US2772543A - Multiple hydraulic compressor in a refrigeration system - Google Patents

Multiple hydraulic compressor in a refrigeration system Download PDF

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US2772543A
US2772543A US344359A US34435953A US2772543A US 2772543 A US2772543 A US 2772543A US 344359 A US344359 A US 344359A US 34435953 A US34435953 A US 34435953A US 2772543 A US2772543 A US 2772543A
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container
gas
compressor
refrigeration system
liquid
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0011Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons liquid pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/02Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows
    • F04B45/033Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive
    • F04B45/0336Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having bellows having fluid drive the actuating fluid being controlled by one or more valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00Compressor arrangements

Definitions

  • Claim. (Cl. 62-115)
  • the invention relates to refrigeration systems.
  • each container consists of a rigid outer vessel and a flexible inner vessel, the pump conduit being connected to discharge liquid into the rigid outer vessel and the flexible inner vessel being connected to the discharge conduit for compressed gas, this latter conduit being the one which leads to the condenser intake.
  • freon gas or other refrigerant does not come in contact with mechanical elements of the pump as they are required to do in a compressor. This permits the use of lower cost construction as it is not necessary to employ the high priced materials now utilized in compressors for air conditioning systems.
  • Fig. 1 is a diagrammatic view of a refrigeration system utilizing my invention.
  • Fig. 2 is a similar view showing a modified construction.
  • Fig. 1 my apparatus has been shown in its relation to the condenser, receiver, expansion valve and evaporator of a typical freon gas refrigeration system. These elements may be of any well known type and may be arranged in the usual manner for any desired purpose or application.
  • My invention comprises apparatus for compressing a gas in such a refrigeration system, including two containers 3, 4 each arranged for confining both a liquid L and a gas G under pressure, an hydraulic pump 5 driven from any suitable power source, conduits 6, 7 connecting the pump to the respective containers, means such as the control valve 8 for stopping the flow of fluid through the conduits, and means such as the control valve 8 for reversing said flow so that each container acts alternately as a compressor and as an expander, compressing while the other container is expanding, and vice versa.
  • container 3 consits of a rigid outer vessel and a flexible inner vessel 9 of neoprene or other suitable material.
  • Vessel 9 is shown in its expanded condition.
  • a similar vessel 10 which forms a part of container 4 is shown in contracted condition.
  • Conduits 6 and 7 connect the pump to the rigid outer vessels 4 and 3, respectively, and the flexible inner vessels 9 and 19 are connected to the discharge conduits 11 and 12 for compressed gas and for return of the low pressure gas from the evaporator.
  • Conduits 11 and 12 are connected by conduits 13 and 14 to the condenser intake, and by conduits 1'5 and 16 to the evaporator discharge.
  • Check valves 17, 1'8, 19 and 20 permit unidirectional .flow of gas into the condenser and from the evaporator discharge, alternately as determined by pressure conditions.
  • Pressure responsive electric switches 21 and 22 are mounted in the containers 3 and 4 and are connected in parallel to a relay 23 arranged to operate a solenoid to control the position of valve 8.
  • a thermostatic control 24 is connected to relay 23 to activate the relay when additional cooling is required.
  • Fig. 1 The condition illustrated in Fig. 1 is that which obtains when flow of the oil, or other hydraulic liquid, is in the direction indicated by the arrows superimposed on conduits 6 and 7.
  • container 4 is acting as a compressor, and container 3 is acting as an expander.
  • the flexible inner vessel 10 contracts, and as the oil leaves container 3, the flexible inner vessel 9 expands.
  • Compressed gas flows from container 4 past check valve 18 as needed to meet refrigeration requirements, while low pressure gas from the evaporator discharge is drawn into container 3 as the suction oil leaves that container.
  • the modified construction shown in Fig. 2 is the same as the construction shown in Fig. 1 except as follows:
  • the containers 3 and 4 are used without flexible inner vessels so that the hydraulic liquid comes into direct contact with the refrigerant gas.
  • the hydraulic fluid should be one in which the gas will not dissolve.
  • the controls 21' and 22 may be liquid level switches.
  • Valve 8 is pressure-actuated by operation of the pump 5 in either direction. When pumping stops, this valve is spring-actuated to return it to a neutral position, cutting off flow in both directions.
  • This apparatus operates in the same manner as that of Fig. 1 insofar as concerns the cycle of compression and expansion of the refrigerant gas in containers 3 and 4-.
  • the reversible motor 25 can be replaced by another power source and the solenoid valve 8 of Fig. 1 substituted for the arrangement here shown. Also it may be possible to employ just one of the containers 3, 4, 3, 4 in a system where it is used alternately as a compressor and an expander.
  • a refrigeration system In a refrigeration system, two reservoirs for expanded refrigerant, said reservoirs being directly connected to a condenser and evaporating system, a hydraulic pump connected to said reservoirs for pumping liquid out of one of said reservoirs through the pump and directly into the other of said reservoirs and alternately to return liquid from said other reservoir to the first reservoir, each reservoir arranged to receive expanded refrigerant from the condenser and evaporating system when said hydraulic pump is removing liquid from said reservoir and transferring said liquid into the other reservoir, and each reservoir further arranged to deliver compressed refrigerant to the condenser and evaporating system when said hydraulic pump is forcing liquid from said other reservoir back into the first reservoir.

