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WO2008079128A1 - Système de réfrigération à base de co2 équipé de compresseurs en tandem, d'un détendeur et d'un économiseur - Google Patents

Système de réfrigération à base de co2 équipé de compresseurs en tandem, d'un détendeur et d'un économiseur Download PDF

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Publication number
WO2008079128A1
WO2008079128A1 PCT/US2006/049286 US2006049286W WO2008079128A1 WO 2008079128 A1 WO2008079128 A1 WO 2008079128A1 US 2006049286 W US2006049286 W US 2006049286W WO 2008079128 A1 WO2008079128 A1 WO 2008079128A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressors
set forth
expander
refrigerant system
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.)
Ceased
Application number
PCT/US2006/049286
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English (en)
Inventor
Alexander Lifson
Michael F. Taras
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.)
Carrier Corp
Original Assignee
Carrier Corp
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 Carrier Corp filed Critical Carrier Corp
Priority to US12/515,471 priority Critical patent/US20100071391A1/en
Priority to CNA2006800568348A priority patent/CN101568770A/zh
Priority to PCT/US2006/049286 priority patent/WO2008079128A1/fr
Priority to EP06846056A priority patent/EP2097686A4/fr
Publication of WO2008079128A1 publication Critical patent/WO2008079128A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—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
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • 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
    • F25B2400/07—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
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • 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

