WO2003019085A1 - Dispositif a cycle de compression de vapeur - Google Patents

Dispositif a cycle de compression de vapeur Download PDF

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Publication number
WO2003019085A1
WO2003019085A1 PCT/DK2002/000570 DK0200570W WO03019085A1 WO 2003019085 A1 WO2003019085 A1 WO 2003019085A1 DK 0200570 W DK0200570 W DK 0200570W WO 03019085 A1 WO03019085 A1 WO 03019085A1
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WO
WIPO (PCT)
Prior art keywords
compression
refrigerant
control means
temperature
vapour
Prior art date
Application number
PCT/DK2002/000570
Other languages
English (en)
Inventor
Niels Peter Raun
Jens Andersen
Gunnar Minds
Original Assignee
Mærsk Container Industri A/S
Lodam Elektronik A/S
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 Mærsk Container Industri A/S, Lodam Elektronik A/S filed Critical Mærsk Container Industri A/S
Publication of WO2003019085A1 publication Critical patent/WO2003019085A1/fr

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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers 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
    • 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
    • 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
    • F25B2400/16—Receivers
    • 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
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • 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

  • a vapour-compression-cycle device A vapour-compression-cycle device
  • the present invention relates to vapour-compression-cycle devices, such as refrigerators, air-conditioning units, heat pumps, etc, using a refrigerant op- erating in a closed circuit under trans-critical conditions, and specifically to the methods of regulating the capacity of such devices.
  • refrigerants as for instance R22, R134a, R404a, CF 2 CI 2
  • refrigerant A number of different substances or mixtures of substances may be used as refrigerant.
  • the choice of refrigerant is among others influenced by condensation temperature, as the critical temperature of the fluid sets the upper limit for the condensation to occur. This technology is treated in full details in the literature, e.g. in the Handbooks of American Society of Heat- ing, Refrigerating and Air Conditioning Engineers Inc., Fundamentals 1989 and Refrigeration 1986.
  • Vapour-compression-cycle devices operating under trans-critical conditions are known from German patent 278095 from 1912.
  • This patent describes a method involving two-stage compression of a refrigerant, with intercooling of said refrigerant in the supercritical region.
  • Two-stage compression involving intercooling is ideal when the process employs a cooling agent that operates under trans-critical conditions as the temperature generated under the compressing process would reach high levels and influence the performance of the cycle.
  • the method described suffers from the drawback that the components are placed in a manner that does not comply with today's demands for high efficiency products/processes.
  • a further vapour-compression-cycle device operating under trans-critical conditions is known from patent application No. PCT/NO89/00089 that describes a vapour-compression-cycle device and wherein the capacity regulation of said device employs a single-stage compression cycle process comprising a single-speed compressing device, where the capacity is regulated by varying the refrigerant-enthalpy difference in the evaporator by changing the specific enthalpy of the refrigerant before throttling. This modulation of specific enthalpy is achieved by varying the pressure in the high-pressure side of the compression cycle device that adjusts the throttling means opening.
  • the commonly used refrigerants when employed in a vapour-compression-cycle device, usually ensures a high COP (coefficient of performance) for the device in question.
  • the COP coefficient of performance
  • the COP is defined as the ratio between the power (kW) consumed for driving the compressing devices and the cooling capacity (kW) produced by the vapour-compression-cycle device.
  • a ratio of 1 :3 - 4 is not uncommon.
  • the COP is approximately 1 :2-3.
  • Another object of the present invention is to provide a vapour-compression- cycle device employing a refrigerant that operates under trans-critical conditions and with the smallest possible power consumption; and to employ attractive refrigerants with respect to environmental hazards.
  • the above and other objects of the present invention are achieved by pro- viding a method operating at usually or usual trans-critical conditions, where the capacity is regulated by regulating the number of revolutions of the drive shaft of the compressing device as a function of the required capacity; and wherein the variable flow control means is regulated as a function of the temperature and/or pressure of the refrigerant measured at the high pres- sure side of the system with respect to optimizing the COP (coefficient of performance) of the system.