Description

1956 F. BERRY MULTIPLE HYDRAULIC COMPRESSOR IN A REFRIGERATION SYSTEM Filed March 24, 1953 CONDENSER RECEIVER EXPANSION VALVE E VAPORA TOR I CONDENSER l4 RECEIVER EXPANSIUN VAL v5 E VAPOR/1T0 INVENTOR. FRANK BERRY BY Q4- ATTOR/VEYS United States Patent MULTIPLE HYDRAULIC COMPRESSOR IN A REFRIGERATION SYSTEM Frank Berry, Corinth, Miss.
Application March 24, 1953, Serial No. 344,359
1 Claim. (Cl. 62-115) The invention relates to refrigeration systems.
Summary Conventional types of refrigeration systems as employed commonly today require the use of gas compressors which act directly on the gas to compress it. According to my invention the gas is compressed hydraulically through the use of an hydraulic pump, doing away entirely with a compressor in the usual sense of the word. This I have accomplished by providing in a refrigeration system a gas compressing apparatus comprising two containers each arranged for confining both a liquid and a gas under pressure, and an hydraulic pump connected by conduits to each of these containers. Liquid is pumped into one of the containers to reduce the volume of the space available for gas within it. The pump receives liquid from the other container to increase the volume of the space available for gas in this other container. Means are provided for stopping the flow of liquid, and also for reversing the flow so that each container acts alternately as a compressor and as an expander, compressing while the other container is expanding, and vice versa.
In my preferred construction each container consists of a rigid outer vessel and a flexible inner vessel, the pump conduit being connected to discharge liquid into the rigid outer vessel and the flexible inner vessel being connected to the discharge conduit for compressed gas, this latter conduit being the one which leads to the condenser intake.
By eliminating the need for the usual gas compressor, many advantages are realized. For one thing, a tiny hydraulic pump when employed in my system will displace a sizeable compressor, with resultant decrease in both Weight and cost. The reduction in weight is a particularly important factor in refrigeration equipment for railroad cars, trucks, automobiles and airplanes. Also my system makes it possible to utilize the high volumetric efiiciency of an hydraulic pump in place of the relatively low volumetric efficiency of the ordinary compressor. Moreover, the efficiency of the hydraulic pump remains high over a wide range of operating speeds which is particularly important in refrigeration for automotive vehicles as it permits the use of a direct drive from the prime mover or from a simple jack shaft. Another advantage of my system is that the freon gas or other refrigerant does not come in contact with mechanical elements of the pump as they are required to do in a compressor. This permits the use of lower cost construction as it is not necessary to employ the high priced materials now utilized in compressors for air conditioning systems.
Description In the drawings, I have illustrated two embodiments which represent the best mode known to me for carrying out my invention.
Fig. 1 is a diagrammatic view of a refrigeration system utilizing my invention.
ice
Fig. 2 is a similar view showing a modified construction.
Referring first to Fig. 1, my apparatus has been shown in its relation to the condenser, receiver, expansion valve and evaporator of a typical freon gas refrigeration system. These elements may be of any well known type and may be arranged in the usual manner for any desired purpose or application. My invention comprises apparatus for compressing a gas in such a refrigeration system, including two containers 3, 4 each arranged for confining both a liquid L and a gas G under pressure, an hydraulic pump 5 driven from any suitable power source, conduits 6, 7 connecting the pump to the respective containers, means such as the control valve 8 for stopping the flow of fluid through the conduits, and means such as the control valve 8 for reversing said flow so that each container acts alternately as a compressor and as an expander, compressing while the other container is expanding, and vice versa.
In the particular construction here shown, container 3 consits of a rigid outer vessel and a flexible inner vessel 9 of neoprene or other suitable material. Vessel 9 is shown in its expanded condition. A similar vessel 10 which forms a part of container 4 is shown in contracted condition. Conduits 6 and 7 connect the pump to the rigid outer vessels 4 and 3, respectively, and the flexible inner vessels 9 and 19 are connected to the discharge conduits 11 and 12 for compressed gas and for return of the low pressure gas from the evaporator. Conduits 11 and 12 are connected by conduits 13 and 14 to the condenser intake, and by conduits 1'5 and 16 to the evaporator discharge. Check valves 17, 1'8, 19 and 20 permit unidirectional .flow of gas into the condenser and from the evaporator discharge, alternately as determined by pressure conditions.
