US3300996A - Variable capacity refrigeration system - Google Patents

Variable capacity refrigeration system Download PDF

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US3300996A
US3300996A US408272A US40827264A US3300996A US 3300996 A US3300996 A US 3300996A US 408272 A US408272 A US 408272A US 40827264 A US40827264 A US 40827264A US 3300996 A US3300996 A US 3300996A
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refrigerant
heat exchange
evaporator
compressed
compressor
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Atwood Theodore
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Allied Corp
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Allied Chemical Corp
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Priority to DE19651476691 priority patent/DE1476691A1/de
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    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves

Definitions

  • FIGURE 2 INVENTOR THEODORE ATWOOD BY ALWWW AT ORNEY United States Patent C) 3,300 996 VARIABLE CAPACETY REFRIGERATION SYSTEM Theodore Atwood, Sparta, N.J., assignor to Allied Chemical Corporation, New York, N.Y., a corporation of New York Filed Nov. 2, 1964, Ser. No. 408,272
  • This invention relates to a variable capacity refrigeration system and more particularly, to a variable capacity refrigeration system employing a novel method of varying the capacity over a relatively wide range and causing the refrigerating capacity to parallel the load requirement.
  • variable capacity is commonly obtained by means of a simple onolf switch controlled by temperature conditions in some part of the system, ordinarily the evaporator, or in the media being controlled. This occasions frequent starting and stopping of the system which results in considerable wear of motors, switches and controls and consequent shorter equipment life. This arrangement is particularly impractical for large commercial units used for low temperature applications and in which there are constant variations in load.
  • the evaporated refrigerant, or suction vapor, on its return to the compressor is divided into two parallel streams. At least one of these streams is conducted through a heat exchange zone in indirect heat exchange relationship with compressed re- Patented Jan.
  • the flow of evaporated refrigerant may be proportioned between the parallel branches to effect the extent of pre-cooling of condensed refrigerant.
  • part or all of total evaporated gas is flowed in indirect heat exchange relationship with condensed refrigerant to compensate for the refrigeration demand change.
  • the proportion of total flow of evaporated refrigerant subjected to such heat exchange may be reduced in conformity with the reduced demand.
  • the How of compressed refrigerant is regulated in response to changes in demand on refrigeration capacity, so as to divert at least a portion thereof through the heat exchange zones referred to above, either before or subsequent to condensation; diversion being effected of part or all of the compressed refrigerant, depending upon the magnitude and direction of the demand change and upon the proportion of evaporated gas being utilized for the pre-cooling.
  • a satisfactory arrangement includes delivery of compressed gas to one of the heat exchange zones and compressed condensate to the other. It will be evident to persons skilled in the art that control of the flows of compressed gas or condensate to the one or both heat exchange zones, whichever may be used, permits a nicety of control of refrigeration capacity, precisely satisfying increases or decreases in demand for that capacity.
  • the invention is applicable to systems containing commercial refrigerants, the choice of which, of course, depends upon the refrigeration temperature required; it is especially well adapted and functions most advantageously with refrigerants which are capable of operating satisfactorily over a relatively wide range of evaporating temperatures; for example, a range of F. to 50 F.
  • An excellent refrigerant, particularly well adapted for use in the system of the invention, is monochloropentafluoroethane which is capable of operation with satisfactory efiiciency at evaporating final temperatures within the range of 50 F. to 50 F. and, of course, at corresponding pressures.
  • FIG. 1 is a curve showing the relationship between refrigerating capacity, and temperature of liquid and vapor leaving the heat exchanger.
  • FIG. 2 is a schematic showing of the refrigeration system including controls.
  • FIG. 1 there is illustrated a curve indicating the range of capacity of GENETRON-IIS.
  • the data is based on a condensing temperature of F. and an evaporating temperature of 20 F.
  • the refrigerating capacity in B.t.u./hr. (vertical scale) is plotted against the temperature of the suction vapor leaving the heat exchanger in degrees F. (lower horizontal scale).
  • the corresponding temperature of the liquid leaving the heat exchanger which liquid is in indirect heat exchange relationship with the suction vapor, may be read from the upper horizontal scale in F. It can readily be seen from the curve in FIG.
  • FIG. 2 there is illustrated diagrammatically a typical system according to the practice of the invention showing refrigerant compressor 1 and thermal expansion valve 5, interconnected with compressed refrigerant line 7, which line contains condenser 2 and liquid receiver 3.