Definitions

  • This application relates to a refrigerant system wherein an expander is utilized to provide a more efficient expansion process, by recapturing energy from this expansion process and utilizing that energy to power at least one system component.
  • a portion of refrigerant is tapped from a location in the expander at which it has been at least partially expanded, and the tapped refrigerant is then utilized to subcool a main refrigerant flow in an economizer heat exchanger.
  • a single expander can provide both main and economizer expansion device functions for the refrigerant system, and enhance these main and economizer expansion device functions.
  • the refrigerant system includes tandem compressors only some of which may be economized.
  • the refrigerant system may be charged with CO 2 refrigerant that, at least for a portion of the time, may operate in a transcritical cycle.
  • Refrigerant compressors circulate a refrigerant through a refrigerant system to condition a secondary fluid.
  • a compressor compresses a refrigerant and delivers it to a first heat exchanger.
  • Refrigerant from the first heat exchanger passes through an expansion device, in which its pressure and temperature are reduced. Downstream of the expansion device, a refrigerant passes through a second heat exchanger, and then back to the compressor.
  • a portion of refrigerant is tapped from a main refrigerant stream downstream of the first heat exchanger.
  • This tapped refrigerant is passed through an expansion device, to be expanded to an intermediate pressure and temperature, and then this partially expanded tapped refrigerant passes in heat exchange relationship with a main refrigerant flow in an economizer heat exchanger.
  • the main refrigerant is subcooled such that it will have a greater thermodynamic potential when it reaches the second heat exchanger.
  • the tapped refrigerant typically in a superheated thermodynamic state, is returned to an intermediate compression point in the compressor downstream of the economizer heat exchanger.
  • Tandem compressors allow the control of the overall capacity provided by the refrigerant system by selectively engaging the tandem compressors. Further, all or only some of the tandem compressors may be economized, and the economizer function may be activated or deactivated to precisely match capacity delivered by a refrigerant system to thermal load demands in the conditioned space.
  • Another feature utilized in refrigerant systems is the use of an expander to provide a more efficient so-called active expansion process (this process can closely follow an isentropic line rather than isenthalpic line for so-called passive expansion devices such as expansion valves and fixed restriction devices).
  • the expanders could be of various designs such as centrifugal, scroll, rotary, screw, shaft-connected piston, free-piston or any other type.
  • CO 2 also known as carbon dioxide or R744
  • R744 carbon dioxide
  • CO 2 refrigerant can benefit greatly from any of the above-mentioned system enhancement options, especially in transcritical applications.
  • no refrigerant system to date has included an expander, tandem compressors and an economizer cycle combined together to provide a powerful combination of operational options and enhancement features.
  • an expander is utilized to provide a more efficient active expansion process to potentially recapture energy from this expansion process, and utilize that energy to power at least one refrigerant system component.
  • the expander increases capacity and enhances efficiency of a refrigerant system through a more efficient expansion process (reduced irreversible losses) and recovering, at least partially, the expansion process energy.
  • a portion of refrigerant that has been at least partially expanded in the expander (or through the first stage of the expander) is tapped and passed through an economizer heat exchanger in heat exchange relationship with a main refrigerant flow.
  • This tapped refrigerant is injected back into the compressor (a single compressor or a multi-stage compressor system consisting of compressors connected in series) at some intermediate pressure. All or only some of the compressors may be economized. Exiting the economizer heat exchanger, the main refrigerant has a higher thermodynamic potential that allows for enhanced refrigerant system performance.
  • the refrigerant system includes at least two tandem compressors that, along with the economizer function, allow for efficient system unloading and precise matching of delivered system capacity to thermal load demands in the conditioned space.
  • the expander may transfer the recovered energy from the expansion process, directly or indirectly through an energy conversion device, to at least partially power one of the tandem compressors.
  • the refrigerant system as disclosed, may use a natural refrigerant such as CO 2 .
  • the proposed refrigerant system enhancements are particularly beneficial for the CO 2 refrigerant system operating in a transcritical cycle.
  • economizer cycle provides the ability to closely tailor the provided capacity of the refrigerant system to thermal load demands in the conditioned space and to enhance performance of the refrigerant system through a more efficient expansion process, economizer cycle and energy recovery, especially for a CO 2 refrigerant system operating in a transcritical cycle.
  • a portion of refrigerant is tapped form a single intermediate tap in the expander to flow through the economizer heat exchanger in the economizer cycle.
  • Figure 1 shows a schematic of a first inventive refrigerant system.
  • Figure 2 shows a second schematic.
  • Figure 3A shows a third schematic.
  • Figure 3B shows an alternate tandem compressor configuration for the refrigerant system depicted in Figure 3A.
  • a refrigerant system 20 is illustrated in Figure 1. As shown, two compressors 22 and 24 operate in tandem to provide compressed refrigerant and deliver it throughout the refrigerant system 20. Obviously, more than two compressors can be
  • tandem compressors have common suction and common discharge manifolds, as known to a person ordinarily skilled in the art, the tandem compressors may have a common suction manifold and separate discharge lines as well as separate suction lines and a common discharge manifold. Additionally, tandem compressors 22 and 24 may have oil and vapor equalization lines (not shown), as known in the art.
  • a compressed refrigerant passes through a heat exchanger 26, and downstream to an expander 28.
  • the heat exchanger 26 becomes a condenser, in the subcritical applications, and a single-phase heat exchanger, or a gas cooler, in the transcritical applications.
  • an active expander instead of a passive expansion device, such as an expansion valve or a fixed restriction expansion device, in which energy from a more efficient isentropic expansion process is recaptured and utilized to power or drive (at least partially) at least one refrigerant system component, such as one of the compressors 22 and 24 (as shown schematically at 29). This energy recovery and transfer can be done directly or indirectly.
  • the expander 28 and the compressor 22 can be located on the same shaft or connected through a mechanical transmission device.
  • the energy from the expansion process may be converted to an electric energy that in turn may assist in driving the compressor 22.
  • Downstream of the expander 28, the refrigerant passes through an evaporator 30, and then back to the compressors 22 and 24.
  • An economizer heat exchanger 32 is incorporated into the circuitry of the refrigerant system 20. As known, an economizer function allows for additional stages of unloading as well as performance (capacity and efficiency) enhancement.
  • a portion of refrigerant is tapped from a tap line 51 connected to an intermediate expansion port in the expander 28 and passed through the economizer heat exchanger 48.
  • the tap line 51 is communicated to a point in the expansion process at which the refrigerant has been at least partially expanded to a pressure intermediate of suction and discharge pressures.
  • the refrigerant flowing in the tap line 51 is at lower pressure and temperature than the refrigerant in the main refrigerant circuit leaving the heat exchanger 26 and cools this refrigerant passing through the economizer heat exchanger 48, preferably in a counterflow heat transfer relationship.