Pressure responsive electric switches 21 and 22 are mounted in the containers 3 and 4 and are connected in parallel to a relay 23 arranged to operate a solenoid to control the position of valve 8. A thermostatic control 24 is connected to relay 23 to activate the relay when additional cooling is required. These pressure responsive switches, thermostatic control and relay may be of the kinds commonly employed for analogous purposes.
Operation The condition illustrated in Fig. 1 is that which obtains when flow of the oil, or other hydraulic liquid, is in the direction indicated by the arrows superimposed on conduits 6 and 7. Under this condition container 4 is acting as a compressor, and container 3 is acting as an expander. As the oil enters container 4, the flexible inner vessel 10 contracts, and as the oil leaves container 3, the flexible inner vessel 9 expands. Thus the volume of the space available for gas within container 4 is reduced, and the volume of the space available for gas Within container 3 is increased. Compressed gas flows from container 4 past check valve 18 as needed to meet refrigeration requirements, while low pressure gas from the evaporator discharge is drawn into container 3 as the suction oil leaves that container.
As soon as all the gas in high pressure container 4 has been forced out, the pressure will increase to a point which actuates the pressure responsive switch 22. This in turn actuates relay 23 and the solenoid to place valve 8 in its neutral position, blocking off the flow of oil in conduits 6 and 7. When additional cooling is required, relay 23 is again actuated, this time by the thermostatic control 24, placing valve 8 in position to produce flow of oil in the direction opposite to that previously described, pumping oil into container 3 and out of container 10. Thus container 3 now becomes the high pressure unit, or compressor, and container 4 the low pressure unit, or expander. Upon completion of a cycle, the pressure responsive switch 21 will actuate relay 23 to place valve 8 again in its neutral position. Any pressure remaining in either container will be added to the suction side of the pump, reducing such power losses as otherwise would be expected to occur.
The modified construction shown in Fig. 2 is the same as the construction shown in Fig. 1 except as follows: The containers 3 and 4 are used without flexible inner vessels so that the hydraulic liquid comes into direct contact with the refrigerant gas. The hydraulic fluid should be one in which the gas will not dissolve. For use with freon gas, I suggest glycerin as the hydraulic liquid. The controls 21' and 22 may be liquid level switches. Relay 23, instead of actuating the valve 8' through a solenoid, controls the starting, stopping and reverse starting of a reversible motor 25. Valve 8 is pressure-actuated by operation of the pump 5 in either direction. When pumping stops, this valve is spring-actuated to return it to a neutral position, cutting off flow in both directions. This apparatus operates in the same manner as that of Fig. 1 insofar as concerns the cycle of compression and expansion of the refrigerant gas in containers 3 and 4-.
If desired, the reversible motor 25 can be replaced by another power source and the solenoid valve 8 of Fig. 1 substituted for the arrangement here shown. Also it may be possible to employ just one of the containers 3, 4, 3, 4 in a system where it is used alternately as a compressor and an expander.
The terms and expressions which I have employed are used in a descriptive and not a limiting sense, and I have no intention of excluding such equivalents of the invention described, or of portions thereof, as fall within the purview of the claim.
I claim:
In a refrigeration system, two reservoirs for expanded refrigerant, said reservoirs being directly connected to a condenser and evaporating system, a hydraulic pump connected to said reservoirs for pumping liquid out of one of said reservoirs through the pump and directly into the other of said reservoirs and alternately to return liquid from said other reservoir to the first reservoir, each reservoir arranged to receive expanded refrigerant from the condenser and evaporating system when said hydraulic pump is removing liquid from said reservoir and transferring said liquid into the other reservoir, and each reservoir further arranged to deliver compressed refrigerant to the condenser and evaporating system when said hydraulic pump is forcing liquid from said other reservoir back into the first reservoir.
References Cited in the file of this patent UNITED STATES PATENTS 225,930 Hoster Mar. 30, 1880 326,545 Class Sept. 22, 1885 514,608 Weatherhead Feb. 13, 1894 1,353,216 Carlson Sept. 21, 1920 1,436,443 Holmes Nov. 21, 1922 1,508,833 Weber Sept. 16, 1924 1,780,335 Canton Nov. 4, 1930 2,039,999 Holyfield May 5, 1936 2,061,869 Gilbert Nov. 24, 1936 2,258,415 Lago Oct. 7, 1941 2,478,321 Robbins Aug. 9, 1949 2,644,401 Ragland July 7, 1953 2,679,732 Dolz June 1, 1954 FOREIGN PATENTS 444,845 Great Britain Mar. 30, 1936 975,954 France Mar. 12, 1951
US344359A 1953-03-24 1953-03-24 Multiple hydraulic compressor in a refrigeration system Expired - Lifetime US2772543A (en)

