EP0604417B1 - Control of high-side pressure in transcritical vapor compression cycle - Google Patents

Control of high-side pressure in transcritical vapor compression cycle Download PDF

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Publication number
EP0604417B1
EP0604417B1 EP91916351A EP91916351A EP0604417B1 EP 0604417 B1 EP0604417 B1 EP 0604417B1 EP 91916351 A EP91916351 A EP 91916351A EP 91916351 A EP91916351 A EP 91916351A EP 0604417 B1 EP0604417 B1 EP 0604417B1
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EP
European Patent Office
Prior art keywords
pressure
throttling valve
gas cooler
refrigerant
circuit
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Expired - Lifetime
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EP91916351A
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German (de)
French (fr)
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EP0604417A1 (en
Inventor
Gustav Lorentzen
Jostein Pettersen
Roar Rektorli Bang
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Sinvent AS
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Sinvent AS
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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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion 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
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the condenser

Definitions

  • the present invention relates to vapor compression cycle devices such as refrigerating, air-conditioning and heat pump systems, operating under transcritical conditions, and more particularly to a method of high-side pressure regulation maintaining optimum operation with respect to energy consumption.
  • PTC application WO 990/07683 discloses a transcritical vapor compression cycle device and a method for regulating its capacity based on modulation of the supercritical high-side pressure.
  • the system consists of a compressor, a gas cooler (condenser), an internal heat exchanger, an evaporator and a receiver. Capacity control is achieved by varying the liquid inventory of the low pressure refrigerant receiver situated intermediate the evaporator and the compressor, where a throttling valve between the high pressure outlet of the internal heat exchanger and evaporator inlet is applied as steering means.
  • the present invention starts from the teaching of the above mentioned WO 90/07683. It is an object of the present invention to provide for a respective method and device, respectively, which is simple and which is adapted to avoid waste of energy.
  • the modulating of the supercritical high-side pressure is performed by controlling the degree of opening of the throttling valve.
  • the control means of the device according to the invention may operatively be connected to the throttling valve and may be adapted to control the degree of opening of the throttling valve.
  • the above method may include that detection of the operating condition is conducted by measurement of the refrigerant temperature adjacent an outlet of the gas cooler.
  • the detecting means comprises means for measuring a parameter representative of the refrigerant temperature adjacent said outlet of the gas cooler.
  • the throttling valve may be a back-pressure controlling unit with variable set-point electronically controlled by a microprocessor.
  • the throttling valve is a back-pressure controlling unit with variable set-point comprising a temperature sensor bulb situated at or near the gas cooler refrigerant outlet or at another location having a temperature representing the operating condition of the circuit, and a membrane arrangement regulating the set-point of the back-pressure controlling unit in a desired relation to the bulb temperature.
  • carbon dioxide is applied as a refrigerant.
  • a well known peculiarity of transcritical cycles (operating with the refrigerant compressed to a supercritical pressure in the high-side) is that the coefficient of performance COP, defined as the ratio between the refrigerating capacity and applied compressor shaft power, can be raised by increasing the high-side pressure, while the gas cooler (condenser) outlet refrigerant temperature is maintained mainly constant. This can be illustrated by means of a conventional pressure enthalpy diagram.
  • the COP increases with increasing high-side pressure only up to a certain level and then begins to decline as the extra refrigerating effect no longer fully compensates for the extra work of compression.
  • a diagram showing the cooling capacity (Q o ), compressor shaft power (P) and their ratio (COP) as a function of high-side pressure can be provided.
  • Fig. 1 illustrates such a diagram generated for refrigerant CO2 at a constant evaporating and gas cooler (condenser) outlet temperature, based on theoretical cycle calculations.
  • the COP reaches a maximum as indicated.
  • the detected refrigerant temperature at the gas cooler (condenser) outlet or some other temperature or parameter corresponding to this will be the only significant steering parameter required as input for control of the throttling valve.
  • a back-pressure controller as throttling valve may give certain advantages in that internal compensation for varying refrigerant mass flow and density is obtained.
  • a throttling valve with back-pressure control will keep the inlet pressure, i.e. high-side pressure, at the set point regardless of refrigerant mass flow and inlet refrigerant temperature.
  • the set-point of the back-pressure controller is then regulated by means of an actuator operating in accordance with the predetermined control scheme indicated above.
  • Fig. 3 illustrates a preferred embodiment of the transcritical refrigerating circuit comprising a compressor 10 connected in series to a gas cooler (condenser) 11, an internal counterflow heat exchanger 12 and a throttling valve 13.
  • An evaporator 14 and a low pressure liquid receiver 16 are connected intermediate the throttling valve and the compressor.
  • a temperature sensor at the gas cooler (condenser) refrigerant outlet 5 provides information on the operating conditions of the circuit to the control system 7 e.g. a microprocessor.
  • the throttling valve 13 is equipped with an actuator 9 and the valve position is automatically modulated in accordance with the predetermined set-point pressure characteristics by the control system.
  • the circuit is now provided with a throttling valve 13 based on a simple mechanical back-pressure controller eliminating use of the microprocessor and electronic control of the valve shown in Example 1.
  • the regulator is equipped with a temperature sensor bulb 5 situated at or near the gas cooler (condenser) refrigerant outlet.
  • the pressure resulting from the sensor bulb temperature mechanically adjusts the set-point of the back-pressure controller according to the gas cooler (condenser) outlet refrigerant temperature.
  • the gas cooler condenser
  • the circuit is based on one of the throttling valve control concepts described in Examples 1 or 2, but instead of locating the temperature sensor or sensor bulb at the gas cooler (condenser) refrigerant outlet, the sensor or sensor bulb measures the inlet temperature of the cooling agent to which heat is rejected.
  • the sensor or sensor bulb measures the inlet temperature of the cooling agent to which heat is rejected.
  • the signal from a temperature sensor or bulb may be replaced by a signal representing the desired cooling or heating capacity of the system. Due to the correspondence between ambient temperature and load, this signal may serve as a basis for regulating throttling valve set-point pressure.