  • Another object of the present invention is achieved by providing regulation means for the vapour-compression-cycle device that comprises means for regulating the revolutions of the drive shaft of said compressing device for regulating the capacity; and means for controlling said variable control means as a function of the temperature of the refrigerant on the high pressure side with respect to optimizing the COP of the system.
  • Still another object of the present invention is to provide a control means, said control means for the conditions given regulating the throttling means on basis of temperature/pressure of the refrigerant on the high-side for optimizing the COP (coefficient of performance)
  • a further object of the present invention is to provide a vapour- compression-cycle device comprising two or more compression stages. By introducing two or more compression stages, it has been proven that an accurate regulation is possible by utilizing more simple specifications of the algorithm for the optimal pressure after the variable flow control means.
  • a further object of the present invention is to provide a method for regulating the regulation means for the variable flow control means at decreasing temperature of the refrigerant arranged to regulating said variable flow control means until a temperature/pressure inferior to the critical temperature, whereupon the opening for refrigerant of the variable flow control means is fully opened, and at increasing temperatures the regulation means starts to regulate said variable flow control means at a temperature higher than the critical temperature.
  • variable flow control means at temperatures of the refrigerant/gas about the critical value of ca. 32°C in order to prevent to many switching in/offs of the compressing devices.
  • a further object of the present invention is to provide a method, wherein the refrigerant, after the first compression stage and before the second compression stage, is cooled in a first cooler that employs air as coolant, said first cooler being with respect to the airflow placed in series, and after a second cooler that employs air as coolant for cooling/condensing the refrigerant after the second stage compression.
  • Yet a further object of the present invention is to provide a method for regulating a transcritical vapour-compression-cycle device employing CO 2 (carbon dioxide) as refrigerant.
  • Yet another object of the present invention is to provide a device comprising means for measuring the temperature of the refrigerant on the high-pressure side with respect to optimizing the COP of the system as a function of the temperature or pressure.
  • Yet another object of the present invention is to provide a vapour- compression-cycle device comprising a cooler employing water as coolant arranged in the integral closed circuit after a compressing device and before the air-cooled cooler.
  • Still another object of the present invention is to provide a vapour- compression-cycle device comprising a receiver arranged in the integral closed circuit after the variable flow control means but before the econo- mizer.
  • Another object of the present invention is to provide a vapour-compression- cycle device employing CO 2 (carbon dioxide) as refrigerant by which a refrigerant operating under trans-critical conditions is environmentally friendly.
  • Yet another object of the present invention is to provide a vapour- compression-cycle device comprising coupling means for establishing water cooling, by which it will be made possible to establish water-cooling when the container is loaded onboard a ship, and air cooling of the heat exchangers/condensers is not sufficient for cooling the refrigerant/gas.
  • a further object of the present invention is to provide a vapour-cycle- compression device comprising means for coupling to a ship's electrical power system, and wherein the compression device is driven by an electrical motor means coupled to said electrical power system, by which it is ensured that the vapour cycle compression device is operational when loaded on a ship for transportation.
  • Yet another object of the present invention is to provide a method employed for refrigerating the interior of a refrigerated container.
  • Figure 1 is a graph illustrating the vapour compression cycles for the refrigerants R134a and C0 2 (carbon dioxide);
  • Figure 2 is a graph illustrating the capacities (Q 0 ) dependency of the temperature of the refrigerant gas/vapour at output of the cooler at maintained pressure;
  • Figure 3 is a graph illustrating the capacity (Q 0 ) dependency of the pressure in the cooler for maintained gas temperature
  • Figure 4 illustrates calculated pressure in the cooler for optimal COP depending off the evaporation temperature and gas temperature at output of the cooler
  • Figure 5 illustrates calculated pressure in the cooler for optimal COP depending off on evaporation temperature and the gas temperature at the output from the cooler
  • Figure 7 is a graph illustrating an H-log P diagram for at two-stage system operating at trans-critical conditions
  • Figure 8 is a graph illustrating a H-log P diagram for at two-stage system operating at sub critical conditions;
  • Figure 9 is a calculated comparison of gas temperature;
  • Figure 10 is a diagram for determining the adjustment pressure
  • Figure 1 1 is a schematic representation of a trans-critical vapour- compression-cycle device according to a preferred embodiment of the invention.
