WO1993006423A1 - Method of high-side pressure regulation in transcritical vapor compression cycle device - Google Patents

Method of high-side pressure regulation in transcritical vapor compression cycle device Download PDF

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Publication number
WO1993006423A1
WO1993006423A1 PCT/NO1991/000119 NO9100119W WO9306423A1 WO 1993006423 A1 WO1993006423 A1 WO 1993006423A1 NO 9100119 W NO9100119 W NO 9100119W WO 9306423 A1 WO9306423 A1 WO 9306423A1
Authority
WO
WIPO (PCT)
Prior art keywords
throttling valve
pressure
refrigerant
gas cooler
circuit
Prior art date
Application number
PCT/NO1991/000119
Other languages
French (fr)
Inventor
Gustav Lorentzen
Jostein Pettersen
Roar Rektorli Bang
Original Assignee
Sinvent 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
Priority to DK91916351.9T priority Critical patent/DK0604417T3/en
Priority to AU85301/91A priority patent/AU669473B2/en
Priority to JP3515570A priority patent/JP2931668B2/en
Priority to EP91916351A priority patent/EP0604417B1/en
Priority to ES91916351T priority patent/ES2088502T3/en
Priority to AT91916351T priority patent/ATE137009T1/en
Priority to PCT/NO1991/000119 priority patent/WO1993006423A1/en
Priority to RU9194030805A priority patent/RU2088865C1/en
Application filed by Sinvent A/S filed Critical Sinvent A/S
Priority to CA002119015A priority patent/CA2119015C/en
Priority to DE69118924T priority patent/DE69118924T2/en
Priority to BR9107318A priority patent/BR9107318A/en
Publication of WO1993006423A1 publication Critical patent/WO1993006423A1/en
Priority to KR1019940700840A priority patent/KR100245958B1/en
Priority to NO940936A priority patent/NO180603C/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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 con ⁇ sumption-
  • a co-pending PCT application, publication No. WO 90/07683, 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 ex ⁇ changer, 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 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 con ⁇ sumption at the given capacity requirement.
  • the actual opera ⁇ ting conditions may be defined by refrigerant temperatures or pressures, by external temperatures or by the capacity re ⁇ quirements.
  • 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 throttling valve control strategy to obtain optimal operation with respect to energy consumption of the disclosed vapor compression device.
  • a steering strategy for the throttling valve in the transcritical vapor compression circuit based on application of predetermined values of optimal high-side pressure corresponding to the detected actual operating conditions of the circuit.
  • the detection of the operating conditions is done by measurement of a temperature at or near the gas cooler (con ⁇ denser) outlet, and the valve position is modulated to the predetermined set-point pressure by an appropriate control system.
  • Fig. 1 is a graph illustrating the theoretical relationship between cooling capacity (Q 0 ) , compressor shaft power
  • Fig. 2 is a graphic illustration of the theoretical re ⁇ lationship between optimum high-side pressure, providing maximum ratio between cooling capacity and shaft power, and gas cooler (condenser) outlet refrigerant temperature at three different evapora ⁇ ting temperatures, and
  • Fig. 3 is a schematic representation of a transcritical vapor compression cycle device constructed in ac ⁇ cordance with a preferred embodiment of the inven ⁇ tion. 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.
  • 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 0 ) , compressor shaft power (P) and their ratio (COP) as a function of high-side pressure can be pro ⁇ vided.
  • Fig. 1 illustrates such a diagram generated for refrig ⁇ erant C0 2 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 sig ⁇ nificant 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 pre ⁇ determined 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 inter ⁇ mediate 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 microprosessor.
  • 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 l.
  • 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.

