CN105865093A - Thermosiphon configuration for cascade refrigeration systems - Google Patents

Thermosiphon configuration for cascade refrigeration systems Download PDF

Info

Publication number
CN105865093A
CN105865093A CN201610082655.7A CN201610082655A CN105865093A CN 105865093 A CN105865093 A CN 105865093A CN 201610082655 A CN201610082655 A CN 201610082655A CN 105865093 A CN105865093 A CN 105865093A
Authority
CN
China
Prior art keywords
thermosiphon
entrance
angle
cascade
inclination
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN201610082655.7A
Other languages
Chinese (zh)
Inventor
奥古斯托·J·偑雷拉·齐默尔曼
达勒·N·赛兹莫尔
小罗伯特·H·奥斯汀
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Heatcraft Refrigeration Products LLC
Original Assignee
Heatcraft Refrigeration Products LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Heatcraft Refrigeration Products LLC filed Critical Heatcraft Refrigeration Products LLC
Publication of CN105865093A publication Critical patent/CN105865093A/en
Pending legal-status Critical Current

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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • 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
    • F25B2400/23—Separators

Abstract

The present application provides a thermosiphon for use with a refrigeration system. The thermosiphon includes a primary flow inlet, an angled secondary flow inlet, and a mixed flow outlet. The angled secondary flow inlet includes an angle of about forty-five degrees or less with respect to the mixed flow outlet.