  • the process will depend on the temperature at the heat exchanger/condensing unit being above or below the critical temperature.
  • the integral circuit process of the refrigerant CO 2
  • the integral circuit process will not be different from the integral circuit process of other refrigerants complying to the Carnot cycle/process.
  • the integral circuit process will be different as CO 2 cannot condense at temperatures above 31 °C. This does not mean the process cannot supply cooling or heating, only that the process is to be configured to comply with another integral circuit process, namely the Lorentz proces.
  • the condenser will no longer be used for condensing the refrigerant, but solely for cooling of the trans critical coolant/fluid, and is hence described as the "gas-cooler"
  • Figure 2 illustrates how the cooling capacity is increased dramatically by changing the temperature of the refrigerant (CO 2 ) by discharge from the gas cooler.
  • the work of the compressing device (W ) remains the same.
  • the temperature of the CO 2 at output of the gas-cooler cannot be chosen arbitrarily, but will be dependent of the conditions of the integral circuit process device given. This may be the temperature of the air, when air is employed as cooling agent, or the temperature of the cooling water, when water is employed as cooling agent. Since it is not possible to control the temperature of the refrigerant at output of the gas cooler, this means that instead a pressure optimal for a requested run (low/high capacity) or just for the conditions given, to maximize COP (coefficient of performance) for the integral circuit process device.
  • Capacity regulating of a trans-critical integral circuit process device employ- ing CO 2 as refrigerant can be achieved -apart from the normal methods - by controlling the pressure in the gas-cooler.
  • a temperature of the CO 2 - refrigerant given at output of the gas cooler, (determent by exterior conditions) it is thus possible to regulate the capacity of the integral circuit process device within a wide range.
  • the principle is illustrated by Figure 4.
  • Figure 4 illustrates the calculated optimal choice - in respect to maximal COP - of the gas pressure in the gas cooler/heat exchanger dependent of the temperature of the refrigerant gas at output from the gas cooler.
  • the optimal high pressure is dependent of both the gas temperature at output of the gas cooler, but even of the evaporation tem- perature. Further the optimal pressure will depend on the mechanical efficiencies of the compressing devices and pressure losses in exchangers and pipes. On the background of an analysis, the optimal high-pressure can be found on the basis of varying evaporation temperatures (T e ) and temperatures at output of the gas cooler (T g , 2 ).
  • the isentropic efficiency compressing device is kept at 0,6.
  • Figure 5 illustrates calculated pressure in the cooler for optimal COP dependent of evaporation temperature and the gas temperature at the output from the cooler.
  • a mathematical formula has been expressed, stating the optimal pressure of the gas/refrigerant at output of the cooler, for optimal COP on the basis of T e and T g , 2 .
  • Figure 7 is a graph illustrating a H-log P diagram for a two-stage system operating at trans-critical conditions. The numbers are referring to the stages of the circle process, where: (1 ) is the condition of the refrigerant at the inlet of the first compressing device (A). (2) the condition after the compression by the low-pressure compressing device (A), the condition of the refrigerant at (3) is after cooling of the gas in the first cooling device (C) and 4 is the condition at the inlet of the high-pressure compressing device (B). The pressure is then elevated to the pressure at (5) after compression in the high-pressure compressing device (B). Hereafter the refrigerant is cooled reaching the stage at (6) after cooling/condensation in the gas cooler/condensing unit (E).
  • the pressure of the refrigerant is reduced at the stage with number (7).