  • the tapped refrigerant is returned through a vapor injection line 53 to the compressors 22 and 24, typically in a superheated state.
  • the vapor injection line 53 manifolds refrigerant to the compressors 22 and 24 and delivers it into the compression chambers within the compressor at an intermediate point in the compression process.
  • each of individual compressors 22 and 24 can be replaced with two compressor stages connected in series.
  • This embodiment achieves the inclusion of the economizer circuit without the need for a separate economizer expansion device, since the expander 28 utilizes an intermediate expansion port for delivering of the economizer branch refrigerant.
  • a single expander can provide both main and economizer expansion device functions at higher efficiency levels than in conventional refrigerant systems equipped with passive expansion devices.
  • two separate expansion stages for the main and economized refrigerant flow can be used instead, and in this case, the economizer branch refrigerant and the tap line 51 can be positioned downstream as well as upstream of the economizer heat exchanger 32.
  • tandem compressors 22 and 24 allow for a more flexible system control by selectively actuating one or both of the compressors to provide a necessary capacity to adequately satisfy thermal load requirements in the conditioned space.
  • Compressors 22 and 24 may have different sizes to allow for more stages of capacity adjustment.
  • the economizer function can be enabled or disabled, for each compressor individually or simultaneously for both compressors, to provide additional capacity stages when necessary.
  • valves 62 and 64 allow for selective engagement and disengagement of the economizer function for the compressors 22 and 24 respectively.
  • the refrigerant system 20 may utilize CO 2 as the refrigerant.
  • the refrigerant system 20 may operate in the transcritical cycle, at least for a portion of the time.
  • the transcritical cycle is normally less efficient than the subcritical cycle, so the abovementioned enhancement features and control options of the present invention (the tandem compressors in combination with the expander and the economizer cycle) will be the most beneficial for the transcritical cycle.
  • FIG. 2 shows another embodiment 70, which is similar to the embodiment 20, however, three tandem compressors 72, 74 and 76, with only one compressor 72 being economized, are illustrated.
  • the refrigerant system 70 would provide additional benefits in operation control and performance enhancement.
  • the combination of the expander 28, the economizer circuit and economizer heat exchanger 32, along with the tandem compressor allows close tailoring of the refrigerant system capacity to achieve desired conditions in the climate controlled environment in the most efficient manner.
  • the control (not shown) for the refrigerant system 70 may be configured to operate the individual compressors 72, 74 and 76 (which, once again, may be of different sizes) or any combinations of them to provide a desired number of unloading staged.
  • the economized refrigerant is returned to only one compressor 72.
  • a worker skilled in this art would recognize the various features and benefits, such as performance, control flexibility, control complexity and cost, that would be provided by returning the refrigerant to one or more than one of the compressors, and can select an appropriate design accordingly.
  • more than two sequential compression-expansion stages and more than one economizer circuit may be integrated into the refrigerant systems 20 and 70.
  • the number of stages is primarily defined by a cost-performance benefit tradeoff. These sequential stages may be represented by stand-alone devices or integrated into a single device.
  • One of such refrigerant systems having two economizer circuits and three compression-expansion stages is shown in Figure 3A.
  • an expander 128 has two intermediate pressure ports associated with two economizer circuits.
  • a higher pressure port 136 communicates with an economizer heat exchanger 134 operating at a higher pressure and temperature
  • a lower pressure port 138 communicates with an economizer heat exchanger 132 operating at a lower pressure and temperature.
  • both higher and lower intermediate pressures mentioned above are positioned between the suction and discharge operating pressures for the refrigerant system 170.
  • Refrigerant flow control devices such as a valve 166 and valves 162 and 164 selectively activate the higher and lower pressure economizer circuits respectively.
  • the valve 164 deactivates the economizer function for both lower pressure compressors 172 and 174, while the valve 162 deactivates the economizer function just for the compressor 172.
  • only two (out of three) lower pressure tandem compressors 172, 174 and 176 are equipped with the economizer ports, the compressors 172 and 174 in particular.
  • the first and second compression stage of the economized tandem compressors 172 and 174 represent the first and second compression stages of the refrigerant system 170, while the non-economized tandem compressor 176 operates between the same manifold pressures as the two sequential stages of the economized compressors 172 and 174.
  • Two higher pressure non- economized tandem compressors 182 and 184 represent the third compression stage of the refrigerant system 170.
  • the recovered portion of the expansion process energy in the expander 128 is transmitted to at least partially power the non- economized lower pressure compressor 176.
  • any other compressor of the refrigerant system 170 can be connected to the power source provided by the expender 128, in a similar manner.
  • the embodiment 170 of Figure 3A is similar to the Figure 1 and Figure 2 embodiments 20 and 70 respectively.
  • Figure 3B embodiment shows an alternate tandem compressor configuration for the refrigerant system depicted in Figure 3A.
  • the compressor 182 of the third compression stage directly communicates with the downstream compressors 172 and 174, while the compressor 184 of the same third compression stage directly communicates with the downstream compressor 176.
  • Two refrigerant flow control valves 192 and 194 in Figure 3B replace a single refrigerant flow control valve 166 of Figure 3A, to selectively engage and disengage the economizer function for each of the compressors 182 and 184 respectively.
  • the compressor 184 now takes advantage of the energy recovery from the refrigerant system expander, as shown at 29 in Figure 3B. It is understood that a person skilled in the art would recognize that many other variations of tandem compressor and economizer circuit configurations, as well as energy recovery arrangements, are feasible and can equally benefit from the invention.
  • tandem compressors described in this application can be separate compressor units, or the compression elements of each of those compressors can be combined within a single compressor shell (as, for example, the compression elements positioned on the opposite ends of the rotating shaft or separate compression elements and associated motors simply enclosed within a single shell).
  • the actual refrigerant system may include additional components, such as, for example, a liquid-suction heat exchanger, a reheat coil, an intercooler, additional economizer heat exchangers or flash tanks.
  • the individual tandem compressors can be of variable capacity type, including variable speed and multi-speed configurations. Further, the compressors may have various unloading options, including intermediate pressure to suction pressure bypass arrangements. The compressors may be unloaded internally, as for example, by separating fixed and orbiting scrolls from each on an intermittent basis.
  • These system configurations are also not limited to a particular compressor type and may include scroll compressors, screw compressors (single or multi-rotor configurations), reciprocating compressors (where, for example, some of the cylinders are used as a low compression stage and the other cylinders are used as a high compression stage) and rotary compressors.
  • the refrigerant system may also consist of multiple separate circuits.
  • the present invention would also apply to a broad range of systems, for example, including mobile container, truck-trailer and automotive systems, packaged commercial rooftop units, supermarket installations, residential units, environmental control units, etc.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