Description

Configuration for the thermosiphon of cascade refrigeration system
Related application
The application is the U.S. of the Serial No. 62/114,603 of requirement submission on February 11st, 2015 The non-provisional application of Provisional Application priority.The U.S. Provisional Application of serial number 62/114,603 passes through Quote in full and be incorporated in herein.
Technical field
The application and consequent patent are usually directed to refrigeration system, particularly relate to a kind of cascade system Cooling system, it uses the thermosyphon connected with cascade vaporizer-condenser low side cooling recirculation assembly System.
Background technology
Cascade refrigeration system generally includes the first end cooling circulation, and the most high-end cooling circulates, Yi Ji Two end cooling circulation, i.e. low side cooling circulations.Two coolings cycle through common heat exchanger, I.e. cascade vaporizer-condenser to engage.Cascade refrigeration system can be in an efficient manner in low-down temperature Cooling is provided.
Current refrigeration trend promotes to use ammonia, carbon dioxide, and other kinds of natural refrigerant Replace the cold-producing medium based on fluorohydrocarbon of routine.Cascade refrigeration system can use ammonia also in height circulates Carbon dioxide is used in low circulation.Additionally, people be interested at least with conventional based on fluorohydrocarbon System compare the whole efficiency improving this refrigeration system based on natural refrigerant.
Thus, it is desirable to have the refrigeration system of such improvement, such as cascade refrigeration system, it uses Natural or other kinds of cold-producing medium provides the efficiency increased for cooling.The refrigeration system of this improvement It is suitable for the high pressure needed for low temperature cascade being cooled down with effective, reliable and secured fashion.
Summary of the invention
The application and consequent patent thus the thermosiphon for refrigeration system is provided. This thermosiphon can include first-class entrance, the second entrance of inclination, and mixed flow outlet. The second entrance tilted can include the angle exporting into about 45 degree or less relative to mixed flow θ1.Compared with vertical orientated, the stream of inclination can improve mass flow or reduces the first entrance stream and mix Close the pressure of outlet stream.
The application and consequent patent also provide for cascade vaporizer-condenser is improved cold-producing medium Mass flow or the method reducing refrigerant pressure loss.The method can comprise the steps: as temperature Difference ring streaming system provides the outlet being connected with cascade vaporizer-condenser, provides first from the first source Cold-producing medium stream, provides second refrigerant stream from the second source, with the angles of less than about 90 degree mixing the One cold-producing medium stream and second refrigerant stream, and by thermosiphon outlet to cascade vaporizer- Condenser provides the cold-producing medium stream of mixing.
The application and consequent patent also provide for the thermosiphon for refrigeration system.Should Thermosiphon can include the tank entrance being connected with liquid-gas separator tank, with one or more pressures The suction port of compressor of the inclination that contracting machine is connected, and the level being connected with cascade vaporizer-condenser Connection outlet.The suction port of compressor tilted can include relative to cascade exit Cheng Yuesi 15 degree or less Angle, θ 1.
After once combining accompanying drawing and appended claims reading following detailed description of book, the application And these and other features of consequent patent and improve those skilled in the art will be show and It is clear to.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the known cascade refrigeration system with high-end circulation and low side circulation.
Fig. 2 is the schematic diagram of the thermosiphon configuration used in known cascade refrigeration system.
Fig. 3 is the alternative embodiment of known thermosiphon configuration.
Fig. 4 is the temperature difference ring of the pressure loss of the mass flow with improvement described herein or reduction Streaming system configures.
Fig. 5 is the alternative embodiment of thermosiphon described herein configuration.
Fig. 6 is the alternative embodiment of thermosiphon described herein configuration.
Detailed description of the invention
Referring now to accompanying drawing, numeral identical in these figures refers to identical element, and Fig. 1 shows Go out an example of cascade refrigeration system 100.Cascade refrigeration system 100 can be used for cooling down super Any kind of room used in city, cold storage etc..Cascade refrigeration system 100 also apply be applicable to it His heating of type, ventilation and air regulation application and/or different types of business and/or work Industry is applied.Entire cascaded refrigeration system 100 can have size or the power of any appropriate.Other classes The refrigeration system of type, circulation and assembly also can use at this.