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

Method of high-side pressure regulation in transcritical vapor compression cycle device
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 con¬ sumption-
Background of the Invention
A co-pending PCT application, publication No. WO 90/07683, 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 ex¬ changer, 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 con¬ sumption at the given capacity requirement. The actual opera¬ ting conditions may be defined by refrigerant temperatures or pressures, by external temperatures or by the capacity re¬ quirements. 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 throttling valve control strategy to obtain optimal operation with respect to energy consumption of the disclosed vapor compression device.
Object of the invention
It is therefore an object of the present invention to provide a new simple method and means for regulating the high-side pressure in a transcritical vapor compression circuit to achieve minimum energy consumption and optimum operation of the system.
Summary of the invention
The above and other objects of the present invention are achieved by provision of a steering strategy for the throttling valve in the transcritical vapor compression circuit based on application of predetermined values of optimal high-side pressure corresponding to the detected actual operating conditions of the circuit. In a preferred embodiment of the invention, the detection of the operating conditions is done by measurement of a temperature at or near the gas cooler (con¬ denser) outlet, and the valve position is modulated to the predetermined set-point pressure by an appropriate control system.
Brief description of the drawings
The invention is described in more details by means of pre¬ ferred embodiments and referring to the attached drawings, Figs. 1-3, where
Fig. 1 is a graph illustrating the theoretical relationship between cooling capacity (Q0) , 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 re¬ lationship between optimum high-side pressure, providing maximum ratio between cooling capacity and shaft power, and gas cooler (condenser) outlet refrigerant temperature at three different evapora¬ ting temperatures, and
Fig. 3 is a schematic representation of a transcritical vapor compression cycle device constructed in ac¬ cordance with a preferred embodiment of the inven¬ tion. 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 (Q0) , compressor shaft power (P) and their ratio (COP) as a function of high-side pressure can be pro¬ vided. Fig. 1 illustrates such a diagram generated for refrig¬ erant C02 at a constant evaporating and gas cooler (condenser) outlet temperature, based on theoretical cycle calculations. At a certain high-side pressure corresponding to p1 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 tempe¬ rature, 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 sig¬ nificant 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 pre¬ determined 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 inter¬ mediate 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 microprosessor. 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 l. 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 tempera¬ ture. 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

Claims
1. Method of modulating high-side pressure in a trans¬ critical vapor compression device 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, c h a r a c t e r i z e d i n t h a t the method comprises steps of detecting at least one of the actual operating conditions of the circuit and modulation of the throttling valve position in accordance with a predetermined set of high pressure values to achieve minimum energy consumption of the device at given capacity requirements.
2. Method according to claim 1, c h a r a c t e r i z e d i n t h a t the detection of the operating conditions is con¬ ducted by measurement of the refrigerant temperature adjacent an outlet of the gas cooler.
3. A method according to claim 1 or 2 c h a r a c t e r i z e d i n t h a t carbon dioxide is applied as a refrigerant.
4. A vapor compression cycle device operating at super¬ critical 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) con¬ nected in series into a circuit, c h a r a c t e r i z e d i n t h a t the device further comprises means (5) for detecting at least one operating condition of the circuit and control means (9) , operatively connected to the detecting means and to the throttling valve, for controlling the degree of opening of the throttling valve as a function of the detected operating condition in accordance with a predetermined set of high pressure values to achieve minimum energy con¬ sumption at given capacity requirements.
5. Device according to claim 4 , c h a r a c t e r i z e d i n t h a t the detecting means (5) comprises means for measuring a parameter representative of the refrigerant tem¬ perature adjacent an outlet of the gas cooler.
6. Device according to claim 4 or 5, where the throttling valve (13) is a back-pressure controlling unit with variable set-point electronically controlled by a microprosessor (7) .
7. Device according to claim 5, where 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 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. AMENDED CLAIMS
[received by the International Bureau on 12 January 1993 (12.01.93); original claims 1 and 4 amended; rem_tining claims unchanged (2 pages)]
1. Method of modulating high-side pressure in a trans¬ critical vapor compression device operating with super¬ critical high-side pressure and comprising a com¬ pressor, a gas cooler, an internal heat exchanger, an expansion means, an evaporator and a low pressure refrigerant receiver connected in series into a circuit, c h a r a c t e r i z e d i n t h a t the method comprises steps of detecting at least one of the actual operating conditions of the circuit and modulation of the supercritical high-side pressure in accordance with a predetermined set of values to achieve minimum energy consumption of the device at given capacity requirements.
2. Method according to claim 1, c h a r a c t e r i z e d i n t h a t the detection of the operating conditions is conducted by measurement of the refrigerant temperature adjacent an outlet of the gas cooler.
3. A method according to claim 1 or 2 c h a r a c t e r i z e d i n t h a t carbon dioxide is applied as a refrigerant.
4. A vapor compression cycle device operating at super¬ critical 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) con¬ nected in series into a circuit, c h a r a c t e r i z e d i n t h a t the device further comprises means (5) for detecting at least one operating condition of the circuit and control means (9) , operatively connected to the detecting means (5) and to the throttling valve, for modulation of the supercritical high-side pressure by controlling the degree of opening of the throttling valve as a function of the detected operating condi¬ tion in accordance with a predetermined set of high pressure values.
5. Device according to claim 4, c h a r a c t e r i z e d i n t h a t the detecting means (5) comprises means for measuring a parameter representative of the refrigerant tem¬ perature adjacent an outlet of the gas cooler.
6. Device according to claim 4 or 5, where the throttling valve (13) is a back-pressure controlling unit with variable set-point electronically controlled by a microprosessor (7) .
7. Device according to claim 5, where 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 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. Statement under Artice 19(1)
The actual amendments of claims 1 and 4 are made in order to more distinctly define our present invention compared to the conven¬ tional systems where expansion/throt ling valves are applied for controlling the refrigerant flow to the evaporator by varying the valve position. The subcritical, high-side pressure in conventional systems is not directly affected by the throttling valve position.
In the present transcritical system the throttling valve is applied for control of the supercritical high-side pressure at substanti¬ ally constant refrigerant flow.
PCT/NO1991/000119 1991-09-16 1991-09-16 Method of high-side pressure regulation in transcritical vapor compression cycle device WO1993006423A1 (en)