Cette invention concerne un système de réfrigération qui comprend un détendeur permettant la mise en oeuvre d'un processus de détente plus efficace et permettant de récupérer une partie de l'énergie à partir de ce processus de détente. Une partie au moins du fluide frigorigène au moins en partie détendue dans le détendeur est prélevée puis acheminée à travers un échangeur thermique économiseur. Dans cet échangeur thermique économiseur, le fluide frigorigène prélevé refroidit un fluide frigorigène de circuit principal augmentant ainsi son potentiel thermodynamique. L'invention concerne également un section de compression pourvue d'au moins deux compresseurs fonctionnant en tandem et permettant une décharge en plusieurs étapes. L'utilisation d'un ou de plusieurs compresseurs en tandem, du cycle de l'économiseur et du détendeur permet au système de réfrigération de fonctionner plus efficacement et de fournir une meilleure souplesse de commande, en particulier, pour un système de réfrigération à base de CO2 fonctionnant dans le cycle transcritique.
PCT/US2006/049286 2006-12-26 2006-12-26 Système de réfrigération à base de co2 équipé de compresseurs en tandem, d'un détendeur et d'un économiseur Ceased WO2008079128A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US12/515,471 US20100071391A1 (en) 2006-12-26 2006-12-26 Co2 refrigerant system with tandem compressors, expander and economizer
CNA2006800568348A CN101568770A (zh) 2006-12-26 2006-12-26 具有串轴式压缩机、膨胀器和经济器的co2制冷剂系统
PCT/US2006/049286 WO2008079128A1 (fr) 2006-12-26 2006-12-26 Système de réfrigération à base de co2 équipé de compresseurs en tandem, d'un détendeur et d'un économiseur
EP06846056A EP2097686A4 (fr) 2006-12-26 2006-12-26 Système de réfrigération à base de co2 équipé de compresseurs en tandem, d'un détendeur et d'un économiseur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2006/049286 WO2008079128A1 (fr) 2006-12-26 2006-12-26 Système de réfrigération à base de co2 équipé de compresseurs en tandem, d'un détendeur et d'un économiseur