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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)
  • Fluid Mechanics (AREA)
  • Auxiliary Devices For And Details Of Packaging Control (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Eye Examination Apparatus (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Processing Of Solid Wastes (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Lasers (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

A vapor compression cycle device operating at supercritical pressure in the high-side of a circuit comprising compressor (10), gas cooler (11), internal heat exchanger (12), throttling valve (13), evaporator (14), low pressure refrigerant receiver is additionally provided with means (5) for detection of at least one operating condition of the circuit, preferentially detection of a parameter representing the refrigerant temperature adjacent to the outlet of the gas cooler (11).

Description

    Field of the Invention
  • The present invention relates to vapor compression cycle devices such as refrigerating, air-conditioning and heat pump systems, operating under transcritical conditions, and more particularly to a method of high-side pressure regulation maintaining optimum operation with respect to energy consumption.
    • Background of the Invention
  • PTC application WO 990/07683 discloses a transcritical vapor compression cycle device and a method for regulating its capacity based on modulation of the supercritical high-side pressure. The system consists of a compressor, a gas cooler (condenser), an internal heat exchanger, an evaporator and a receiver. Capacity control is achieved by varying the liquid inventory of the low pressure refrigerant receiver situated intermediate the evaporator and the compressor, where a throttling valve between the high pressure outlet of the internal heat exchanger and evaporator inlet is applied as steering means.
  • Excessive tests conducted recently on a prototype of the transcritical vapor compression unit show that for some specific applications of the invention, e.g. in mobile air-conditioning units working at varying loads and conditions, the high-side pressure at less than full capacity should be adjusted in accordance with the actual operating conditions (load) of the unit, in order to achieve minimum energy consumption at the given capacity requirement. The actual operating conditions may be defined by refrigerant temperatures or pressures, by external temperatures or by the capacity requirements. Any available state-of-the-art capacity control system, e.g. on/off, variable capacity compressor or variable speed control, can be used separately and independently of the throttling valve steering in the disclosed circuit to regulate the cooling or heating capacity.
  • Consequently it was necessary to develop a new control strategy for a transcritical vapor compression cycle device to obtain optimal operation with respect to energy consumption of the disclosed vapor compression device.
  • In the field of subcritical vapor compression cycles it is known to control a throttling valve in response to the actual operating conditions of the cycle, cf. US-A-1 591 302, SE-B-463 533 and US-A-3 638 446.
  • According to the precharacterizing clauses of claims 1 and 4, the present invention starts from the teaching of the above mentioned WO 90/07683. It is an object of the present invention to provide for a respective method and device, respectively, which is simple and which is adapted to avoid waste of energy.
  • According to the invention, the above object is achieved by
    • a method of controlling a transcritical vapor compression cycle device operating with supercritical high-side pressure and comprising a compressor, a gas cooler, an internal heat exchanger, a throttling valve, an evaporator and a low pressure refrigerant receiver connected in series into a circuit, characterized by the steps of detecting at least one of the actual operating conditions of the circuit and modulating the supercritical high-side pressure in accordance with a predetermined set of values which define the minimum energy consumption of the device for the detected operation conditions at given capacity requirements,
    • and by
    • a vapor compression cycle device operating at supercritical pressure in the high-side and comprising a compressor, a gas cooler, an internal heat exchanger, a throttling valve, an evaporator and a low pressure refrigerant receiver connected in series into a circuit, characterized by means for detecting at least one operating condition of the circuit and control means, operatively connected to the detecting means, for modulating the supercritical high-side pressure in accordance with a predetermined set of high pressure values which define the minimum energy consumption of the device for the detected operating condition at given capacity requirements,
    • respectively.
  • According to a preferred embodiment of the method according to the invention, the modulating of the supercritical high-side pressure is performed by controlling the degree of opening of the throttling valve. Accordingly, the control means of the device according to the invention may operatively be connected to the throttling valve and may be adapted to control the degree of opening of the throttling valve.
  • Moreover, the above method may include that detection of the operating condition is conducted by measurement of the refrigerant temperature adjacent an outlet of the gas cooler. Accordingly, in the device according to the invention, the detecting means comprises means for measuring a parameter representative of the refrigerant temperature adjacent said outlet of the gas cooler.
  • The throttling valve may be a back-pressure controlling unit with variable set-point electronically controlled by a microprocessor.
  • Furthermore, according to a preferred embodiment, the throttling valve is a back-pressure controlling unit with variable set-point comprising a temperature sensor bulb situated at or near the gas cooler refrigerant outlet or at another location having a temperature representing the operating condition of the circuit, and a membrane arrangement regulating the set-point of the back-pressure controlling unit in a desired relation to the bulb temperature.
  • Finally it is preferred that carbon dioxide is applied as a refrigerant.
    • Brief description of the drawings
  • The invention is described in more details by means of preferred embodiments and referring to the attached drawings, Figs. 1-3, where
    • Fig. 1
    is a graph illustrating the theoretical relationship between cooling capacity (Qo), compressor shaft power (P) and their ratio (COP) in the transcritical vapor compression cycle at varying high-side pressure, at constant evaporating temperature and gas cooler (condenser) outlet refrigerant temperature,