  • the refrigerant is cooled further by the economizer, by which some sub-cooling is ensured reaching the stage (8), which indicates the condition of the refrigerant before the evaporating in the evaporator.
  • variable flow control means continues to be a controlling factor for the gas temperature, decreasing until 27.5°C, following which it must be completely open. Conversely, at increasing gas temperature a regulation is not initiated until the temperature exceeds 32.5°C. This function is necessary to avoid too excessive switch in and switch outs at gas temperatures around the critical temperature of about 32°C.
  • gas pressure and temperature within the receiver will always settle at a level that corresponds to the saturation pres- sure that prevails where the gas expands, at constant enthalpy, above the throttle valve to upper or lower threshold curve.
  • FIG 11 shows a schematic representation of a trans-critical vapour- compression-cycle device according to a preferred embodiment of the invention, comprising two-stage compression of a refrigerant.
  • the vapour-compression-cycle device comprises a first compressing device (A) with an inlet and an outlet side, connected in series to a first heat exchanger (C) and employing air as coolant; and a subsequent second compressing device (B) with an inlet and outlet side, connected to a counter flow heat exchanger (D) and employing water as coolant.
  • a second heat exchanger (E) employing air as coolant is arranged.
  • Said first and second heat exchangers (C, E) employing air as coolant are, with respect to the airflow, arranged in series with the second heat exchanger (E) first and the first heat exchanger (C) second, arranged in a trunk-like or similar space providing a air path for the cooling air.
  • a ventilator fan is arranged to ensure a sufficient airflow for the heat exchanging process.
  • a sensor device followed by a variable flow control means (F) comprising regulation means (not shown) and a receiver (G) are arranged, followed by an economizer (H) with an inlet and outlet, and a throttling means (expansion vessel) (J) comprising a sensor attached to the suction line, described in the latter.
  • an economizer by-pas line comprising an inlet and outlet is connected with en- trance after the economizer (H) and before the throttling means (expansion vessel) (J) and the outlet connected to the integral closed circuit after the first heat exchanger (C) and before the second compression device (B).
  • a throttling means (expansion vessel) (I) is arranged before the economizer, said throttling means (expansion vessel) (I) with the sensor being attached to the in the economizer by-pass line after the economizer (H).
  • the function of throttling means (expansion vessel) (I) will be known to the skilled person, hence it will not be described in further detail in the following, it is the function of the economizer (H) to ensure some degree of sub-cooling of the refrigerant.
  • an evaporator (K) with an inlet and an outlet is connected to the inlet connected with the throttling means (expan- sion vessel) (J) and the outlet to the side connected to the inlet of the first compression device (A), by a line/pipe hereafter described as suction line.
  • a line/pipe hereafter described as suction line.
  • the function and arrangement of throttling means (expansion vessel) (J) and sensor will be known to the skilled person, hence it will not be described in further detail in the following.
  • the evaporator (K) is installed inside a container in which a refrigerated atmosphere is required as it will be likewise understood that a ventilation fan (L) is advantageously arranged to circulate air around the evaporator (K).
  • the first compression device (A) and the following second compression de- vice (B) both comprising a drive shaft are, in the representation of Figure 1 , shown as a two-stage compressing device unit, sharing the same drive shaft, said drive shaft being coupled to a motor means. It will, however, be understood that the above described embodiment of the invention is intended to be exemplary only and not in any way limiting the scope of the invention. It will be appreciated that the two-stage compressing device driven by one motor means can be replaced by two single stage compressing devices each comprising a motor means.
  • the vapour-compression-cycle device comprises a first sensor means ar- ranged on the high-pressure side in the closed circuit before the variable flow control means (F) and after the second cooler (E). Another sensor means is arranged in the closed circuit after the evaporator and before the first inlet of the compression device (A).
  • the sensor means is, in a preferred embodiment, temperature sensors, monitoring the temperature condition of the refrigerant/gas and giving a input signal to the vapour-compression-cycle devices regulation means for regulating the capacity of the vapour- compression-cycle device.