Publications (1)

Publication Number Publication Date
WO2008079128A1 true WO2008079128A1 (fr) 2008-07-03

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US (1) US20100071391A1 (fr)
EP (1) EP2097686A4 (fr)
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WO2014179699A1 (fr) * 2013-05-02 2014-11-06 Emerson Climate Technologies, Inc. Système de commande de climatisation à compresseurs multiples
WO2016153841A1 (fr) * 2015-03-20 2016-09-29 Carrier Corporation Unité de réfrigération de transport avec compresseurs multiples
WO2017021293A1 (fr) * 2015-07-31 2017-02-09 Bitzer Kühlmaschinenbau Gmbh Dispositif et procédé permettant la mise en œuvre d'un processus de vaporisation à froid
WO2017200916A1 (fr) * 2016-05-17 2017-11-23 Daikin Applied Americas Inc. Turbo-économiseur utilisé dans un système refroidisseur
US9989279B2 (en) 2010-04-29 2018-06-05 Carrier Corporation Refrigerant vapor compression system with intercooler
US10598395B2 (en) 2018-05-15 2020-03-24 Emerson Climate Technologies, Inc. Climate-control system with ground loop
US11149971B2 (en) 2018-02-23 2021-10-19 Emerson Climate Technologies, Inc. Climate-control system with thermal storage device
US11346583B2 (en) 2018-06-27 2022-05-31 Emerson Climate Technologies, Inc. Climate-control system having vapor-injection compressors
US11585608B2 (en) 2018-02-05 2023-02-21 Emerson Climate Technologies, Inc. Climate-control system having thermal storage tank

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US8631666B2 (en) 2008-08-07 2014-01-21 Hill Phoenix, Inc. Modular CO2 refrigeration system
US9541311B2 (en) 2010-11-17 2017-01-10 Hill Phoenix, Inc. Cascade refrigeration system with modular ammonia chiller units
US9664424B2 (en) 2010-11-17 2017-05-30 Hill Phoenix, Inc. Cascade refrigeration system with modular ammonia chiller units
US9657977B2 (en) 2010-11-17 2017-05-23 Hill Phoenix, Inc. Cascade refrigeration system with modular ammonia chiller units
CN102200364A (zh) * 2011-04-22 2011-09-28 上海海事大学 一种运用双压循环原理的开式经济器
WO2012166338A2 (fr) * 2011-05-31 2012-12-06 Carrier Corporation Système de compresseur hybride et procédés
US9970696B2 (en) 2011-07-20 2018-05-15 Thermo King Corporation Defrost for transcritical vapor compression system
ES2987619T3 (es) 2012-09-20 2024-11-15 Thermo King Llc Módulo de refrigeración de transporte eléctrico
CN103776188B (zh) * 2013-01-21 2017-03-08 摩尔动力(北京)技术股份有限公司 间冷单工质热制冷制热系统
US10132529B2 (en) 2013-03-14 2018-11-20 Rolls-Royce Corporation Thermal management system controlling dynamic and steady state thermal loads
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CN101568770A (zh) 2009-10-28
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