    Fig. 2
    is a graphic illustration of the theoretical relationship between optimum high-side pressure, providing maximum ratio between cooling capacity and shaft power, and gas cooler (condenser) outlet refrigerant temperature at three different evaporating temperatures, and
    Fig. 3
    is a schematic representation of a transcritical vapor compression cycle device constructed in accordance with a preferred embodiment of the invention.
    Detailed description of the Invention
  • A well known peculiarity of transcritical cycles (operating with the refrigerant compressed to a supercritical pressure in the high-side) is that the coefficient of performance COP, defined as the ratio between the refrigerating capacity and applied compressor shaft power, can be raised by increasing the high-side pressure, while the gas cooler (condenser) outlet refrigerant temperature is maintained mainly constant. This can be illustrated by means of a conventional pressure enthalpy diagram. However, the COP increases with increasing high-side pressure only up to a certain level and then begins to decline as the extra refrigerating effect no longer fully compensates for the extra work of compression.
  • Thus, for each set of actual operating conditions defined for instance by evaporating temperature and refrigerant temperature at the gas cooler (condenser) outlet, a diagram showing the cooling capacity (Qo), compressor shaft power (P) and their ratio (COP) as a function of high-side pressure can be provided. Fig. 1 illustrates such a diagram generated for refrigerant CO₂ at a constant evaporating and gas cooler (condenser) outlet temperature, based on theoretical cycle calculations. At a certain high-side pressure corresponding to p' in Fig. 1, the COP reaches a maximum as indicated.
  • By combining such results, i.e. corresponding data for gas cooler (condenser) outlet refrigerant temperature, evaporating temperature and high-side pressure providing maximum COP (p'), at varying operating conditions, a new set of data, as shown in Fig. 2, is provided, which may be applied in the throttling valve steering strategy. By regulating the high-side pressure in accordance with this diagram, a maximum ratio between refrigerating capacity and compressor shaft power will always be maintained.
  • Under maximum load conditions it still may be expedient to operate the system at a discharge pressure well above the level corresponding to maximum COP for a shorter period of time, to limit the compressor volume required and thereby the capital cost and overall energy consumption. At low load conditions, however, a combination of reduced high-side pressure to a predetermined optimum level and capacity regulation conducted by a separate control system will provide minimum energy consumption.
  • Since varying evaporating temperature has a noticeable effect only at high gas cooler (condenser) outlet refrigerant temperature, this influence may be neglected in practice. Thus the detected refrigerant temperature at the gas cooler (condenser) outlet or some other temperature or parameter corresponding to this (e.g. cooling water inlet temperature, ambient air temperature, cooling or heating load) will be the only significant steering parameter required as input for control of the throttling valve.
  • The use of a back-pressure controller as throttling valve may give certain advantages in that internal compensation for varying refrigerant mass flow and density is obtained. A throttling valve with back-pressure control will keep the inlet pressure, i.e. high-side pressure, at the set point regardless of refrigerant mass flow and inlet refrigerant temperature. The set-point of the back-pressure controller is then regulated by means of an actuator operating in accordance with the predetermined control scheme indicated above.
    • Example 1
  • Fig. 3 illustrates a preferred embodiment of the transcritical refrigerating circuit comprising a compressor 10 connected in series to a gas cooler (condenser) 11, an internal counterflow heat exchanger 12 and a throttling valve 13. An evaporator 14 and a low pressure liquid receiver 16 are connected intermediate the throttling valve and the compressor. A temperature sensor at the gas cooler (condenser) refrigerant outlet 5 provides information on the operating conditions of the circuit to the control system 7 e.g. a microprocessor. The throttling valve 13 is equipped with an actuator 9 and the valve position is automatically modulated in accordance with the predetermined set-point pressure characteristics by the control system.
    • Example 2
  • Referring to Figure 3 the circuit is now provided with a throttling valve 13 based on a simple mechanical back-pressure controller eliminating use of the microprocessor and electronic control of the valve shown in Example 1. The regulator is equipped with a temperature sensor bulb 5 situated at or near the gas cooler (condenser) refrigerant outlet.
  • Through a membrane arrangement, the pressure resulting from the sensor bulb temperature mechanically adjusts the set-point of the back-pressure controller according to the gas cooler (condenser) outlet refrigerant temperature. By adjusting spring forces and charge in the sensor 5 an appropriate relation between the temperature and pressure in the actual regulation range may be obtained.
    • Example 3
  • The circuit is based on one of the throttling valve control concepts described in Examples 1 or 2, but instead of locating the temperature sensor or sensor bulb at the gas cooler (condenser) refrigerant outlet, the sensor or sensor bulb measures the inlet temperature of the cooling agent to which heat is rejected. By counterflow heat exchange, there is a relation between gas cooler (condenser) refrigerant outlet and cooling medium inlet temperatures, as the refrigerant outlet temperature closely follows the cooling medium inlet temperature. The applied cooling medium is normally ambient air or cooling water.
  • While the invention has been illustrated and described in the drawings and foregoing description in terms of preferred embodiments it is apparent that changes and modifications may be made therein without departing from the spirit or scope of the invention as set forth in the appended claims. Thus, e.g. in any of the concepts described in Examples 1 or 2, the signal from a temperature sensor or bulb may be replaced by a signal representing the desired cooling or heating capacity of the system. Due to the correspondence between ambient temperature and load, this signal may serve as a basis for regulating throttling valve set-point pressure.