  • the vapour-compression-cycle device according to a preferred embodiment of the invention is suitable for installation in a container of the type used on in particular ships, for the transportation of goods that require refrigerated surroundings.
  • the ship's power system When the device is loaded onboard, the ship's power system is connected to provide the drive motor for the compressing devices (A, B) and all other electrical components that are powered electrically, and the counter flow heat exchanger (D) is connected to a cooling water system, said cooling water system providing cold water for containers equipped with a va- pour-compression-cycle device comprising a heat exchanger employing water as cooling agent/coolant.
  • the ventilation fan (N) is turned off and the cooling of the refrigerant after the second compression device (B) is taken over from the second heat exchanger (E) by the counter flow heat exchanger (D).
  • An airflow as the result of convexion in the airpath ensures some amount of cooling air or the first heat exchanger (C)
  • variable control means in principle must be fully open and in super critical operation adjustable. It will however be practical possible to make this conversion pass without dramatic variations in the temperature of the refrigerant.
  • variable flow control means The regulation of the variable flow control means is illustrated in figure 9, listing the comparison between the gas temperature at output gas cooler and optimal gas pressure, and with the regulating curve sketched, said regulation curve determent by the following equation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un procédé et un dispositif destinés à réguler la capacité d'un cycle de compression de vapeur comprenant un dispositif de compression, un condensateur, au moins un refroidisseur, un dispositif de régulation de débit variable, et un évaporateur relié en série et formant un circuit fermé autonome avec un réfrigérant fonctionnant dans des conditions transcritiques, dans lesquels la capacité est régulée par régulation du nombre de révolution de l'arbre d'entraînement du dispositif de compression comme fonction de la capacité nécessaire. En outre, le dispositif de régulation du débit variable est régulé comme fonction de la température et/ou de la pression du réfrigérant mesurée du côté haute pression du système par rapport à l'optimisation du coefficient de performance (COP). Ceci permet de produire un nouveau dispositif amélioré simple et efficace destiné à réguler la capacité d'un dispositif à cycle de compression de vapeur transcritique ne présentant pas les défauts susmentionnés; et d'améliorer l'efficacité du processus à cycle de compression de vapeur.
PCT/DK2002/000570 2001-08-31 2002-09-02 Dispositif a cycle de compression de vapeur WO2003019085A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA200101283 2001-08-31
DKPA200101283 2001-08-31

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WO2003019085A1 true WO2003019085A1 (fr) 2003-03-06

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Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1462738A1 (fr) * 2003-03-26 2004-09-29 Sanyo Electric Co., Ltd. Réfrigérateur
WO2005003651A3 (fr) * 2003-06-26 2005-06-09 Carrier Corp Commande d'un systeme frigorifique
WO2005057095A1 (fr) * 2003-11-20 2005-06-23 Modine Manufacturing Company Systeme de refroidissement au co2
FR2864212A1 (fr) * 2003-12-19 2005-06-24 Armines Ass Pour La Rech Et Le Systeme thermodynamique a evaporation etagee et a sous refroidissement renforce adapte a des melanges a grand glissement de temperature
NL1026728C2 (nl) * 2004-07-26 2006-01-31 Antonie Bonte Verbetering van koelsystemen.
