EP1816415A2 - Kälteanlage mit Umlauf von flüssigem Kältemittel durch Druck - Google Patents

Kälteanlage mit Umlauf von flüssigem Kältemittel durch Druck Download PDF

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Publication number
EP1816415A2
EP1816415A2 EP07002617A EP07002617A EP1816415A2 EP 1816415 A2 EP1816415 A2 EP 1816415A2 EP 07002617 A EP07002617 A EP 07002617A EP 07002617 A EP07002617 A EP 07002617A EP 1816415 A2 EP1816415 A2 EP 1816415A2
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EP
European Patent Office
Prior art keywords
refrigerant
refrigerating system
heat exchanger
pumping
primary
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.)
Withdrawn
Application number
EP07002617A
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English (en)
French (fr)
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EP1816415A3 (de
Inventor
Bent Johansen
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.)
Carrier Corp
Original Assignee
Birton AS
Carrier Corp
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 Birton AS, Carrier Corp filed Critical Birton AS
Publication of EP1816415A2 publication Critical patent/EP1816415A2/de
Publication of EP1816415A3 publication Critical patent/EP1816415A3/de
Withdrawn legal-status Critical Current

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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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems

Definitions

  • the invention relates to a cascade refrigerating system comprising a primary refrigerating system operating with a first refrigerant, which primary refrigerating system comprises compressor means connected to condensing means, where the primary refrigerating system further comprises heat exchanging means, where heat is exchanged from a secondary refrigerating system, which secondary refrigerating system comprises pumping means arranged to supply refrigerant to evaporating means and where the secondary refrigerating system comprises at least two pumping vessels connected through respective check valves, which pumping vessels are connected to at least one heat exchanger, in which refrigerant is evaporated to generate a high pressure, which high pressure is led to the top of one of the pumping vessels to supply refrigerant to the evaporation means.
  • GB 1,146,428 describes improvements in a flooded coil refrigerating system, where tanks are designed to collect a re-circulating excess refrigerant from the evaporators to eliminate slugging of the compressor.
  • the driving force of the prior art system is the pressure difference between the compressor discharge or condenser pressure and the suction pressure of the compressor, which is similar to most other refrigerating systems.
  • one of the receivers is connected to the condenser, and liquid refrigerant fills the first receiver, which at the same time is connected through restriction means to flooded evaporators, from which refrigerant is led to the second receiver, where liquid remains and gas is led to the suction side of the compressor.
  • valves are opened and closed to change the operation of the receivers.
  • DE 3511421 A1 describes a refrigeration circuit, which comprises adjustable means to increase the pressure in the refrigeration circuit with a low condensation temperature. This way it is possible to fulfil condensation by using very low refrigerant temperatures with a very low condensation pressure without experiencing circulation problems.
  • the system relates to energy savings by means of low condensing temperatures, which maintains sufficient refrigerant pressure for the expansion valve.
  • EP 1 046 868 A2 describes a refrigerating system having a refrigeration cycle, which provides optimised energy consumption.
  • Prior art discloses the use of the gravity force for generating flow of the refrigerant. Gravity force systems can be difficult to install on site due to physical restrictions regarding the installation of components and the piping in buildings.
  • EP 1536190 A1 concerns a cascade refrigerating system comprising a first high temperature refrigerating system operating with a first refrigerant, where the first high temperature system comprises heat exchanging means, where heat is exchanged from a second low temperature refrigerating system.
  • the second low temperature refrigerating system comprises pumping means arranged to supply refrigerant to evaporating means.
  • the second low temperature refrigerating system may comprise at least two pumping vessels connected through respective check valves, which pumping vessels are connected to heating means in which refrigerant is evaporated to generate high pressure, which high pressure is led to the top of the pumping vessels to press refrigerant towards the evaporation means.
  • liquid refrigerant evaporates and generates pressure in the related vessel as it is exposed to the heating means. This way the circulation system is able to operate with refrigerant completely without oil, since the system does not include any compressors or pumps. This leads to improved performance and improved heat transfer.