  • expanded refrigerant line 9 is divided into branched parallel segments 19 and 20.
  • Branches 19 and 20 each contain a heat exchange zone indicated generally at 6 and 21, respectively, comprising in the latter case,
  • by-pass 7B for line 7 contains a coil 24, disposed in heat exchange relationship with evaporated refrigerant branch 19 and in the same manner as described above, the How of condensed compressed refrigerant is proportioned between by-pass line 713 and line 7, by operation of valves 8 located in line 7 and by-pass line 7B, preferably controlled by temperature sensing device 13, by means of actuating lines 25.
  • valves 8, or valves 10 for that matter may be controlled manually.
  • valves 8 regulate the quantity of compressed refriger ant liquid flowing through heat exchange zone 6 and of compressed refrigerant liquid flowing directly to evaporating coil 4 through thermal expansion valve 5.
  • Valves 17 and 18 serve to regulate flow of evaporated refrigerant as between the divided parallel branches, 19 and 20, of the evaporated (expanded) refrigerant line 9 and can conveniently be valves which shut off flow to one branch, while permitting total flow through the other branch, such as solenoid valves.
  • a proportioning valve 16 is provided which permits flow of evaporated refrigerant to take place to a lesser or greater extent in either branch 19 or 20, or both, thus providing a modulating type flow a s,between segments 19 and 20.
  • Valve pairs 8 and 10 may be manipulated together with valve 16 or valves 17 and 18 so that evaporated refrigerant fiow can take place to the compressor, through either of segments 19 and 20 of expanded refrigerant line, or through both in any proportion, in (or out of) heat exchange relationship with compressed refrigerant passing through heat exchange zones 6 and 21.
  • sensing unit 13 responds to increased temperature in cooling space 14 surrounding evaporator 4, indicating an increased load; it causes control unit 12 to operate valve pairs 8 and 10 and/or valve 16 or, in place of valve 16, valves 17 and 18, if such are provided, by means of the appropriate actuating lines 15, 23 and 25, which connect the various valves with control unit 12, to direct a greater proportional flow of expanded refrigerant gas through heat exchange zone 6.
  • the cool expanded refrigerant vapor in segment 20 is directed to pass in indirect heat exchange relationship with the very warm refrigerant discharge vapor from the outlet of compressor I, conducted via by-pass 7A through heat exchange zone 21, the warm discharge vapor will be pre-cooled somewhat before condensation and subsequent evaporation, however, the relatively large offsetting effect of the increased volume of further expanded refrigerant vapor in the compressor, will cause less refrigerant to be pumped through the system and thus result in a net loss in refrigerating capacity.
  • the temperature and hence volume of the evaporated gas will also be increased after indirect heat exchange with the compressed condensate; the effect of change in evaporated gas volume is more than offset by the increase in evaporator capacity resulting from lower condensate temperature.
  • Heat exchange zone 21 when used alone, or in conjunction with heat exchange zone 6, serves a double purpose.
  • heat supplied from the warm compressed refrigerant vapor contained in compressed refrigerant vapor by-pass conduit 7A, to the refrigerant flowing in the compressor via expanded refrigerant segment 20, tends to keep the expanded refrigerant vapor in vaporous state and thus serves to protect the compressor against liquid slugging.
  • heat exchange zone 21 serves as a slugging preventative means.
  • Control unit 12 may operate electrically or by pressure and accordingly, actuating lines 15, 23 and 25 can be electric or pressure lines depending on choice of control. In a given case, depending on design requirements, any of the actuating lines may be deactivated and the valve pairs 8 and 10, and valve 16 or valves 17 and 18 preset to permit a predetermined refrigerant fiow with respect to heat exchange zones 6 and 21.
  • Sensing unit 13 may be any one of a number of conventional thermostatic control dcvices responsive to temperature change,
  • sensing bulb such as a sensing bulb similar to thermal valve sensing bulb ll, a bimetallic strip, or the like.
  • compressor 1 compresses and discharges used, relatively warm, gaseous refrigerant via compress-ed refrigerant conduit '7, directly to. condenser 2, by-passing heat exchange zone 21.
  • Condenser 2 serves to cool the gas and cause it to give up its latent heat of evaporation under high pressure. Under such conditions, the gas is converted to a liquid, which is collected in receiver 3, which serves to store said condensate until needed.
  • the compressed condensate then flows to evaporating unit 4, which is at reduced pressure, through valve pair 8, either directly through conduit 7 or indirectly through conduit 7B, which latter route passes through heat exchange zone 6.
