EP1536192A1 - Système frigorifique - Google Patents

Système frigorifique Download PDF

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Publication number
EP1536192A1
EP1536192A1 EP03027254A EP03027254A EP1536192A1 EP 1536192 A1 EP1536192 A1 EP 1536192A1 EP 03027254 A EP03027254 A EP 03027254A EP 03027254 A EP03027254 A EP 03027254A EP 1536192 A1 EP1536192 A1 EP 1536192A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
pressure
compressor
receivers
evaporators
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Withdrawn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
EP03027254A
Other languages
German (de)
English (en)
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.)
BIRTON AS
Original Assignee
BIRTON AS
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 filed Critical BIRTON AS
Priority to EP03027254A priority Critical patent/EP1536192A1/fr
Priority to EP04025510A priority patent/EP1536190A1/fr
Publication of EP1536192A1 publication Critical patent/EP1536192A1/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • F25B2400/161—Receivers arranged in parallel

Definitions

  • the invention relates to a refrigerating system where a refrigerant is conducted in piping by means of pressure produced by at least one compressor, the system including a condenser that may discharge refrigerant into at least two receivers through each their pipe branch provided with respective check valves, the receivers being arranged to supply refrigerant to at least one evaporators through a check valve associated with each receiver, where at least one compressor is arranged for supplying gas refrigerant at a first pressure level to the condenser.
  • Such a system is prior art and disclosed in GB 1,146,428, which relates to improvements in a flooded coil refrigerant system where tanks are designed for collecting a recirculating 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, similar to most other refrigerant systems..
  • one of the receivers are connected to the condenser, and liquid refrigerant is filling 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 is remaining and gas is led to the suction side of the compressor.
  • valves are opened and closed in order to change the operation of the receivers.
  • the purpose of the invention to provide a simple and energy efficient refrigerating system, that is suitable for refrigerant circulation, without using circulation pumps in refrigeration systems.
  • the system contains pressure generating means supplying refrigerant gas to the receivers at a second pressure level higher than the first pressure level, and where the refrigeration system is provided with a control circuit arranged to control a solenoid valve at the inlet of each receiver for altematingly supplying refrigerant gas to the receivers.
  • the refrigerating system according to the invention differs from prior art in having at least one compressor delivering refrigerant at a higher pressure and bypassing the condenser before entering the receivers.
  • the high pressure refrigerant is then used for pressing liquid refrigerant out of the receiver which is not being filled with a cooled refrigerant from the condenser.
  • the pressure difference between the high pressure gas and the normal condensing pressure must be high enough to provide a driving force for the refrigerant through a subsequent number of valves and evaporators before returning to compressors or the condenser.
  • the piping coming from the outlets of the first and the second compressors may be interconnected through a valve, which valve generates a pressure difference.
  • the system may be arranged in a preferred embodiment so that the evaporators are divided into a first group of evaporators for cooling at relatively high temperature and a second group of evaporators for cooling at a relatively low temperature, where the piping is arranged so as to conduct discharged refrigerant from the first group of evaporators directly to the condenser and to conduct discharged refrigerant from the second group of evaporators directly to the inlet of the compressors.
  • the system might instead comprise at least a first compressor for generating a first higher pressure level, and at least a second compressor for generating a second lower pressure, where the second compressor is connected to the receivers through controllable valves, and where at least the second compressor is connected to the condenser.
  • Fig. 1 shows a refrigerating system 2 comprising at one compressor 6 where the outlet from the first compressor 6 is through valve 60 connected through piping 8 for supply of warm refrigerant further into piping 10 which leads to a condenser 12, from which piping 14 is connected through valves 68,74 which valves 68,74 are no-return valves for which piping 76,78 leads to receivers 16,18.
  • the outlet of the receivers 16,18 are connected through no-return valves 20,22 to piping 24 which leads to flow restriction means 26,28,30,32 which restriction means might be electronically controlled expansion valves. From the restriction means, the refrigerant is led further to evaporators 34,36,38,40.
  • a gas pipe 46 connected to the piping 8 and forming a warm gas pipe 10, which is led to the condenser 12.
  • the outlets 48,50 of the evaporators 38,40 are combined in a piping 52, which contains a cold gas that is led to the inlet of the compressors 6.
  • the compressor 6 at its outlet reaches a pressure P1 where the gas reaches a pressure P2 after passage of valve 60, where P1 is higher than P2.
  • a pressure line 62 is connected to a magnetic valve 64,70 so that pressure from the compressor 6 where the pressure is P1 can be delivered through the magnetic valves 64,70 over piping 76,78 to the receivers 16,18.
  • compressors 6 will operate and deliver hot gas at the outlet line 62 at the pressure P1 and also hot gas with a pressure P2 at the line 8 after passage of valve 60.
  • the warm gas in the piping 8 is combined with gas coming from evaporators 34,36 which could be supermarket cooling equipments operating at a temperature which is over zero degrees, which means that a relatively low pressure drop has occurred over the evaporators 34,36 so that the pressure at the outlet from these evaporators are approximately equal to the pressure leaving the compressor 6 after passage of valve 60.