EP1688686A2 (fr) * 2005-02-02 2006-08-09 Sanyo Electric Co., Ltd. Dispositif d'alimentation pour boissons
WO2006087005A1 (fr) * 2005-02-18 2006-08-24 Carrier Corporation Procede de controle de haute pression dans un circuit de refrigeration, supercritique par intermittence
WO2007027173A1 (fr) 2005-08-31 2007-03-08 Carrier Corporation Système de chauffage d’eau à pompe à chaleur utilisant un compresseur à vitesse variable
EP1632736A3 (fr) * 2004-09-07 2007-11-14 SANYO ELECTRIC Co., Ltd. Pompe à chaleur et machine à sécher
EP1462739A3 (fr) * 2003-03-27 2009-03-11 Sanyo Electric Co., Ltd. Appareil à cycle de frigorigène
EP1684034A3 (fr) * 2004-12-30 2009-05-13 Nakayama Engineering Company Limited Système de réfrigération et son procédé de commande
EP2068093A1 (fr) * 2006-09-11 2009-06-10 Daikin Industries, Ltd. Dispositif de réfrigération
WO2009082405A1 (fr) 2007-12-26 2009-07-02 Carrier Corporation Système réfrigérant à refroidisseur intermédiaire et injection de liquide/vapeur
US20100326100A1 (en) * 2008-02-19 2010-12-30 Carrier Corporation Refrigerant vapor compression system
EP2068099A3 (fr) * 2007-12-05 2012-02-15 Hitachi Ltd. Système de cycle de réfrigération, installation de liquéfaction de gaz naturel, système de pompe à chaleur, et procédé pour modifier le système de cycle de réfrigération
WO2012109057A3 (fr) * 2011-02-08 2012-10-11 Carrier Corporation Echangeur de chaleur a rejet de chaleur refroidi par l'eau
US20140053585A1 (en) * 2011-04-21 2014-02-27 Carrier Corporation Transcritical Refrigerant Vapor System With Capacity Boost
EP3000993A1 (fr) 2014-09-26 2016-03-30 MAUL, Martin Dispositif de production d'energie, en particulier installation orc
DE102015010593A1 (de) 2015-08-11 2017-03-30 Audi Ag Betriebsverfahren für eine Kälteanlage und zugehörige Kälteanlage
DE102016204405A1 (de) 2016-03-17 2017-09-21 Martin Maul Vorrichtung zur Energieerzeugung, insbesondere ORC-Anlage
WO2017189420A1 (fr) * 2016-04-27 2017-11-02 Carrier Corporation Système de transport réfrigéré refroidi par eau
EP4113035A1 (fr) * 2021-07-02 2023-01-04 Mitsubishi Heavy Industries Thermal Systems, Ltd. Dispositif de congélation, système de congélation et procédé de commande de dispositif de congélation

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0786632A2 (fr) * 1996-01-25 1997-07-30 Denso Corporation Système de réfrigération avec soupape de commande de pression
US5685160A (en) * 1994-09-09 1997-11-11 Mercedes-Benz Ag Method for operating an air conditioning cooling system for vehicles and a cooling system for carrying out the method
EP0952412A2 (fr) * 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Système frigorifique et procédé pour son fonctionnement
EP1046869A1 (fr) * 1999-04-20 2000-10-25 Sanden Corporation Système de réfrigération et d'air conditionné
EP1059495A2 (fr) * 1999-06-08 2000-12-13 Mitsubishi Heavy Industries, Ltd. Cycle de compression à vapeur surcritique
US6250099B1 (en) * 1998-07-31 2001-06-26 Zexel Corporation Refrigerating device
EP1202004A1 (fr) * 2000-10-30 2002-05-02 Calsonic Kansei Corporation Cycle de refroidissement et procédé de commande associé

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5685160A (en) * 1994-09-09 1997-11-11 Mercedes-Benz Ag Method for operating an air conditioning cooling system for vehicles and a cooling system for carrying out the method