Claims (9)

  1. A method of controlling a transcritical vapor compression cycle device operating with supercritical high-side pressure and comprising a compressor (10), a gas cooler (11), an internal heat exchanger (12), a throttling valve (13), an evaporator (14) and a low pressure refrigerant receiver (16) connected in series into a circuit,
    characterized by
    the steps of detecting at least one of the actual operating conditions of the circuit and modulating the supercritical high-side pressure in accordance with a predetermined set of values which define the minimum energy consumption of the device for the detected operation conditions at given capacity requirements.
  2. The method according to claim 1,
    characterized in that
    said modulating of the supercritical high-side pressure is performed by controlling the degree of opening of the throttling valve (13).
  3. The method according to claims 1 or 2,
    characterized in that
    the detection of the operating condition is conducted by measurement of the refrigerant temperature adjacent an outlet (5) of the gas cooler (11).
  4. A vapor compression cycle device operating at supercritical pressure in the high-side and comprising a compressor (10), a gas cooler (11), an internal heat exchanger (12), a throttling valve (13), an evaporator (14) and a low pressure refrigerant receiver (16) connected in series into a circuit,
    characterized by
    means for detecting at least one operating condition of the circuit and control means (9), operatively connected to the detecting means, for modulating the supercritical high-side pressure in accordance with a predetermined set of high pressure values which define the minimum energy consumption of the device for the detected operating condition at given capacity requirements.
  5. The device according to claim 4,
    characterized in that
    said control means (9) is operatively connected to the throttling valve (13) and is adapted to control the degree of opening of the throttling valve (13).
  6. The device according to claim 4 or 5,
    characterized in that
    the detecting means comprises means for measuring a parameter representative of the refrigerant temperature adjacent an outlet (5) of the gas cooler (11).
  7. The device according to any of claims 4 to 6,
    characterized in that
    the throttling valve (13) is a back-pressure controlling unit with variable set-point electronically controlled by a microprocessor (7).
  8. The device according to any of claims 4 to 6,
    characterized in that
    the throttling valve (13) is a back-pressure controlling unit with variable set-point comprising a temperature sensor bulb situated at or near the gas cooler refrigerant outlet (5) or at another location having a temperature representing the operating condition of the circuit, and a membrane arrangement regulating the set-point of the back-pressure controlling unit in a desired relation to the bulb temperature.
  9. The device according to any of claims 4 to 8,
    characterized in that
    carbon dioxide is applied as a refrigerant.
EP91916351A 1991-09-16 1991-09-16 Control of high-side pressure in transcritical vapor compression cycle Expired - Lifetime EP0604417B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/NO1991/000119 WO1993006423A1 (en) 1991-09-16 1991-09-16 Method of high-side pressure regulation in transcritical vapor compression cycle device

Publications (2)

Publication Number Publication Date
EP0604417A1 EP0604417A1 (en) 1994-07-06