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Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2883835A (en) * 1955-10-05 1959-04-28 Cornelius P Pikey Method and apparatus for portable refrigeration cycle
US2914924A (en) * 1958-12-01 1959-12-01 George B Murphy Refrigeration system
US2916200A (en) * 1956-08-17 1959-12-08 Arthur V Jackson Compressor for refrigeration system
US2941375A (en) * 1956-08-31 1960-06-21 Tulacz Piotr Plant for the production of oxygen
US3045436A (en) * 1959-12-28 1962-07-24 Ibm Pneumatic expansion method and apparatus
US3255601A (en) * 1961-11-03 1966-06-14 Orpha B Brandon Methods and apparatus for utilizing implosive reactions in refrigeration and heat transfer processes
US3426545A (en) * 1966-10-21 1969-02-11 Clayton T Lloyd Generation of gas at high pressures
US3549503A (en) * 1968-10-09 1970-12-22 Harold R Hay Process and apparatus for the distillation of distilland displaced by distillate
US3684405A (en) * 1969-06-13 1972-08-15 Nat Res Dev Apparatus for pumping a fluid
US3742721A (en) * 1970-01-08 1973-07-03 Technip Cie Method of regulation of the temperature of the liquefied gas or gaseous mixture in an apparatus for the liquefaction of gaseous fluids
US3763663A (en) * 1972-07-31 1973-10-09 R Schlichtig Pneumatic powered diaphragm pump system for heat transfer
US4515516A (en) * 1981-09-30 1985-05-07 Champion, Perrine & Associates Method and apparatus for compressing gases
US4673415A (en) * 1986-05-22 1987-06-16 Vbm Corporation Oxygen production system with two stage oxygen pressurization
WO1992019924A1 (en) * 1991-05-04 1992-11-12 Hydrodynamique S.A. Holding Method and device providing isothermal compression of a compressible fluid
US5169295A (en) * 1991-09-17 1992-12-08 Tren.Fuels, Inc. Method and apparatus for compressing gases with a liquid system
FR2838181A1 (en) * 2002-04-08 2003-10-10 Lukac Dragoslaw High pressure hydraulic pump for feeding large number of air conditioning systems, comprises high pressure pump driving liquid gas from main reservoir to high pressure reservoir and output divider
DE102008041939A1 (en) 2008-09-10 2010-03-11 Ago Ag Energie + Anlagen A method of operating a heat pump or chiller or engine and heat pump or chiller and engine
WO2010063817A2 (en) * 2008-12-05 2010-06-10 Thermea. Energiesysteme Gmbh Device and method for compacting or compressing a gas
EP2273118A2 (en) 2009-06-02 2011-01-12 AGO AG Energie + Anlagen Cyclical process in a liquid piston converter
US20150128616A1 (en) * 2012-07-27 2015-05-14 Pressure Wave Systems Gmbh Compressor for a Cooling Device and a Refrigeration Machine
US20170175729A1 (en) * 2014-09-08 2017-06-22 Pressure Wave Systems Gmbh Cooling Device Equipped with a Compressor Device