  • the condensate evaporates, absorbing heat from surrounding medium 14 when converting to gaseous form, thus cooling said medium.
  • the flow of compressed condensate to evaporator 4 is regulated by thermal expansion valve 5.
  • This valve is connected to a temperature sensitive bulb 11 located at the outlet of the cooling unit. When this bulb is warmed, expansion of the fluid in it causes a diaphragm or bellows to which it is connected (not shown in the drawing) to expand, which in turn tends to open an expansion valve needle situated in valve 5 by means of electric or pressure actuating line 26, thus enabling the cooling coils of evaporator t to fill more completely and therefore cool more etficiently.
  • These mechanisms serve to control the flow of evaporated refrigerant, after it leaves the cooling coils in evaporator 4, through expanded refrigerant line or conduit 9 which is split or branched at the point indicated by 16, so that evaporated refrigerant can flow to the compressor via alternate routes.
  • One route carries the evaporated refrigerant through segment 19 and in heat exchange relationship with coil 24 of heat exchange zone 6.
  • the other route carries the evaporated refrigerant directly to the compressor, by-passing heat exchange zone 6.
  • the latter route may be optionally provided with an available auxiliary heat source, such as described heretofore, to assist in preventing liquid slugging in the compressor.
  • Segments l9 and of expanded refrigerant line 9 may, of course, connect with the compressor by means of separate suction inlets, however, as shown in the drawing, it is more expedient to reunite said segments at a point beyond either of heat exchange zones 6 or 21.
  • sensing device 13 when temperature rises in cooling space 14, indicating a heavier load, sensing device 13 is triggered which signals control unit 12, which in turn operates proportioning valve 16 to permit evaporated refrigerant to flow through segment 19 and heat exchange zone 6 and also valve pair 8 to permit compressed condensate to flow through condiut 7B and heat exchange zone 6.
  • control unit 12 opcrates valve pair Hi to direct compressed refrigerant away from by-pass conduit 7A and heat exchange zone 21.
  • the relatively cool evaporated refrigerant in segment 19 absorbs heat from the relatively warm compressed condensate in coil 24-.
  • the compressed condensate thus pre cooled, before flowing through cooling coils in evaporator 4, has increased capacity for absorbing heat from cooling space lid.
  • valve 16 When temperature in cooling space 14 falls, indicating a lighter load, the above-described sequence of events is triggered except that valve 16, is operated so as to cause evaporated refrigerant to flow through segment 20, by-passing heat exchange zone 6 and valve pair 8 is operated so as to direct compressed condensate directly to evaporator 4, by-passing conduit 78 and heat exchange zone 6.
  • valve 16 When temperature in cooling space 14 falls, indicating a lighter load, the above-described sequence of events is triggered except that valve 16, is operated so as to cause evaporated refrigerant to flow through segment 20, by-passing heat exchange zone 6 and valve pair 8 is operated so as to direct compressed condensate directly to evaporator 4, by-passing conduit 78 and heat exchange zone 6.
  • the pre-cooling effect of compressed condensate, feeding to the evaporator is diminished, resulting in a relative lowering of the refrigeratingcapacity of the system.
  • the overall result of the above-described arrangement is that the refrigeration capacity of the system at a given
  • refrigerant In general, in order for a substance to be useful as a refrigerant, it must have a low boiling point and in passing from a liquid to a gas, must absorb a high quantity of heat per pound. It is also desirable that the specific volume of the gas be small in order to minimize equipment size. Ideally, refrigerants should be .nonflammable, stable non-toxic, non-corrosive, non-explosive and non-injurious to lubricants used in the system. In the system according to the invention, it is desirable that the refrigerant employed have an additional thermodynamic property: viz. that the ratio of its specific heat of the vapor to its latent heat of evaporation be high.
  • the refrigerant should also be capable of operation over a wide range of evaporator temperatures. It has been found that GENETRON-IIS (chloropentafluoroethane) combines all of the above-described properties. It has a boiling point of 37.7 F., is highly stable, inert, nonflam mable, has no evident toxicity and is non-corrosive. Moreover, GENETRON-llS exhibits a wide capacity variation responsive to change in demand on cooling requirements, which capacity can readily be varied by use of heat exchange means such as employed herein.
  • GENETRON-IIS chloropentafluoroethane
  • refrigerants may be employed which have the above-described combination of properties.
  • a particular class of compounds, within which such refrigerants may be found, are the halogenated hydrocarbons containing one or more fluorine and/or chlorine atoms.