Normally describing, cascade refrigeration system 100 can include the first or high-end circulation 110 and second Or low side circulation 120.High-end circulation 110 can include one or more high end compression machine 130, high-end Oil eliminator 140, high-end condenser 150, high end reception device 160, and high-end expansion gear 170. High-end circulation 110 may also include suction/liquid heat exchanger 180 and sucking collector 190.High-end Circulation 110 can include the stream of cold-producing medium 200.Cold-producing medium 200 can include ammonia or other types refrigeration The stream of agent.High-end circulation 110 assembly can have any suitably sized, shape, configuration or power. High-end circulation 110 can use other and extra assembly and configuration at this.
Low side circulation 120 can include that one or more low side compressor 210, low side are separating of oil similarly Device 220, low side liquid-gas separator tank 230, one or more low side expansion gear 240 and one Or multiple low side vaporizer 250.Low side circulation 120 can include having pump 270 and multiple flow valve Centre (medium) temperature loop 260 of 280 and low-temperature circuit 290.Catcher 300 also may be used Use at this.Low side circulation 120 can include the stream of cold-producing medium 310.Cold-producing medium 310 can include two Carbonoxide or the stream of other types cold-producing medium.Low side circulates 120 assemblies can have any suitable chi Very little, shape, configuration or power.That low side circulation 120 can use other at this or extra assembly And configuration.
Two circulations 110,120 can be engaged by cascade evaporator/condenser 320.Cold-producing medium 200, The respective stream of 310 can be by cascade evaporator/condenser 320 heat-shift.Cascade vaporizer/ Condenser 320 can have any applicable size, shape, configuration or power.Other assemblies or its He can use at this in configuration.
Cold-producing medium 200 can be compressed by high end compression machine 130 and condense in high-end condenser 150. In cold-producing medium 200 is storable in high end reception device 160 and can be drawn out of on demand and steam with satisfied cascade Send out the load of device/condenser 320.Cold-producing medium 200 then can pass through suction/liquid heat exchanger 180, High-end expansion gear 170 and cascade evaporator/condenser 320.Cold-producing medium 200 again by suck/ Liquid heat exchanger 180 also returns high end compression machine 130.Suction/liquid heat exchanger 180 can quilt It was used for before cold-producing medium 200 enters cascade evaporator/condenser 320 it is carried out sub-cooled. Other assemblies and other configurations can use at this.
Low side circulation 120 can be similar.Cold-producing medium 310 based on carbon dioxide can be by low side Compressor 210 compresses, then by cascade evaporator/condenser 320.Cold-producing medium 310 can be stored up In there is low side liquid-gas separator tank 230 and extract out on demand.Cold-producing medium 310 can by one or Multiple low side expansion gears 240 and one or more low side vaporizer 250.Low side circulation 120 can divide For low-temperature circuit 290 and medium temperature loop 260.Other assemblies and other configurations can use at this.
Low side circulation 120 is used as thermosiphon 330.Based on thermal gradient rather than such as pump and The machinery of analog, thermosiphon 330 ensure that fluid (is cold-producing medium in the present case 310) circulation.In this example embodiment, thermosiphon 330 can have and low side liquid-gas separator The tank entrance 340 that tank 230 is connected, the suction port of compressor 350 being connected with low side compressor 210, And with the cascade cascade exit 360 that is connected of vaporizer-condenser 320.
In using, the liquid/gas flow of carbon dioxide coolant 310 can be transferred to low side liquid-gas separator Tank 230, carry out in liquid-gas separator tank 230 liquid edema caused by disorder of QI from.Gas part can be through thermosyphon System 330 be sent to cascade vaporizer-condenser 320, and with leave the gas of low side compressor 210 Body mixes so that steam is condensed into liquid.Other assemblies and other configurations can use at this.
Fig. 1 and Fig. 2 illustrates the example of the conventional configuration of thermosiphon 330.Suction port of compressor 350 are in a line with cascade exit 360.Tank entrance 340 can about 90 degree of (90 °) angles to hang down Straight relation is incorporated to provide the shape 370 being essentially tank similar " T " for thermosiphon 330. Fig. 3 illustrates similar configuration, and wherein tank entrance 340 and cascade exit 360 are in a line, and right In compressor, suction port of compressor 350 is vertically incorporated to the shape 380 of similar " T ".No matter two Kind orientation in any, several stream with about vertical angle merge.
The stream from low side liquid-gas separator tank 230 through tank entrance 340 can be considered first-class 390.The stream going to suction port of compressor 350 from compressor 210 can be considered second 400.False As used arranged perpendicular, caused the interruption of various stream by the thermosiphon 330 that pressure drop is sensitive May just become operation problem above and in efficiency.In conventional cascade system, through tank entrance 340 First-class 390 can be at about 435.07psia (about 3000kpa), temperature about 22 degrees Fahrenheit is (about -5.5 degrees Celsius) and there is the mass flow of about 0.17 or 0.18kg/s.Through compressor 360 Second 400 can be at about 145 degrees Fahrenheits (about 63 degrees Celsius) and there is about 0.09kg/s Mass flow.After merging, the outlet stream 410 of the mixing at cascade exit 360 can be at about 434.87psia (about 2998kpa), about 45 degrees Fahrenheits (about 7.2 degrees Celsius) also have about 0.26 Or the mass flow of 0.27kg/s.Other pressure, temperature, mass flow and other parameters can be This uses.