  • JP 2002048422 describes a natural circulation type heat pumping system comprising a cascade condenser, an ammonia refrigerant system, a carbon dioxide refrigerant system, hence a carbon dioxide gas generated by the carbon dioxide refrigerating system is guided to the capacitors 3 and heat exchanged with an ammonia liquid of the ammonia refrigerant system.
  • the system furthermore comprises pressure tanks for containing liquefied carbon dioxide from the condensers 3 to heat the liquefied carbon dioxide via heat exchangers and to increase the pressure inside the tanks; the liquefied carbon dioxide is lifted to a serge tank installed above the evaporator of the carbon dioxide refrigerating system.
  • a high level serge tank 6 is necessary to secure continued flow to evaporator means.
  • JP 11 132507 describes a refrigerating system with improved reliability of refrigerant circulation by means of a reduction of the number of trouble occurring factor spots by means of a method according to which there is a need for a valve mechanism to switch pressurization through evaporation of a refrigerant.
  • the pressure reduction is eliminated from a device formed to generate a circulation drive force for refrigerant in a circuit by utilizing a pressure generated through heating and cooling of a refrigerant.
  • a drive force generating circuit having a liquid receiver is connected to a liquid line of a refrigerant circuit B on the utilization side of a secondary refrigerant system.
  • a refrigerating device comprises a heater to generate high pressure through evaporation of a refrigerant by heating the pressurized heat-exchanger and a cooler to generate low pressure through condensation of a refrigerant by cooling a pressure-reduced heat-exchanger.
  • Regulating the heating amount of the heater and the cooling amount of the cooler alternately generates a state to generate high pressure in the liquid receiver, and a state wherein low pressure is exerted, hence discharge of liquid from the liquid receiver, and recovery of liquid to the liquid receiver is alternately affected.
  • EP 0857936 B1 concerns a heat exchanger on a secondary heat source exchanging heat with a heat exchanger on the primary heat source in a primary cooling circuit, and which is connected to an indoor heat exchanger through a gas pipe and a liquid pipe.
  • a tank storing a liquid cooling medium is connected at its lower end to the liquid pipe and at its upper end to a pressure adjustment mechanism.
  • Check valves are disposed on both sides of the connecting portion of the tank having regard to the liquid pipe.
  • the internal pressure of the tank is either high or low and the state of the pressure changes by means of the pressure adjustment mechanism, thus the liquid cooling medium is supplied to the indoor heat exchanger, when the pressure is high, and the liquid cooling medium is recovered from the heat exchanger on the secondary side of the tank and is circulated by a secondary cooling circuit during low pressure.
  • JP 11 023079 concerns a method according to which a natural refrigerant is used in a circulation cycle on the secondary side, a booster is arranged in a position below primary and secondary heat-exchanging parts, and a solenoid valve is arranged on the outlet side of a boosting device.
  • a secondary refrigerant being a natural refrigerant such as CO2, which is radiated and condensed by a refrigerator 1 on the primary side, is fed to a heat-exchanger 2 on the secondary side by the absorbing of heat, and a substance to be cooled is cooled.
  • a secondary refrigerant evaporated by the heat-exchanger on the secondary side is returned to the refrigerator on the primary side, and by means of its own weight it drops into a liquid reservoir situated downstream from the condensing part of the refrigerator on the primary side, and the refrigerant is stored therein.
  • a secondary refrigerant in the liquid reservoir is supplied by means of its own weight to a booster through a check valve. When a liquid refrigerant is sufficiently stored in a booster, solenoid valves are closed.
  • a secondary refrigerant is heated by a heating device to increase the internal pressure of the booster, and the secondary refrigerant is fed to a heat-exchanger on the secondary side through a piping on the secondary side.
  • the present application does not describe any pressure equalization in the tanks when alternating between tanks.
  • the purpose of the invention is to provide an energy efficient refrigerating system suitable for refrigerant circulation with reduced energy consumption for the circulation of refrigerant in refrigerating systems.
  • the energy for generating pressure in the secondary refrigerating system is removed from the first refrigerating system, making this application energy neutral.
  • the secondary liquid refrigerant When the secondary liquid refrigerant is exposed to heat in the heat exchanger, it evaporates and generates pressure in the related vessel. This way the circulation system can operate with refrigerant completely without oil since the system does not include any compressors or pumps. This leads to better performance and better heat transfer.