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US225930A (en) * 1880-03-30 Theodore g
US326545A (en) * 1885-09-22 class
US514608A (en) * 1894-02-13 weatherhead
US1353216A (en) * 1918-06-17 1920-09-21 Edward P Carlson Hydraulic pump
US1436443A (en) * 1919-09-03 1922-11-21 Bradford B Holmes Pump
US1508833A (en) * 1919-05-29 1924-09-16 Frederick C Weber Refrigerating apparatus
US1780335A (en) * 1927-04-22 1930-11-04 Cantonice Corp Electrical pump
GB444845A (en) * 1934-03-06 1936-03-30 Mueller Friedrich Improvements in or relating to means for raising liquids
US2039999A (en) * 1935-02-04 1936-05-05 Earl F Holyfield Refrigeration compressor
US2061869A (en) * 1930-04-19 1936-11-24 Gilbert James Walter Refrigerating system
US2258415A (en) * 1938-03-11 1941-10-07 Lago Francis Refrigerating apparatus
US2478321A (en) * 1948-03-24 1949-08-09 James S Robbins Gas compressor
FR975954A (en) * 1948-09-23 1951-03-12 Refrigeration appliance device
US2644401A (en) * 1951-03-15 1953-07-07 Standard Oil Dev Co Apparatus for pumping drilling fluids
US2679732A (en) * 1951-01-12 1954-06-01 Dolz Heinrich Otto Herrmann Small electric refrigerating machine

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US225930A (en) * 1880-03-30 Theodore g
US326545A (en) * 1885-09-22 class
US514608A (en) * 1894-02-13 weatherhead
US1353216A (en) * 1918-06-17 1920-09-21 Edward P Carlson Hydraulic pump
US1508833A (en) * 1919-05-29 1924-09-16 Frederick C Weber Refrigerating apparatus
US1436443A (en) * 1919-09-03 1922-11-21 Bradford B Holmes Pump
US1780335A (en) * 1927-04-22 1930-11-04 Cantonice Corp Electrical pump
US2061869A (en) * 1930-04-19 1936-11-24 Gilbert James Walter Refrigerating system
GB444845A (en) * 1934-03-06 1936-03-30 Mueller Friedrich Improvements in or relating to means for raising liquids
US2039999A (en) * 1935-02-04 1936-05-05 Earl F Holyfield Refrigeration compressor
US2258415A (en) * 1938-03-11 1941-10-07 Lago Francis Refrigerating apparatus
US2478321A (en) * 1948-03-24 1949-08-09 James S Robbins Gas compressor
FR975954A (en) * 1948-09-23 1951-03-12 Refrigeration appliance device
US2679732A (en) * 1951-01-12 1954-06-01 Dolz Heinrich Otto Herrmann Small electric refrigerating machine
US2644401A (en) * 1951-03-15 1953-07-07 Standard Oil Dev Co Apparatus for pumping drilling fluids