Fig. 4 illustrates an example of thermosiphon 420 described herein.Thermosiphon 420 can have and cascade exit 440 tank entrance 430 in a row.Substitute above-described compressor Entrance 350 is with the vertical orientated tank entrance 340 that is incorporated to, and thermosiphon 420 can include the pressure tilted Contracting machine entrance 450.The suction port of compressor 450 tilted can tank entrance 430 or cascade exit 440 relatively Centrage arrange with angle, θ 1.Angle, θ 1 preferably can be from being approximately more than about zero degree (0 °) to about four 15 degree (45 °) left and right.Other angles can use at this.Other assemblies and other configurations can be at these Use.
Fig. 5 illustrates the further example of thermosiphon 460 described herein.At this example In, thermosiphon 460 can include the tank entrance 470 tilted and/or the suction port of compressor tilted 480.Then entrance 470,480 can be merged into cascade exit 490 to form substantial similar " Y " Shape.The tank entrance 470 tilted can the centrage of cascade exit 490 relatively be arranged with angle, θ 2. Angle, θ 2 the most greater than about zero degree (0 °) is to about 45 degree (45 °) left and right.Other angles Degree can use at this.The suction port of compressor 480 tilted is used as and above-described similar angle Degree θ 1.Specifically, angle, θ 1 and θ 2 can be identical or different.Other assemblies and other configurations Also can use at this.
Following table is shown for the thermosiphon 330 of Fig. 2 and 3 and the temperature difference ring of Figure 4 and 5 The change of the mass flow of streaming system 420,460.This comparison supposes in tank pressure at inlet and temperature Spending identical, at suction port of compressor, mass flow is identical with temperature, pressure and temperature at cascade exit Spend identical.Mass flow that is that enter tank entrance and that leave cascade exit will change.For Fig. 4 Thermosiphon 420 in the suction port of compressor 450 of inclination, angle, θ 1 is from six degree (6 °) It is changed to about 90 degree (90 °).Equally, for the tank entrance of inclination of thermosiphon 460 470 and tilt suction port of compressor 480, angle, θ 1 is changed to about 30 degree from about ten degree (10 °) (30 °), and θ 2 is changed to about 30 degree (30 °) from about three degree (3 °).Each in mass flow Kind change thus be illustrated according to kilogram per second.
Tank inlet flow rate and cascade exit flow thus arranged perpendicular relative to Fig. 2 and Fig. 3 occur Change and improvement.Use about six degree (6 °) to the angle of about eleventh (11 °) to improve to cascade out Mass flow at Kou is from about 0.26kg/s to about 0.33kg/s or adds 41 about percent (41%).Compared to the setting of vertical angle, change the angle of second 400 first-class 390 Degree thus provide the first flow of increase and/or identical entrance velocity provided along first-class Reduce pressure to decline.
Fig. 6 illustrates the further embodiment of thermosiphon 500 described herein.At this example In, thermosiphon 500 can include the cascade exit 520 of tank entrance 510 and word order.? In this example, thermosiphon 500 can include the suction port of compressor 530 tilted.The compression tilted The angle, θ 1 of machine entrance 530 thus alterable.The suction port of compressor 530 tilted can have variable Diameter 540.Equally, the diameter of variable-diameter 540 is variable.Change angle and diameter also can by with In tank entrance 510.Tank entrance 510 can have about 1-3/8 inch (about 34.9 millimeters) left and right Diameter.Other assemblies and other configurations can use at this.
Under to represent the above-described tank entrance 510 of hypothesis constant and change angle, θ 1 and diameter from about The example that 0.4 inch (about 10.2 millimeters) change to about one (1) inch (about 25.4 millimeters).
Would have about the variable-diameter 540 of angle, θ 1 about 10.2 millimeters of 30 degree for inclination Suction port of compressor 530 therefore baseline relative to Fig. 2 brings the improvement more than 100%.Specifically, come More cold-producing medium can be extracted out from liquid-gas separator tank 230 from the higher second of compressor 210 310 and there is not the situation of obstructed flow in the case of the jet of small diameter.Equally, inclination Diameter proportion between suction port of compressor 530 and tank entrance changes from about 0.7 to about 0.3, the most extremely The ratio of few 0.5.
Depend on operating parameter, it is possible to variable-diameter 540 is dynamically set.Such as, variable-diameter 540 Can be changed according to the load of total system and analogue.Herein it is contemplated that other parameters.Though Thermosiphon the most herein efforts be made so that uses carbon dioxide coolant 310, but described herein Thermosiphon can be used for merging any kind of first-class and second.
Should be appreciated that some embodiment only relating to the application and consequent patent above.? Usual spirit and scope without departing from the present invention by claim below and equivalents thereof In the case of, those skilled in the art can many modifications may be made and improves to the application.