  • the heat exchanger has an inlet for the second refrigerant, which is connected to the lower part of the pumping vessels, where the heat exchanger has an outlet connected to the upper part of the pumping vessels. It is hereby achieved that liquid secondary refrigerant is supplied by gravity from at least one of two pumping vessels to a related heat exchanger located in the same level as the lower part of the pumping vessels.
  • the refrigerant is injected into one or more heat exchangers where the pressurized gas is produced by evaporating the second refrigerant. This way a pressure difference is provided, which pressure difference has enough force to press refrigerant through the refrigerating system.
  • the pressurized gas produced by the evaporating secondary refrigerant is supplied into the vessel acting as high pressure.
  • the high pressure of the contained liquid refrigerant makes the liquid refrigerant flow through non-return valves into the liquid line.
  • a control circuit makes the sequence alter so the second vessel supplies liquid and the first vessel fill up.
  • the upper part of the pumping vessels can be connected through a line, which line contains solenoid valves towards the vessels from where the line is further connected to the return line from the evaporators through a solenoid valve.
  • a line which line contains solenoid valves towards the vessels from where the line is further connected to the return line from the evaporators through a solenoid valve.
  • a common heat exchanger may comprise a first section, which first section is connected to the permanent open line, where a second and third section of the common heat exchanger is connected to the pumping vessels.
  • control can be performed by small and less expensive solenoids valves.
  • the material of the heat exchanger is always pre-heated by the primary refrigerant, ensuring a quick heating action.
  • first and a second heat exchanger is serially coupled and connected to the permanent open line.
  • standard heat exchangers may be used as long as a mostly unrestricted flow of the first refrigerant is achieved through the serially coupled heat exchangers.
  • the invention further relates to a method for operating a refrigerating system with free energy, which refrigerating system can be operated by at least two pumping means to supply refrigerant to evaporating means through expansion means, where the refrigerant flows from the evaporators through condensing means, from where the refrigerant flows back towards the pumping means, which pumping means can be pressurized by evaporating refrigerant in at least one heat exchanger for supplying refrigerant at high pressure towards the evaporation means, where the heat exchanger can be heated primarily by free energy flowing towards and away from the heat exchanger through permanent open lines.
  • Free energy can be achieved by connecting the heat exchanger to refrigerant flowing to or from a condensing means operating with sufficient high temperature.
  • the heating energy for generating pumping pressure of the secondary refrigerant is removed from the primary refrigerating system, which makes the circulation system work with "free energy" without any external energy source.
  • Free energy for generating pumping pressure of the secondary refrigerant can be achieved by connecting the heat exchanger to refrigerant flowing to or from a condensing means operating with sufficient high temperature.
  • the heating energy for generating pumping pressure of the secondary refrigerant is removed from the primary refrigerating system, which makes the circulation system work with "free energy” without any external energy source.
  • Free energy for generating pumping pressure of the secondary refrigerant can be achieved by superheating the suction gas from the evaporating means or from additional superheating means, which makes the circulation system work with “free energy” from the cooling load without any external energy source.
  • Additional heating means can be added, if there is not sufficient superheated gas available.
  • heating energy for generating pumping pressure of the secondary refrigerant can be achieved by heating the heat exchanger by any (waste) energy flowing in a liquid or gaseous media through lines to and from the heat exchanger.
  • the described systems can provide pressurized circulation of the secondary refrigerant of rotating parts in pumps or compressors and the refrigerating system requires limited regular maintenance.
  • fig. 1 shows an embodiment of the invention comprising compressor means
  • fig. 2 shows an alternative embodiment of the invention
  • fig. 3 describes a third embodiment of the invention
  • fig. 4 shows an alternative embodiment of the invention.
  • Fig. 1 shows a first cascade refrigerating system, where the cascade heat exchanger 2 is cooled by a primary refrigerating system 4.
  • the primary refrigerating system 4 can be any suitable system using any suitable refrigerant.
  • the heat exchanger 2 functions as the cascade condenser of the secondary refrigerating system. Liquid flows through the pipe 9 and alternates further through the pipe 8 or 10, which leads to non-return valves 12 or 14 and through the pipe 16 or 18 into the pumping vessels 20 or 22.