EP0604417B1 true EP0604417B1 (en) 1996-04-17

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EP (1) EP0604417B1 (en)
JP (1) JP2931668B2 (en)
KR (1) KR100245958B1 (en)
AT (1) ATE137009T1 (en)
AU (1) AU669473B2 (en)
BR (1) BR9107318A (en)
CA (1) CA2119015C (en)
DE (1) DE69118924T2 (en)
DK (1) DK0604417T3 (en)
ES (1) ES2088502T3 (en)
NO (1) NO180603C (en)
RU (1) RU2088865C1 (en)
WO (1) WO1993006423A1 (en)

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US6523365B2 (en) * 2000-12-29 2003-02-25 Visteon Global Technologies, Inc. Accumulator with internal heat exchanger
US6923011B2 (en) 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
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JP2000346472A (en) 1999-06-08 2000-12-15 Mitsubishi Heavy Ind Ltd Supercritical steam compression cycle
JP2001033115A (en) * 1999-07-16 2001-02-09 Zexel Valeo Climate Control Corp Refrigeration cycle
WO2001006183A1 (en) * 1999-07-16 2001-01-25 Zexel Valeo Climate Control Corporation Refrigerating cycle
FR2796595B1 (en) * 1999-07-22 2001-09-28 Valeo Climatisation REGULATOR DEVICE FOR AIR CONDITIONING CIRCUIT, PARTICULARLY A MOTOR VEHICLE
JP2001174076A (en) * 1999-10-08 2001-06-29 Zexel Valeo Climate Control Corp Refrigeration cycle
JP3838008B2 (en) * 2000-09-06 2006-10-25 松下電器産業株式会社 Refrigeration cycle equipment
NO20014258D0 (en) * 2001-09-03 2001-09-03 Sinvent As Cooling and heating system
US6568199B1 (en) 2002-01-22 2003-05-27 Carrier Corporation Method for optimizing coefficient of performance in a transcritical vapor compression system
EP1489367B1 (en) 2002-03-28 2011-08-24 Panasonic Corporation Refrigerating cycle device
JP2003294338A (en) * 2002-03-29 2003-10-15 Japan Climate Systems Corp Heat exchanger
JP4143434B2 (en) 2003-02-03 2008-09-03 カルソニックカンセイ株式会社 Vehicle air conditioner using supercritical refrigerant
DE10337136A1 (en) * 2003-08-11 2005-03-24 Behr Gmbh & Co. Kg Air conditioning and method for controlling the heating power of the same
US6959557B2 (en) 2003-09-02 2005-11-01 Tecumseh Products Company Apparatus for the storage and controlled delivery of fluids
US7096679B2 (en) 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
DE102004015297A1 (en) * 2004-03-29 2005-11-03 Andreas Bangheri Apparatus and method for cyclic vapor compression
JP4179231B2 (en) 2004-06-09 2008-11-12 株式会社デンソー Pressure control valve and vapor compression refrigeration cycle
JP4613526B2 (en) 2004-06-23 2011-01-19 株式会社デンソー Supercritical heat pump cycle equipment
DE602005025256D1 (en) 2005-02-18 2011-01-20 Carrier Corp METHOD FOR CONTROLLING HIGH PRESSURE IN A INTERMITTENTLY SUPERCRITICAL COOLING CIRCUIT
JP2007139342A (en) * 2005-11-21 2007-06-07 Mitsubishi Heavy Ind Ltd Air conditioner and pressure control valve for the same
JP2008064439A (en) * 2006-09-11 2008-03-21 Daikin Ind Ltd Air conditioner
US8157538B2 (en) 2007-07-23 2012-04-17 Emerson Climate Technologies, Inc. Capacity modulation system for compressor and method
CA2749562C (en) 2009-01-27 2014-06-10 Emerson Climate Technologies, Inc. Unloader system and method for a compressor
US10378533B2 (en) 2011-12-06 2019-08-13 Bitzer Us, Inc. Control for compressor unloading system
JP2013124802A (en) * 2011-12-14 2013-06-24 Panasonic Corp Refrigeration cycle apparatus
CN104937351B (en) * 2013-01-31 2017-09-01 开利公司 Many separation transport refrigeration systems with energy-saving appliance
CN112432376B (en) * 2020-11-24 2021-09-03 同济大学 Carbon dioxide refrigerating and freezing system and intelligent switching-mixing control method

