary according to the demands of the downstream EXVs 105, 106.
  • the HPCV controller additionally controls the HPCV 115 according to the pressure/temperature requirements of the AC BPHE 121.
  • the HPCV controller may control the HPCV 115 according to a lower control bound such that the pressure/temperature of the AC BPHE 121 does not fall beneath a lower threshold set point, such as approximately 1°C so as to not physically damage the AC BPHE 121.
  • the HPCV controller may control the HPCV 115 according to a dynamically changing upper operational pressure/temperature setpoint of the AC BPHE 121.
  • the dynamic upper operational pressure/temperature setpoint of the AC BPHE 121 may vary dynamically according to the current AC load of the AC integration 101.
  • the HPCV controller may control the HPCV 115 to maximise floating so as to derive operational efficiencies for the refrigeration circuits yet while meeting the dynamic upper operational pressure/temperature setpoint of the AC BPHE 121 such that the AC BPHE 121 is able to meet the load requirements of the AC integration 101.
  • the dynamic upper operational pressure/temperature setpoint of the AC BPHE may be dictated by the maximum flowrate through the AC BPHE 121.
  • the AC controller may signal the HPC via the controller to decrease the pressure/temperature of the AC BPHE 121.
  • the system 200 comprises two suction groups comprising the MT suction group and the LT suction group.
  • the MT suction group may comprise an MT compressor group 111 feeding into the HT line 119 and MT suction line 114 which feeds into the MT compressor group 11. Furthermore, an MT EXV 105 may feed into the MT suction line 114.
  • the LT suction group may comprise an LT compressor group 112 feeding into the MT suction line 114.
  • An LT suction line 113 may feed into the LT compressor group 112 and a low temperature EXV of the 106 may feed into the LT suction line 113.
  • the LT suction line 113 may feed via a passive LT liquid subcooler to reduce or eliminate flash gas input to the LT EXV 106.

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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)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un système de banc de réfrigération transcritique à compression parallèle et intégré à une climatisation, lequel système qui comprend une vanne de commande haute pression alimentant un réservoir de liquide. Le réservoir de liquide alimente au moins un groupe d'aspiration et ledit au moins un groupe d'aspiration alimente un refroidisseur de gaz. Le refroidisseur de gaz alimente la vanne de commande haute pression. Le système comprend un échangeur de chaleur de climatisation entre la vanne de commande haute pression et le réservoir de liquide. Le système élimine ainsi le besoin d'un groupe d'aspiration séparé, d'éléments et dispositifs de commande associés, ce qui réduit la dépense d'investissement et le coût d'installation.
PCT/AU2019/050245 2018-03-23 2019-03-21 Système de banc de réfrigération transcritique à compression parallèle et intégré à une climatisation et procédés de commande associés WO2019178641A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2019238571A AU2019238571A1 (en) 2018-03-23 2019-03-21 An air-conditioning integrated parallel compression transcritical refrigeration rack system and control methods thereof

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2018900957A AU2018900957A0 (en) 2018-03-23 An air-conditioning integrated parallel compression transcritical refrigeration rack system and control methods thereof
AU2018900957 2018-03-23

Publications (1)

Publication Number Publication Date
WO2019178641A1 true WO2019178641A1 (fr) 2019-09-26

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Application Number Title Priority Date Filing Date
PCT/AU2019/050245 WO2019178641A1 (fr) 2018-03-23 2019-03-21 Système de banc de réfrigération transcritique à compression parallèle et intégré à une climatisation et procédés de commande associés

Country Status (2)

Country Link
AU (1) AU2019238571A1 (fr)
WO (1) WO2019178641A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
CN101668998A (zh) * 2007-02-02 2010-03-10 开利公司 增强式制冷系统

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5245836A (en) * 1989-01-09 1993-09-21 Sinvent As Method and device for high side pressure regulation in transcritical vapor compression cycle
CN101668998A (zh) * 2007-02-02 2010-03-10 开利公司 增强式制冷系统

Also Published As

Publication number Publication date
AU2019238571A1 (en) 2020-10-08

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