  • Representative compounds from this class, which would be useful in the practice of theinvention, are octafluorocyclobutane, perfluoropropane and chloroperfiuoropropane.
  • Useful refrigerants from without this class of chemical compounds, sulfur hexafluoride being exemplary, may be readily surmised by practitioners of the invention by study of thermodynamic data without departing from the spirit of the invention.
  • variations and embodiments may be developed which do not depart from the spirit of the invention and accordingly applicant intends to be limited only by the reasonable scope of the appended claims.
  • EXAMPLE 1 The system is as above-described in the illustrative cycle, excepting that all evaporated refrigerant (suction gas) is directed through segment 19, so as to pass in indirect heat exchange relationship with refrigerant condensate flowing through coil 24 of heat exchange zone 6. (See FIG. 2.)
  • the refrigerant employed is GENTRON- (chloropentafluoroethane) on a F. condensing -20 F. evaporating cycle.
  • Heat exchange zone 6 is so designed as to be capable of an approach of 10 F. between leaving liquid and vapor temperature. This system equalizes with a suction gas temperature of 62 F. and a refrigerant condensate temperature of 72 F.
  • EXAMPLE 2 The system is identical to that described in Example 1 excepting that all evaporated refrigerant (suction gas) is directed through segment 20, so as to pass in indirect heat exchange relationship with compressed refrigerant flowing through coil 22 of heat exchange zone 21. (See FIG. 2.)
  • the relatively warm compressed refrigerant gas gives up heat to the relatively cool suction vapor. (This may either be sensible heat or latent heat depending on the amount of super-heat present.)
  • Heat exchange zone 21 is sized to maintain the same suction gas temperature as before (+62 F.) and the specific volume of the suction vapor accordingly remains as before, viz. 1.56 cu. ft./1b.
  • sensing element 13 acts to proportion the flow between heat exchange zones 6 and 21 (or between heat exchange zone 6 or no heat exchange zone), thereby either increasing or decreasing the effective cooling, until a balance point is reached.
  • EXAMPLE 3 The system is identical to that of Example 1, excepting that monochlorodifiuoromethane is used as refrigerant. With the 120 F. condensing/20 F. evaporating cycle, the 10 F. approach in the heat exchange zone results in suction gas at a temperature of 72 F. In order to obtain a cooling capacity of 1120 B.t.u./hr. with heat exchange zone 6 in use, a compressor of .71 cu. ft./minute pumping capacity is required.
  • EXAMPLE 4 This system is identical to that of Example 3, excepting that all evaporated refrigerant (suction gas) is directed through heat exchange zone 21. System capacity is reduced to 913 B.t.u./hr., representing only an 18% reduction from maximum capacity.
  • EXAMPLE 5 This system is identical to that of Example 3, excepting that dichlorodilluoromethane is used as refrigerant. With the 120 F. condensing/20 F. evaporating cycle, the F. approach in the heat exchange zone results in suction gas at a temperature of 62 F. In order to obtain a cooling capacity of 1120 B.t.u./hr. with heat exchange zone 6 in use, a compressor of 1.09 cu. ft./minute pumping capacity is required.
  • EXAMPLE 6 This system is identical to that of Example 5, excepting that all evaporated refrigerant (suction gas) is directed through heat exchange zone 21. System capacity is reduced to 865 B.t.u./hr., representing only a 23% reduction from maximum capacity.
  • variable capacity refrigeration system comprising in combination:
  • a compressed refrigerant conduit including a condenser, a compressed refrigerant vapor portion and a compressed refrigerant condensate portion, connecting the compressor with the evaporator,
  • valve means disposed and arranged to regulate the proportion of evaporated refrigerant fiow as between said parallel branches
  • valve means being responsive to temperature changes in a cooling space surrounding the evaporator
  • the compressor, condenser and evaporator being connected in circuitous flow relationship.
  • variable capacity refrigeration system in which one portion of the compressed refrigerant conduit is disposed in heat exchange relationship with one of the parallel branches of the evaporated refrigerant conduit, said portion of the compressed refrigerant conduit being the compressed refrigerant vapor portion.
  • a variable capacity refrigeration system in which one portion of the compressed refrigerant conduit is disposed in heat exchange relationship with one of the parallel branches of the evaporated refrigerant conduit, said portion of the compressed refrigerant conduit being the compressed refrigerant condensate portion.