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1591302A (en) * 1925-06-09 1926-07-06 William S Franklin Automatic expansion valve for refrigerating systems
US3413815A (en) * 1966-05-02 1968-12-03 American Gas Ass Heat-actuated regenerative compressor for refrigerating systems
US3400555A (en) * 1966-05-02 1968-09-10 American Gas Ass Refrigeration system employing heat actuated compressor
US3638446A (en) * 1969-06-27 1972-02-01 Robert T Palmer Low ambient control of subcooling control valve
GB1544804A (en) * 1977-05-02 1979-04-25 Commercial Refrigeration Ltd Apparatus for and methods of transferring heat between bodies of fluid or other substance
SE463533B (en) * 1987-04-13 1990-12-03 Handelsbolaget Heliovent Arrangement for temperature-based refrigerant control in a heat pump
NO890076D0 (en) * 1989-01-09 1989-01-09 Sinvent As AIR CONDITIONING.
US5042262A (en) * 1990-05-08 1991-08-27 Liquid Carbonic Corporation Food freezer

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0952344A2 (en) 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Flow control valve for a variable displacement refrigerant compressor
US6105380A (en) * 1998-04-16 2000-08-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
US6260369B1 (en) 1998-04-16 2001-07-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Flow control valve for a variable displacement refrigerant compressor
US6182456B1 (en) 1998-04-20 2001-02-06 Denso Corporation Supercritical refrigerating cycle system
DE19917048B4 (en) * 1998-04-20 2005-11-03 Kabushiki Kaisha Toyota Jidoshokki, Kariya Supercritical refrigeration cycle system
US6523365B2 (en) * 2000-12-29 2003-02-25 Visteon Global Technologies, Inc. Accumulator with internal heat exchanger
US6923011B2 (en) 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
DE102005044029B3 (en) * 2005-09-14 2007-03-22 Stiebel Eltron Gmbh & Co. Kg Heat pump for heating water for heating purposes comprises a coolant circuit operated in the supercritical region and having a de-super heater, a vaporizer, a compressor and a throttle valve and a control unit

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CA2119015A1 (en) 1993-04-01
JP2931668B2 (en) 1999-08-09
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ATE137009T1 (en) 1996-05-15
AU669473B2 (en) 1996-06-13
WO1993006423A1 (en) 1993-04-01
JPH06510111A (en) 1994-11-10
NO940936L (en) 1994-03-16
EP0604417A1 (en) 1994-07-06
AU8530191A (en) 1993-04-27
NO940936D0 (en) 1994-03-16
DE69118924T2 (en) 1996-11-21
NO180603C (en) 1997-05-14
RU2088865C1 (en) 1997-08-27
NO180603B (en) 1997-02-03
ES2088502T3 (en) 1996-08-16
CA2119015C (en) 2002-07-09
RU94030805A (en) 1997-04-20
DE69118924D1 (en) 1996-05-23
BR9107318A (en) 1995-11-07
DK0604417T3 (en) 1996-08-26

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