Claims (15)

1. for a thermosiphon for refrigeration system, including:
First-class entrance；
The second entrance tilted；With
Mixed flow exports；
Wherein, the second entrance of described inclination includes exporting into about 45 relative to described mixed flow The angle, θ 1 of degree or less.
2. thermosiphon as claimed in claim 1, wherein said first-class entrance includes and liquid gas The tank entrance that separator pot is connected.
3. thermosiphon as claimed in claim 1, wherein said second entrance includes and one Or the suction port of compressor that multiple compressor is connected.
4. thermosiphon as claimed in claim 1, the outlet of wherein said mixed flow includes and cascade The cascade exit that vaporizer-condenser is connected.
5. thermosiphon as claimed in claim 1, wherein said first-class entrance includes inclination First-class entrance.
6. thermosiphon as claimed in claim 5, the first-class entrance of wherein said inclination includes The angle, θ 2 of about 45 degree or less is exported into relative to described mixed flow.
7. thermosiphon as claimed in claim 5, the first-class entrance of wherein said inclination, inclines Oblique second entrance and mixed flow outlet include the shape substantially like Y.
8. thermosiphon as claimed in claim 6, wherein angle, θ 1 is equal to angle, θ 2.
9. thermosiphon as claimed in claim 6, wherein angle, θ 1 is different from angle, θ 2.
10. thermosiphon as claimed in claim 1, wherein angle, θ 1 is relative to described mixed flow Outlet is 30 degree or less.
11. thermosiphons as claimed in claim 1, wherein angle, θ 1 is relative to described mixed flow Outlet is eleventh or less.
12. thermosiphons as claimed in claim 1, the second entrance of wherein said inclination includes The second entrance that variable-diameter tilts.
13. thermosiphons as claimed in claim 12, the second of wherein said variable-diameter inclination Inflow entrance includes the diameter of 10.2 millimeters or less.
14. thermosiphons as claimed in claim 12, the second of wherein said variable-diameter inclination Inflow entrance and first-class entrance include the diameter proportion of about 0.5 or less.
15. 1 kinds are improved refrigerant mass fluxes to cascading vaporizer-condenser or reduce refrigerant pressure damage The method lost, including:
The outlet being connected with described cascade vaporizer-condenser is provided for thermosiphon；
First cold-producing medium stream is provided from the first source；
Second refrigerant stream is provided from the second source；
Described first cold-producing medium stream and second refrigerant stream is mixed with the angles of less than about 90 degree；And By the outlet of described thermosiphon, the cold-producing medium stream of mixing is supplied to described cascade steam Send out device-condenser.
CN201610082655.7A 2015-02-11 2016-02-05 Thermosiphon configuration for cascade refrigeration systems Pending CN105865093A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562114603P 2015-02-11 2015-02-11
US62/114,603 2015-02-11

Publications (1)

Publication Number Publication Date
CN105865093A true CN105865093A (en) 2016-08-17

Family

ID=55527737

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201610082655.7A Pending CN105865093A (en) 2015-02-11 2016-02-05 Thermosiphon configuration for cascade refrigeration systems

Country Status (4)

Country Link
US (1) US20160231063A1 (en)
EP (1) EP3056838A1 (en)
CN (1) CN105865093A (en)
CA (1) CA2919464A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11118817B2 (en) * 2018-04-03 2021-09-14 Heatcraft Refrigeration Products Llc Cooling system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2359595A (en) * 1943-07-27 1944-10-03 Gen Electric Refrigerating system
US3093976A (en) * 1962-04-20 1963-06-18 Carl O Walcutt Refrigeration system including receiver
US4253309A (en) * 1978-12-28 1981-03-03 Thore Abrahamsson Heat pump arrangement
US4367634A (en) * 1979-04-12 1983-01-11 Bolton Bruce E Modulating heat pump system
US4599870A (en) * 1981-03-25 1986-07-15 Hebert Theodore M Thermosyphon heat recovery