  • variable capacity refrigeration system comprising in combination:
  • a compressed refrigerant conduit including a condenser, a compressed refrigerant vapor portion and a compressed refrigerant condensate portion, connecting the compressor with the evaporator,
  • valve means disposed and arranged to regulate the proportion of evaporated refrigerant flow as between said parallel branches
  • valve means being responsive to temperature changes in a cooling space surrounding the evaporator, a higher temperature therein signaling a heavier load and causing a greater proportional flow of refrigerant through the branch of the evaporated refrigerant conduit disposed in heat exchange relationship with the compressed refrigerant condensate portion of the compressed refrigerant conduit, 9. lower temperature therein signaling a lighter load and causing a greater proportional fiow of refrigerant through the other branch of the evaporated refrigen ant conduit,
  • the compressor, condenser and evaporator being connected in circuitous flow relationship.
  • a variable capacity refrigeration system according to claim 4 in which solenoid valves are employed to direct refrigerant flow as between the parallel branches of the evaporated refrigerant conduit.
  • a variable capacity refrigeration system in which a proportioning valve is employed to direct the refrigerant flow as between the parallel branches 9 of the evaporated refrigerant conduit, thus providing a modulating type control.
  • variable capacity refrigeration system comprising in combination:
  • a compressed refrigerant conduit including a condenser, a compressed refrigerant vapor portion and a compressed refrigerant condensate portion, connecting the compressor with the evaporator,
  • valve means disposed and arranged to regulate the proportion of evaporated refrigerant flow as between said parallel branches
  • valve means being responsive to temperature changes in a cooling space surrounding the evaporator and (i) means to circulate a refrigerant in closed circuitous flow relationship from compressor to condenser to evaporator to compressor.
  • variable capacity refrigeration system of claim 7 wherein the circulating refrigerant is a member selected form the group consisting of monochloropentafiuoroethane, octafluorocyclobutane, perfluoropropane, chloroperfiuoropropane and sulfur hexafiuoride.
  • variable capacity refrigeration system of claim 7 wherein the refrigerant is a halogenated hydrocarbon containing at least one halogen atom selected from the group consisting of chlorine and fluorine.
  • variable capacity refrigeration system of claim 9 wherein the refrigerant is monochloropentafluoroethane.
  • a variable capacity refrigeration system comprising in combination:
  • a compressed refrigerant conduit including a condenser, a compressed refrigerant vapor portion and a compressed refrigerant condensate portion, connecting the compressor with the vaporator,
  • proporti-oning valve means disposed and arranged to regulate the proportionate flow of refrigerant as between the parallel branches
  • the proportioning valve mean being responsive to temperature changes in a cooling space surrounding the evaporator, a higher temperature therein signaling a heavier load and causing a greater proportional flow of refrigerant through the branch of the evaporated refrigerant conduit disposed in heat exchange relationship with the compressed refrigerant condensate portion of the compressed refrigerant conduit, a lower temperature therein signaling a lighter load and causing a greater proportional flow of refrigerant through the other branch of the evaporated refrigerant,
  • (i) means to circulate monochloro-pentafiuoroethane in closed circuitous flow relationship from compressor to condenser to evaporator to compressor.
  • a variable capacity refrigeration system according to claim 11 in which solenoid valves are substituted for the proportioning valve which serves to distribute the refrigerant flow as between the parallel branches of the evaporated refrigerant conduit.
  • a variable capacity refrigeration system according to claim 11 in which heat is supplied to the other of the parallel branches of the evaporated refrigerant conduit.