EP0786632A2 (fr) * 1996-01-25 1997-07-30 Denso Corporation Système de réfrigération avec soupape de commande de pression
EP0952412A2 (fr) * 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Système frigorifique et procédé pour son fonctionnement
US6250099B1 (en) * 1998-07-31 2001-06-26 Zexel Corporation Refrigerating device
EP1046869A1 (fr) * 1999-04-20 2000-10-25 Sanden Corporation Système de réfrigération et d'air conditionné
EP1059495A2 (fr) * 1999-06-08 2000-12-13 Mitsubishi Heavy Industries, Ltd. Cycle de compression à vapeur surcritique
EP1202004A1 (fr) * 2000-10-30 2002-05-02 Calsonic Kansei Corporation Cycle de refroidissement et procédé de commande associé

Cited By (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1316212C (zh) * 2003-03-26 2007-05-16 三洋电机株式会社 制冷剂循环装置
US7111471B2 (en) 2003-03-26 2006-09-26 Sanyo Electric Co., Ltd. Refrigerant cycle apparatus
EP1462738A1 (fr) * 2003-03-26 2004-09-29 Sanyo Electric Co., Ltd. Réfrigérateur
EP1462739A3 (fr) * 2003-03-27 2009-03-11 Sanyo Electric Co., Ltd. Appareil à cycle de frigorigène
WO2005003651A3 (fr) * 2003-06-26 2005-06-09 Carrier Corp Commande d'un systeme frigorifique
KR100755160B1 (ko) * 2003-06-26 2007-09-04 캐리어 코포레이션 냉각 시스템의 제어
EP2282142A1 (fr) * 2003-06-26 2011-02-09 Carrier Corporation Contrôle de système de réfrigération
US7000413B2 (en) 2003-06-26 2006-02-21 Carrier Corporation Control of refrigeration system to optimize coefficient of performance
KR101054784B1 (ko) * 2003-11-20 2011-08-05 모다인 매뉴팩츄어링 컴파니 이산화탄소 냉각 시스템
GB2421563A (en) * 2003-11-20 2006-06-28 Modine Mfg Co Co2 cooling system
WO2005057095A1 (fr) * 2003-11-20 2005-06-23 Modine Manufacturing Company Systeme de refroidissement au co2
WO2005059450A1 (fr) * 2003-12-19 2005-06-30 Armines Systeme thermodynamique a evaporation etagee et a sous refroidissement renforce adapte a des melanges a gran glissement de temperature
FR2864212A1 (fr) * 2003-12-19 2005-06-24 Armines Ass Pour La Rech Et Le Systeme thermodynamique a evaporation etagee et a sous refroidissement renforce adapte a des melanges a grand glissement de temperature
WO2006011789A1 (fr) * 2004-07-26 2006-02-02 Antonie Bonte Perfectionnements dans des systemes de refroidissement transcritique
NL1026728C2 (nl) * 2004-07-26 2006-01-31 Antonie Bonte Verbetering van koelsystemen.
EP1632736A3 (fr) * 2004-09-07 2007-11-14 SANYO ELECTRIC Co., Ltd. Pompe à chaleur et machine à sécher
US7325333B2 (en) 2004-09-07 2008-02-05 Sanyo Electric Co., Ltd. Heat pump device and drying machine
US8640473B2 (en) 2004-12-30 2014-02-04 Nakayama Engineering Company Limited Refrigeration apparatus and method for controlling the same
EP1684034A3 (fr) * 2004-12-30 2009-05-13 Nakayama Engineering Company Limited Système de réfrigération et son procédé de commande
US7841195B2 (en) 2004-12-30 2010-11-30 Nakayama Engineering Company Limited Refrigeration apparatus and method for controlling the same
EP1688686A2 (fr) * 2005-02-02 2006-08-09 Sanyo Electric Co., Ltd. Dispositif d'alimentation pour boissons
EP1688686A3 (fr) * 2005-02-02 2010-01-27 Sanyo Electric Co., Ltd. Dispositif d'alimentation pour boissons
US8186171B2 (en) 2005-02-18 2012-05-29 Carrier Corporation Method for controlling high-pressure in an intermittently supercritically operating refrigeration circuit
WO2006087005A1 (fr) * 2005-02-18 2006-08-24 Carrier Corporation Procede de controle de haute pression dans un circuit de refrigeration, supercritique par intermittence