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2883835A (en) * 1955-10-05 1959-04-28 Cornelius P Pikey Method and apparatus for portable refrigeration cycle
US2916200A (en) * 1956-08-17 1959-12-08 Arthur V Jackson Compressor for refrigeration system
US2941375A (en) * 1956-08-31 1960-06-21 Tulacz Piotr Plant for the production of oxygen
US2914924A (en) * 1958-12-01 1959-12-01 George B Murphy Refrigeration system
US3045436A (en) * 1959-12-28 1962-07-24 Ibm Pneumatic expansion method and apparatus
US3255601A (en) * 1961-11-03 1966-06-14 Orpha B Brandon Methods and apparatus for utilizing implosive reactions in refrigeration and heat transfer processes
US3426545A (en) * 1966-10-21 1969-02-11 Clayton T Lloyd Generation of gas at high pressures
US3549503A (en) * 1968-10-09 1970-12-22 Harold R Hay Process and apparatus for the distillation of distilland displaced by distillate
US3684405A (en) * 1969-06-13 1972-08-15 Nat Res Dev Apparatus for pumping a fluid
US3742721A (en) * 1970-01-08 1973-07-03 Technip Cie Method of regulation of the temperature of the liquefied gas or gaseous mixture in an apparatus for the liquefaction of gaseous fluids
US3763663A (en) * 1972-07-31 1973-10-09 R Schlichtig Pneumatic powered diaphragm pump system for heat transfer
US4515516A (en) * 1981-09-30 1985-05-07 Champion, Perrine & Associates Method and apparatus for compressing gases
US4673415A (en) * 1986-05-22 1987-06-16 Vbm Corporation Oxygen production system with two stage oxygen pressurization
WO1992019924A1 (en) * 1991-05-04 1992-11-12 Hydrodynamique S.A. Holding Method and device providing isothermal compression of a compressible fluid
US5169295A (en) * 1991-09-17 1992-12-08 Tren.Fuels, Inc. Method and apparatus for compressing gases with a liquid system
US5387089A (en) * 1991-09-17 1995-02-07 Tren Fuels, Inc. Method and apparatus for compressing gases with a liquid system
FR2838181A1 (en) * 2002-04-08 2003-10-10 Lukac Dragoslaw High pressure hydraulic pump for feeding large number of air conditioning systems, comprises high pressure pump driving liquid gas from main reservoir to high pressure reservoir and output divider
DE102008041939A1 (en) 2008-09-10 2010-03-11 Ago Ag Energie + Anlagen A method of operating a heat pump or chiller or engine and heat pump or chiller and engine
WO2010063817A2 (en) * 2008-12-05 2010-06-10 Thermea. Energiesysteme Gmbh Device and method for compacting or compressing a gas
DE102008060598A1 (en) * 2008-12-05 2010-06-10 Thermea. Energiesysteme Gmbh Apparatus and method for compressing or compressing a gas
WO2010063817A3 (en) * 2008-12-05 2011-01-06 Thermea. Energiesysteme Gmbh Device and method for compacting or compressing a gas
EP2273118A2 (en) 2009-06-02 2011-01-12 AGO AG Energie + Anlagen Cyclical process in a liquid piston converter
EP2273118A3 (en) * 2009-06-02 2012-10-03 AGO AG Energie + Anlagen Cyclical process in a liquid piston converter
US20150128616A1 (en) * 2012-07-27 2015-05-14 Pressure Wave Systems Gmbh Compressor for a Cooling Device and a Refrigeration Machine
US11231029B2 (en) * 2012-07-27 2022-01-25 Pressure Wave Systems Gmbh Compressor for a cooling device and a refrigeration machine
US20170175729A1 (en) * 2014-09-08 2017-06-22 Pressure Wave Systems Gmbh Cooling Device Equipped with a Compressor Device
CN107094367A (en) * 2014-09-08 2017-08-25 压力波系统股份有限公司 Compressor set, the cooling device for being equipped with the compressor set and the method for operating the compressor set and the cooling device
US11028841B2 (en) * 2014-09-08 2021-06-08 Pressure Wave Systems Gmbh Cooling device equipped with a compressor device

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