  • the outlet of the pumping vessels 20 or 22 are connected through pipe 24 or 26, through non-return valves 28 or 30 into the liquid line 32, which leads to flow restriction means 34, which restriction means might be electronically controlled expansion valves.
  • the restriction means 34 the secondary refrigerant is led to evaporators 40.
  • the outlet pipes 52 from the evaporator 40 are led to the cascade condenser 2.
  • a part stream of the liquid secondary refrigerant is led from the pumping vessels 20 or 22 through magnetic valves 120 and 122 and into the pipe 60 or 62 into one of the sections of a common heat exchanger 67, where liquid secondary refrigerant is evaporated when exposed to a heat source.
  • the evaporated refrigerant gas is led back to the related vessels 20, 22 through the pipes 68, 70 generating pressure for the operation of the system.
  • the common heat exchanger is heated by liquid primary refrigerant.
  • the entire liquid primary refrigerant leaves the cascade condenser through line 100 and is led to the central section of the common heat exchanger 67 from which the now subcooled primary refrigerant flows through line 106 towards the cascade expansion valve 112.
  • the vessel 20, 22 will in loading mode equalize pressure through pipe 72, 74, onto the solenoid valves 76, 78, through the pipes 80, 82, 84 into the common return line 52 or 44.
  • the vessel 20 operates at high pressure when supplying liquid and the vessel 22 operates at low pressure when loading liquid.
  • the solenoid valve 76 is closed and the liquid is trapped inside the HP vessel 20. Due to the high pressure, the inlet non-return valve 12 is closed and the outlet non-return valve 28 is open. By opening the solenoid valve 120, the trapped liquid is heated/evaporated by the heat exchanger 67, generating high pressure.
  • the solenoid valve 78 and 79 are open so the pressure of vessel 22 is equalized to the condenser 2 and the liquid is drained by gravity from the condenser 2 through non-return valve 14 to vessel 22.
  • the HP vessel (20) is empty, the system alternates.
  • the system is controlled by a monitoring device 21, 23 or by means of a timer (not shown).
  • the solenoid valve 79 in the common venting line 84 closes both the solenoid valves 76 and 78 equalizing the pressure between vessel 20 and 22.
  • the solenoid valve 78 closes, solenoid valves 76 and 79 opens and vessel 22 is now in operation as HP vessel supplying liquid.
  • the solenoid valve 76 and 79 are open so the pressure of vessel 20 is equalized to the condenser 2 and the liquid is drained by gravity from the condenser 2 through non-return valve 12 to vessel 20.
  • the HP vessel (22) is empty, the system alternates again.
  • the system can operate by changing between an active (supplying) and an inactive (loading) vessel during the entire operation.
  • Fig. 2 shows an alternative embodiment of the invention. Most of the functions of the second refrigerating system are equal to those shown in fig. 1, thus they will not be mentioned. The only differences between fig. 1 and 2 will be mentioned in the following.
  • the major difference is that the common heat exchanger 48 in fig. 2 is connected differently than in fig. 1.
  • the common heat exchanger 48 is supplied through a line 46, where the secondary refrigerant returns mostly as a gas from the evaporator 40.
  • the heating energy for generating pumping pressure of the secondary refrigerant can be achieved by superheating the suction gas from the evaporating means 40 or from additional superheating means 42, which makes the circulation system work with "free energy" from the cooling load without any external energy source. Additional heating means can be added, if there is not sufficient superheated gas available (not shown).
  • the superheated refrigerant is led through line 46 to the common heat exchanger 48, where refrigerant is heated/evaporated in the other parts of the heat exchanger.
  • the refrigerant leaves through line 50, which leads towards the condenser 2.
  • Fig. 3 describes a third embodiment of the invention by showing a combination of the features from fig. 1 and fig. 2.
  • Two common heat exchangers 48 and 67 are used.
  • the common heat exchanger 48 operates as described in fig. 2
  • the common heat exchanger 67 operates as described in fig. 1. This way the two exchangers can operate parallel with two different "free energy" heat sources.
  • Fig. 4 shows an alternative embodiment, which is very much like the system shown in fig. 3, thus only the differences will be described. The only difference is that additional cooling/condenser means are shown, which can operate parallel to the condenser 2 to condense the secondary refrigerant.
  • the cooling/condenser means 92 could i.e. be an outdoor "free cooling" coil, which during winter can reduce the temperature of the refrigerant so that condensing is performed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Jet Pumps And Other Pumps (AREA)
EP07002617A 2006-02-07 2007-02-07 Kälteanlage mit Umlauf von flüssigem Kältemittel durch Druck Withdrawn EP1816415A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DKPA200600173 2006-02-07