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4134273A (en) * 1977-04-22 1979-01-16 Brautigam Robert F Home heating and cooling system
NO160469C (en) * 1985-05-31 1994-09-23 Norske Stats Oljeselskap Y-shaped connector for connecting liquid and / or gas-conducting pipelines.
AU2001270225A1 (en) * 2000-06-28 2002-01-08 Igc Polycold Systems, Inc. High efficiency very-low temperature mixed refrigerant system with rapid cool down
DE10121544B4 (en) * 2001-05-03 2007-08-16 Axima Refrigeration Gmbh Process for the liquefaction of a reactive gas
CN101084409B (en) * 2004-10-07 2011-03-23 布鲁克斯自动化有限公司 Efficient heat exchanger for refrigeration process
KR100609169B1 (en) * 2004-11-02 2006-08-02 엘지전자 주식회사 Cascade refrigerating cycle
CA2658316A1 (en) * 2006-07-25 2008-01-31 Shell Internationale Research Maatschappij B.V. Method and apparatus for vaporizing a liquid stream
US8282017B2 (en) * 2007-11-02 2012-10-09 Tube Fabrication Design, Inc. Multiple cell heat transfer system
US9989280B2 (en) * 2008-05-02 2018-06-05 Heatcraft Refrigeration Products Llc Cascade cooling system with intercycle cooling or additional vapor condensation cycle
KR101061225B1 (en) * 2009-11-12 2011-08-31 포항공과대학교 산학협력단 Method for manufacturing fluid transport network and fluid transport network using same
EP2596301B1 (en) * 2010-07-23 2020-10-14 Carrier Corporation Ejector cycle refrigerant separator
GB201211208D0 (en) * 2012-06-25 2012-08-08 Stenhouse James T Materials and methods to improve energy efficiency and enable ultra fast recovery after defrost cycle in cascade refrigeration systems

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2359595A (en) * 1943-07-27 1944-10-03 Gen Electric Refrigerating system
US3093976A (en) * 1962-04-20 1963-06-18 Carl O Walcutt Refrigeration system including receiver
US4253309A (en) * 1978-12-28 1981-03-03 Thore Abrahamsson Heat pump arrangement
US4367634A (en) * 1979-04-12 1983-01-11 Bolton Bruce E Modulating heat pump system
US4599870A (en) * 1981-03-25 1986-07-15 Hebert Theodore M Thermosyphon heat recovery

Also Published As

Publication number Publication date
EP3056838A1 (en) 2016-08-17
US20160231063A1 (en) 2016-08-11
CA2919464A1 (en) 2016-08-11

Similar Documents

Publication Publication Date Title
DE102006035784B4 (en) Refrigeration system for transcritical operation with economiser and low pressure collector
US10408508B2 (en) Oil recovery for refrigeration system
US20160138847A1 (en) Transcritical carbon dioxide refrigeration system with multiple ejectors
CN105627608B (en) A kind of Auto-cascade cycle steam compressed refrigerating circulating system of gas gas blowout emitter synergy
CN105004100B (en) Vapor compression refrigeration/heat pump system of single refrigerant circuit, more pressures of inspiration(Pi)
JP6606194B2 (en) air compressor
CN105737427A (en) One-grade self-overlaying low-temperature refrigeration circulating system using double-stage gas-liquid separator
CN106196681A (en) Middle fractional condensation type self-cascade refrigeration system system and refrigeration plant
CN205641301U (en) Heat pump type air conditioning system
CN106225319A (en) A kind of double evaporating temperatures refrigeration and heat pump air conditioner unit and the method for back-heating type non-azeotropic mixed working medium
CN205807894U (en) A kind of Auto-cascade cycle three temperature varying capacity output refrigeration system
CN104848574A (en) Synergistic fractional condensing type steam compression refrigeration cycle system
CN104864622A (en) Auto-cascade steam compression type refrigeration cycle system
CN105865093A (en) Thermosiphon configuration for cascade refrigeration systems
CN103574957A (en) Multiplex modular system
KR101839781B1 (en) Heat recovery apparatus
JPS6038561A (en) Heater for composite heat pump
KR20080012638A (en) Refrigeration system
CN206847137U (en) A kind of multicomponent mixture work medium single-stage separating, throttling circulates cryogenic refrigeration system
CN108317761A (en) A kind of auto-cascading refrigeration system and control method of the compression of list two-stage coupling
US10267542B2 (en) Wide speed range high-efficiency cold climate heat pump
US11326789B2 (en) Air conditioning system and control method thereof
CN205373118U (en) Cooling cycle system and refrigeration plant
CN103574958A (en) Multiplex modular system
CN109425140B (en) Refrigeration circuit and refrigeration plant based on non-azeotropic mixed working medium

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20160817

WD01 Invention patent application deemed withdrawn after publication