EP2273214A3 (fr) * 2005-02-18 2011-11-02 Carrier Corporation Procédé de contrôle de haute pression dans un circuit de réfrigération, supercritique par intermittence
EP1938021A4 (fr) * 2005-08-31 2010-09-01 Carrier Corp Système de chauffage d'eau à pompe à chaleur utilisant un compresseur à vitesse variable
WO2007027173A1 (fr) 2005-08-31 2007-03-08 Carrier Corporation Système de chauffage d’eau à pompe à chaleur utilisant un compresseur à vitesse variable
EP1938021A1 (fr) * 2005-08-31 2008-07-02 Carrier Corporation Système de chauffage d'eau à pompe à chaleur utilisant un compresseur à vitesse variable
EP2068093A1 (fr) * 2006-09-11 2009-06-10 Daikin Industries, Ltd. Dispositif de réfrigération
EP2068093A4 (fr) * 2006-09-11 2014-12-24 Daikin Ind Ltd Dispositif de réfrigération
EP2068099A3 (fr) * 2007-12-05 2012-02-15 Hitachi Ltd. Système de cycle de réfrigération, installation de liquéfaction de gaz naturel, système de pompe à chaleur, et procédé pour modifier le système de cycle de réfrigération
WO2009082405A1 (fr) 2007-12-26 2009-07-02 Carrier Corporation Système réfrigérant à refroidisseur intermédiaire et injection de liquide/vapeur
EP2235448A1 (fr) * 2007-12-26 2010-10-06 Carrier Corporation Système réfrigérant à refroidisseur intermédiaire et injection de liquide/vapeur
EP2235448A4 (fr) * 2007-12-26 2013-12-11 Carrier Corp Système réfrigérant à refroidisseur intermédiaire et injection de liquide/vapeur
JP2011512509A (ja) * 2008-02-19 2011-04-21 キャリア コーポレイション 冷媒蒸気圧縮システム
US20100326100A1 (en) * 2008-02-19 2010-12-30 Carrier Corporation Refrigerant vapor compression system
WO2012109057A3 (fr) * 2011-02-08 2012-10-11 Carrier Corporation Echangeur de chaleur a rejet de chaleur refroidi par l'eau
US10401094B2 (en) 2011-02-08 2019-09-03 Carrier Corporation Brazed plate heat exchanger for water-cooled heat rejection in a refrigeration cycle
US9360237B2 (en) * 2011-04-21 2016-06-07 Carrier Corporation Transcritical refrigerant vapor system with capacity boost
US20140053585A1 (en) * 2011-04-21 2014-02-27 Carrier Corporation Transcritical Refrigerant Vapor System With Capacity Boost
EP3000993A1 (fr) 2014-09-26 2016-03-30 MAUL, Martin Dispositif de production d'energie, en particulier installation orc
DE102014014032A1 (de) * 2014-09-26 2016-03-31 Martin Maul Vorrichtung zur Energieerzeugung, insbesondere ORC-Anlage
DE102015010593A1 (de) 2015-08-11 2017-03-30 Audi Ag Betriebsverfahren für eine Kälteanlage und zugehörige Kälteanlage
DE102015010593B4 (de) 2015-08-11 2018-12-06 Audi Ag Betriebsverfahren für eine Kälteanlage und zugehörige Kälteanlage
DE102016204405A1 (de) 2016-03-17 2017-09-21 Martin Maul Vorrichtung zur Energieerzeugung, insbesondere ORC-Anlage
WO2017189420A1 (fr) * 2016-04-27 2017-11-02 Carrier Corporation Système de transport réfrigéré refroidi par eau
CN109073283A (zh) * 2016-04-27 2018-12-21 开利公司 水冷式冷藏运输系统
US20190128568A1 (en) * 2016-04-27 2019-05-02 Carrier Corporation Water-Cooled Refrigerated Transport System
CN109073283B (zh) * 2016-04-27 2021-08-03 开利公司 水冷式冷藏运输系统
EP4113035A1 (fr) * 2021-07-02 2023-01-04 Mitsubishi Heavy Industries Thermal Systems, Ltd. Dispositif de congélation, système de congélation et procédé de commande de dispositif de congélation

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