  • Piping 46 is led to a mixing point where piping 46 is combined with piping 8.
  • This receiver 16 is in this situation filled with liquid refrigerant, and in the meantime, pressure at P1 is led through the magnetic valve 70 towards the receiver which also has a no-return valve 74 connected to the liquid refrigerant line 14 but where this return valve is closed because of the pressure situation, high pressure is through line 78 led to the receiver 18 where this pressure P1 is activating the content of liquid refrigerant to flow to the outlet of the receiver 18, and through the no-return valve 22 to the piping 24 and from here to the evaporators 34,36,38,40.
  • the receiver 18 is empty which could be detected by detection means or by using a timer (not shown).
  • the detection or the timer means might communicate to an electronic system (also not shown), and when the receiver 18 is empty, the receiver 16 is probably more or less full of a liquid.
  • the magnetic valve 70 is closed and the magnetic valve 64 is opened. This leads to a change in the situation so liquid refrigerant is now pressed out by the pressure P1 from the receiver 16 through the one-way valve 20 and further to the evaporators 34,36,38,40 just as described with reference to the other receiver. In this way, the system can operate by changing between an active and an inactive receiver during the whole operation of the system 2.
  • Fig. 2 shows a refrigerating system 2 comprising compressors 4,5,6 where the outlet from the first compressor 4 is connected through piping 8 for supply of warm refrigerant further into piping 10 which leads to a condenser 12, from which piping 14 is connected through valves 68,74 which valves 68,74 are no-return valves for which piping 76,78 leads to receivers 16,18.
  • the outlet from the receivers 16,18 are connected through no-return valves 20,22 to piping 24 which leads to flow restriction means 26,28,30,32 which restriction means might be electronically controlled expansion valves. From the restriction means, the refrigerant is led further to evaporators 34,36,38,40.
  • a gas pipe 46 connected to the piping 8 and forming a warm gas pipe 10 which is led to the condenser 12.
  • the outlets 48,50 from the evaporators 38,40 are combined in a piping 52, which contains a cold gas that is led to the inlet of the compressors 4, 5, 6.
  • the compressor 4 at its outlet reaches a pressure P2 where the compressor 6 at its outlet reaches a pressure P1 where P1 is higher than P2.
  • a pressure line 62 is connected to a magnetic valve 64,70 so that pressure from the compressor 6 where the pressure is P2 can be delivered through the magnetic valves 64,70 over piping 76,78 to the receivers 16,18.
  • Magnetic valves 66,72 are connected to the inlet 76,78 to the receivers 16,18, where the magnetic valves 66,72 are connected to tubing 10 leading hot gas towards the condenser 12. Opening magnetic valves 66,77 is used to avoid critical pressure build up in the receiver.
  • At least one of the compressors 4, 5, 6 or maybe further compressors will operate and deliver hot gas at the outlet line 8 at the pressure P2 and also hot gas with a pressure P1 at the line 62.
  • the warm gas in the piping 8 is combined with gas coming from evaporators 34,36 which could be supermarket cooling equipments operating at a temperature which is over zero degrees, which means that a relatively low pressure drop has occurred over the evaporators 34,36 so that the pressure at the outlet from these evaporators are approximately equal to the pressure leaving the compressor 4.
  • Piping 46 is led to a mixing point where piping 46 is combined with piping 8.
  • This receiver 16 is in this situation filled with liquid refrigerant, and in the meantime, pressure at P1 is led through the magnetic valve 70 towards the receiver which also has a no-return valve 74 connected to the liquid refrigerant line 14 but where this return valve is closed because of the pressure situation, high pressure is through line 78 led to the receiver 18 where this pressure P1 is activating the content of liquid refrigerant to flow to the outlet of the receiver 18, and through the no-return valve 22 to the piping 24 and from here to the evaporators 34,36,38,40.
  • the receiver 18 is empty which could be detected by detection means or by using a timer (not shown).
  • the detection or timer means might communicate to an electronic system (also not shown), and when the receiver 18 is empty.
  • the receiver 16 is probably more or less full of a liquid.
  • the magnetic valve 70 is closed and the magnetic valve 64 is opened. This leads to a change in the situation so liquid refrigerant is now pressed out by the pressure P2 from the receiver 16 through the one-way valve 20 and further to the evaporators 34,36,38,40 just as described with reference to the other receiver. In this way, the system can operate by changing between an active and an inactive receiver during the whole operation of the system 2.
  • valve 60 is placed which in an open situation is shunting between the pressure P1 and P2 so these two pressures are equalised.
  • the compressor 6 can be used for producing warm gas for the condenser, and in this way, increase the flow to the condenser if necessary.
  • the valve 60 might be a modulated solenoid valve or a pressure controlled valve where only part of the hot gas delivered from the compressor 6 is delivered through the valve 60. In this way, the pressure P1 is still achieved but most of the hot gas that is produced by the compressor 6 is led through the valve 60 towards the line 8.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP03027254A 2003-11-28 2003-11-28 Système frigorifique Withdrawn EP1536192A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP03027254A EP1536192A1 (fr) 2003-11-28 2003-11-28 Système frigorifique
EP04025510A EP1536190A1 (fr) 2003-11-28 2004-10-27 Système de refroidissement avec circulation de réfrigérant liquide par pression