  • variable capacity in a refrigerant system which comprises:
  • a refrigerant possessing a wide capacity variation responsive to change in demand on cooling requirements in closed circuitous flow through a refrigeration system comprising a compressor, an evaporator, a compressed refrigerant conduit including a condenser, a compressed refrigerant vapor portion and a compressed refrigerant condensate portion, connecting the compressor with the evaporator, and an evaporated refrigerant conduit connecting the evaporator with the compressor in split parallel flow relationship
  • variable capacity in a refrigerant system which comprises:

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US4428853A (en) 1981-10-19 1984-01-31 Institut Francais Du Petrole Process for the heating and/or thermal conditioning of a building by means of a heat pump operated with a specific mixture of working fluids
US20160245567A1 (en) * 2015-02-25 2016-08-25 Heatcraft Refrigeration Products Llc Integrated Suction Header Assembly
US11112155B1 (en) 2018-11-01 2021-09-07 Booz Allen Hamilton Inc. Thermal management systems
US11293673B1 (en) 2018-11-01 2022-04-05 Booz Allen Hamilton Inc. Thermal management systems
US11313594B1 (en) 2018-11-01 2022-04-26 Booz Allen Hamilton Inc. Thermal management systems for extended operation
US11561030B1 (en) 2020-06-15 2023-01-24 Booz Allen Hamilton Inc. Thermal management systems
US11644221B1 (en) 2019-03-05 2023-05-09 Booz Allen Hamilton Inc. Open cycle thermal management system with a vapor pump device
US11752837B1 (en) 2019-11-15 2023-09-12 Booz Allen Hamilton Inc. Processing vapor exhausted by thermal management systems
US11796230B1 (en) 2019-06-18 2023-10-24 Booz Allen Hamilton Inc. Thermal management systems
US11835270B1 (en) * 2018-06-22 2023-12-05 Booz Allen Hamilton Inc. Thermal management systems

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US2691273A (en) * 1951-11-26 1954-10-12 Philco Corp Feed control means for refrigeration apparatus

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US2022774A (en) * 1934-12-29 1935-12-03 Gen Motors Corp Refrigerating apparatus
US2223900A (en) * 1939-05-22 1940-12-03 York Ice Machinery Corp Refrigeration
US2691273A (en) * 1951-11-26 1954-10-12 Philco Corp Feed control means for refrigeration apparatus

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4428853A (en) 1981-10-19 1984-01-31 Institut Francais Du Petrole Process for the heating and/or thermal conditioning of a building by means of a heat pump operated with a specific mixture of working fluids
US4468337A (en) * 1981-10-19 1984-08-28 Institut Francais Du Petrole Process for the heating and/or thermal conditioning of a building by means of a heat pump operated with a specific mixture of working fluids
US20160245567A1 (en) * 2015-02-25 2016-08-25 Heatcraft Refrigeration Products Llc Integrated Suction Header Assembly
US11092369B2 (en) 2015-02-25 2021-08-17 Heatcraft Refrigeration Products Llc Integrated suction header assembly
US11835270B1 (en) * 2018-06-22 2023-12-05 Booz Allen Hamilton Inc. Thermal management systems
US11448431B1 (en) 2018-11-01 2022-09-20 Booz Allen Hamilton Inc. Thermal management systems for extended operation
US11486607B1 (en) 2018-11-01 2022-11-01 Booz Allen Hamilton Inc. Thermal management systems for extended operation
US11313594B1 (en) 2018-11-01 2022-04-26 Booz Allen Hamilton Inc. Thermal management systems for extended operation
US11333402B1 (en) 2018-11-01 2022-05-17 Booz Allen Hamilton Inc. Thermal management systems
US11384960B1 (en) 2018-11-01 2022-07-12 Booz Allen Hamilton Inc. Thermal management systems
US11408649B1 (en) 2018-11-01 2022-08-09 Booz Allen Hamilton Inc. Thermal management systems
US11421917B1 (en) 2018-11-01 2022-08-23 Booz Allen Hamilton Inc. Thermal management systems
US11168925B1 (en) 2018-11-01 2021-11-09 Booz Allen Hamilton Inc. Thermal management systems
US11448434B1 (en) 2018-11-01 2022-09-20 Booz Allen Hamilton Inc. Thermal management systems
US11293673B1 (en) 2018-11-01 2022-04-05 Booz Allen Hamilton Inc. Thermal management systems
US11536494B1 (en) 2018-11-01 2022-12-27 Booz Allen Hamilton Inc. Thermal management systems for extended operation
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US11561036B1 (en) 2018-11-01 2023-01-24 Booz Allen Hamilton Inc. Thermal management systems
US11561029B1 (en) 2018-11-01 2023-01-24 Booz Allen Hamilton Inc. Thermal management systems
US11644221B1 (en) 2019-03-05 2023-05-09 Booz Allen Hamilton Inc. Open cycle thermal management system with a vapor pump device
US11801731B1 (en) 2019-03-05 2023-10-31 Booz Allen Hamilton Inc. Thermal management systems
US11796230B1 (en) 2019-06-18 2023-10-24 Booz Allen Hamilton Inc. Thermal management systems
US11752837B1 (en) 2019-11-15 2023-09-12 Booz Allen Hamilton Inc. Processing vapor exhausted by thermal management systems
US11561030B1 (en) 2020-06-15 2023-01-24 Booz Allen Hamilton Inc. Thermal management systems

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GB1105190A (en) 1968-03-06
DE1476691A1 (de) 1969-10-23

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