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EP1816415A2 true EP1816415A2 (de) 2007-08-08
EP1816415A3 EP1816415A3 (de) 2010-11-24

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TW (1) TWD121118S1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016017697A (ja) * 2014-07-08 2016-02-01 株式会社前川製作所 アイスリンクの冷却設備及び冷却方法
CN110425776A (zh) * 2019-08-19 2019-11-08 北京丰联奥睿科技有限公司 一种v型竖管蒸发式冷却塔及其双控制空调系统
CN114251862A (zh) * 2020-09-24 2022-03-29 北京市京科伦工程设计研究院有限公司 单级二氧化碳多联机冷热多功能中央空调

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD579923S1 (en) 2007-01-05 2008-11-04 Apple Inc. Ear piece
CN106705489B (zh) * 2017-01-20 2019-05-24 上海理工大学 结合空气源热泵热水的变制冷剂流量系统及其控制方法

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1146428A (en) 1967-09-26 1969-03-26 John Edward Watkins Liquid refrigerant recirculating system
DE3511421A1 (de) 1985-03-29 1986-10-02 Brown Boveri - York Kälte- und Klimatechnik GmbH, 6800 Mannheim Kaeltemittelkreislauf fuer eine kaelteanlage
JPH1123079A (ja) 1997-06-27 1999-01-26 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH11132507A (ja) 1997-10-29 1999-05-21 Daikin Ind Ltd 冷凍装置
EP1046868A2 (de) 1999-04-19 2000-10-25 Luciano Zanon Kälteanlage mit einem ein optimiertes Verbrauch bietenden Kältekreislauf
JP2002048422A (ja) 2000-07-31 2002-02-15 Kyoritsu Reinetsu Kk ヒートポンプ
EP0857936B1 (de) 1995-10-24 2003-01-08 Daikin Industries, Limited Wärmetransportsystem
EP1536190A1 (de) 2003-11-28 2005-06-01 Birton A/S Kälteanlage mit Umlauf von flüssigem Kältemittel durch Druck

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1146428A (en) 1967-09-26 1969-03-26 John Edward Watkins Liquid refrigerant recirculating system
DE3511421A1 (de) 1985-03-29 1986-10-02 Brown Boveri - York Kälte- und Klimatechnik GmbH, 6800 Mannheim Kaeltemittelkreislauf fuer eine kaelteanlage
EP0857936B1 (de) 1995-10-24 2003-01-08 Daikin Industries, Limited Wärmetransportsystem
JPH1123079A (ja) 1997-06-27 1999-01-26 Mitsubishi Heavy Ind Ltd 冷凍装置
JPH11132507A (ja) 1997-10-29 1999-05-21 Daikin Ind Ltd 冷凍装置
EP1046868A2 (de) 1999-04-19 2000-10-25 Luciano Zanon Kälteanlage mit einem ein optimiertes Verbrauch bietenden Kältekreislauf
JP2002048422A (ja) 2000-07-31 2002-02-15 Kyoritsu Reinetsu Kk ヒートポンプ
EP1536190A1 (de) 2003-11-28 2005-06-01 Birton A/S Kälteanlage mit Umlauf von flüssigem Kältemittel durch Druck

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
STOECKER W.F:: "Industrial refrigeration", pages: 241 - 251
STOECKER W.F:: "Industrial refrigeration", pages: 246 - 247

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016017697A (ja) * 2014-07-08 2016-02-01 株式会社前川製作所 アイスリンクの冷却設備及び冷却方法
CN110425776A (zh) * 2019-08-19 2019-11-08 北京丰联奥睿科技有限公司 一种v型竖管蒸发式冷却塔及其双控制空调系统
CN114251862A (zh) * 2020-09-24 2022-03-29 北京市京科伦工程设计研究院有限公司 单级二氧化碳多联机冷热多功能中央空调
US12345457B2 (en) 2020-09-24 2025-07-01 Beijing Jingkelun Engineering Design and Research Institute Co., Ltd. Single-stage carbon dioxide multi-split cooling and heating multifunctional central air conditioner

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TWD121118S1 (zh) 2008-01-21
EP1816415A3 (de) 2010-11-24

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