Priority Applications (13)

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
JP3515570A JP2931668B2 (en) 1991-09-16 1991-09-16 High side pressure regulation method in supercritical vapor compression circuit
EP91916351A EP0604417B1 (en) 1991-09-16 1991-09-16 Control of high-side pressure in transcritical vapor compression cycle
ES91916351T ES2088502T3 (en) 1991-09-16 1991-09-16 PRESSURE CONTROL ON THE HIGH PRESSURE SIDE IN A TRANSCRITICAL STEAM COMPRESSION CYCLE.
AT91916351T ATE137009T1 (en) 1991-09-16 1991-09-16 HIGH PRESSURE CONTROL IN A TRANSCRITICAL STEAM COMPRESSION CIRCUIT
DK91916351.9T DK0604417T3 (en) 1991-09-16 1991-09-16 Control of pressure on the high pressure side in a transcritical vapor compression cycle
RU9194030805A RU2088865C1 (en) 1991-09-16 1991-09-16 Method of control of pressure at delivery side in steam-compression cycle plant at supercritical compression of steam (versions) and plant for realization of this method
AU85301/91A AU669473B2 (en) 1991-09-16 1991-09-16 Method of high-side pressure regulation in transcritical vapor compression cycle device
CA002119015A CA2119015C (en) 1991-09-16 1991-09-16 Method of high-side pressure regulation in transcritical vapor compression cycle device
DE69118924T DE69118924T2 (en) 1991-09-16 1991-09-16 HIGH PRESSURE CONTROL IN A TRANSCRITICAL VAPOR COMPRESSION CIRCUIT
BR9107318A BR9107318A (en) 1991-09-16 1991-09-16 High side pressure modulation process in a transcritical vapor compression device, and vapor compression cycle device
KR1019940700840A KR100245958B1 (en) 1991-09-16 1994-03-15 Vapor compression cycle device and the method of high side pressure regulation in the device
NO940936A NO180603C (en) 1991-09-16 1994-03-16 Method of high pressure regulation in a transcritical compression cooling system and a compression cooling system for carrying out the same

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 (1)

Publication Number Publication Date
WO1993006423A1 true WO1993006423A1 (en) 1993-04-01

Family

ID=19907665

Family Applications (1)

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

Country Status (13)

Country Link
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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WO1994014016A1 (en) * 1992-12-11 1994-06-23 Sinvent A/S Trans-critical vapour compression device
EP0701096A3 (en) * 1994-09-09 1997-11-12 Daimler-Benz Aktiengesellschaft Method for operating a cold producing installation for air conditioning of vehicles and cold producing installation carrying out the same
WO1998030847A1 (en) * 1997-01-08 1998-07-16 Norild As Refrigeration system with closed circuit circulation
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US6343486B1 (en) 1999-06-08 2002-02-05 Mitsubishi Heavy Industries, Ltd. Supercritical vapor compression cycle
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US7302807B2 (en) 2002-03-28 2007-12-04 Matsushita Electric Industrial Co., Ltd. Refrigerating cycle device
US6895769B2 (en) 2003-02-03 2005-05-24 Calsonic Kansei Corporation Air conditioning apparatus using supercritical refrigerant for vehicle
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US7607315B2 (en) 2004-06-09 2009-10-27 Denso Corporation Pressure control valve and vapor-compression refrigerant cycle system using the same
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US8157538B2 (en) 2007-07-23 2012-04-17 Emerson Climate Technologies, Inc. Capacity modulation system for compressor and method
US8807961B2 (en) 2007-07-23 2014-08-19 Emerson Climate Technologies, Inc. Capacity modulation system for compressor and method
US8308455B2 (en) 2009-01-27 2012-11-13 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
CN112432376A (en) * 2020-11-24 2021-03-02 同济大学 Carbon dioxide refrigerating and freezing system and intelligent switching-mixing control method

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BR9107318A (en) 1995-11-07
NO940936D0 (en) 1994-03-16

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