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03027254A EP1536192A1 (fr) 2003-11-28 2003-11-28 Système frigorifique

Publications (1)

Publication Number Publication Date
EP1536192A1 true EP1536192A1 (fr) 2005-06-01

Family

ID=34442890

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03027254A Withdrawn EP1536192A1 (fr) 2003-11-28 2003-11-28 Système frigorifique

Country Status (1)

Country Link
EP (1) EP1536192A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2492617A3 (fr) * 2011-02-25 2013-03-13 Leprieur Michel Dispositif pour améliorer la performance des installations frigorifiques
CN107024045A (zh) * 2011-06-13 2017-08-08 阿雷斯科技术有限公司 冷凝器蒸发器系统及其操作方法
US10260779B2 (en) 2011-06-13 2019-04-16 Aresco Technologies, Llc Refrigeration system and methods for refrigeration

Citations (3)

* 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
EP1046868A2 (fr) * 1999-04-19 2000-10-25 Luciano Zanon Système frigorifique comprenant un circuit frigorifique à consommation optimalisée

Patent Citations (3)

* 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
EP1046868A2 (fr) * 1999-04-19 2000-10-25 Luciano Zanon Système frigorifique comprenant un circuit frigorifique à consommation optimalisée

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2492617A3 (fr) * 2011-02-25 2013-03-13 Leprieur Michel Dispositif pour améliorer la performance des installations frigorifiques
CN107024045A (zh) * 2011-06-13 2017-08-08 阿雷斯科技术有限公司 冷凝器蒸发器系统及其操作方法
US10260779B2 (en) 2011-06-13 2019-04-16 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
CN107024045B (zh) * 2011-06-13 2020-01-31 阿雷斯科技术有限公司 冷凝器蒸发器系统及其操作方法
US10989445B2 (en) 2011-06-13 2021-04-27 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
US11549727B2 (en) 2011-06-13 2023-01-10 Aresco Technologies, Llc Refrigeration system and methods for refrigeration

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