US20110154849A1 - Symmetric refrigerant regulator for flooded multichannel evaporator - Google Patents

Symmetric refrigerant regulator for flooded multichannel evaporator Download PDF

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US20110154849A1
US20110154849A1 US13/061,631 US200913061631A US2011154849A1 US 20110154849 A1 US20110154849 A1 US 20110154849A1 US 200913061631 A US200913061631 A US 200913061631A US 2011154849 A1 US2011154849 A1 US 2011154849A1
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Prior art keywords
evaporator
refrigerant
heat exchanger
suction
condenser
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US13/061,631
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Lars Christian Wulff Zimmermann
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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
    • F25B13/00—Compression machines, plants or systems, with reversible 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/052—Compression system with heat exchange between particular parts of the system between the capillary tube and another part of the refrigeration cycle

Definitions

  • the invention relates to a refrigerant circuit with a compressor (A), a condenser (D), a evaporator (C) and a suction-gas heat exchanger wherein the refrigerant is capillary-tube throttled in two steps, firstly from the condenser to the suction-gas heat exchanger (F) and then from the suction-gas heat exchanger to the evaporator (E).
  • the purpose of such a circuit is to distribute the refrigerant so that the evaporator is flooded, and that the suction gas at the compressor inlet is overheated.
  • Such a circuit is known from DK174179 wherein the suction-gas heat exchanger condenses the vapour which reaches the fluid container so that only pure liquid is conducted further. Simultaneously the heat exchanger regulates the pressure in the container—and thereby regulates the magnitude of the flow of refrigerant to the evaporator. The magnitude of this flow of refrigerant controls the extent of flooding (or overheating) of the suction gas which controls how strong the suction-gas heat exchanger cools the condensate between the two throttling steps. The process is self-adjusting, and when equilibrium is reached, the evaporator is flooded.
  • FIG. 1 Compressor (A), 4-way valve (B) wherein the direction of the flow of refrigerant can be changed.
  • Evaporator/condenser (C,D) is symmetrical and connected through two nozzles, e.g. two identical capillary tubes (E,F) which meets in the suction-gas heat exchanger (H), and heat exchanger with the suction line (G).
  • FIG. 2 shows a regulator for multichannel evaporator/condenser.
  • 3 capillary tubes (E) for connection to the evaporator and 2 capillary tubes (F) for connection to the condenser.
  • the suction line (G) is guides through the external jacket (H) which exhibits channels for the capillary tubes.
  • FIG. 3 shows the temperatures in the suction-gas heat exchanger.
  • Te is the temperature of the suction gas at the inlet of the heat exchanger, and Tx is the “almost” constant temperature at the liquid side.
  • Tc shows how the temperature of the condenser lies with respect to the heat exchanger.
  • FIGS. 4 and 5 show calculations of the circuit in an enthalpy-log(pressure)-diagram.
  • the refrigerant is R290
  • the evaporation temperature is ⁇ 25° C.
  • the condensing temperature is 45° C.
  • the circuit in FIG. 4 has a larger load of refrigerant than the circuit in FIG. 5 , which pulls the evaporator (EF) further to the left.
  • the line segment CD is enthalpy transferred by the heat exchanger
  • the line segment (FG) is the corresponding shift of the evaporator towards lower enthalpy.
  • the evaporator contains almost 3 times so much refrigerant as the evaporator in FIG. 5 .
  • the invention differs from DK 174179 in that the liquid container is lacking. Instead the amount of circulated refrigerant is adjusted to the load conditions by binding excess refrigerant in the evaporator. This happens by the excess of refrigerant, through the suction-gas heat exchanger, lowers the enthalpy at the inlet of the evaporator whereby the ratio between vapour and liquid is shifted—so that the density of the refrigerant is increased.
  • the construction is symmetric and the flow of refrigerant can be changed so that the evaporator and condenser exchange their functions. This provides the opportunity for defrosting of the evaporator—or that the evaporator can be applied for both cooling and heating.
  • the method is independent of the gravitational field and it can function in aeroplanes wherein the system is turned up side down, and in space crafts completely without gravitational field.
  • the method is self-adjusting and without movable parts, and therefore it can be placed in inaccessible places or it can be embedded completely in insulation foam.
  • the invention can be applied with all sizes of systems and with most refrigerants—albeit not zeotropic mixtures with large temperature slip, because in this case, the regulation of the enthalpy of the evaporator would imply large fluctuations of the temperature of the evaporator.
  • the throttling means consists of two throttling steps separated by a suction-gas heat exchanger wherein the flow velocity through the suction-gas heat exchanger is so high that liquid and gas are not separated.
  • the two throttling steps can be established by two nozzles, e.g. two capillary tubes, and the suction-gas heat exchanger by two concentric tubes which fulfil the following two requirements:
  • the heat transfer property must be sufficient for removing all fluid refrigerants from the suction gas, under all operational conditions.
  • the flow velocity, at the condenser side, must be so high that liquid and gas are not separated. This is fulfilled at turbulent flow defined by Reynolds's number being larger than 3000.
  • the condensate passes the suction-gas heat exchanger as a mixture of liquid and vapour wherein there is thermodynamic equilibrium between pressure and temperature.
  • the suction gas removes enthalpy from the condensate, some of the vapour condensates—but no significant change of the pressure appears and therefore no change in the temperature either.
  • the suction gas passes the condensate in counter current and is heated to a temperature close to the temperature of the condensate.
  • This process is self-adjusting
  • a drop in enthalpy at the evaporator inlet implies a larger density in the evaporator—and thereby a binding of the refrigerant—which reduces the cause—which was excess of circulating refrigerant.
  • the construction is symmetrical and the flow of the refrigerant can be changed so that the evaporator and condenser exchange function.
  • the invention can easily be extended to regulate systems wherein the evaporator and/or the condenser are partitioned into several sections.
  • the nozzles to and from the suction-gas heat exchanger can be replaced by more parallel nozzles so that there is a separate nozzle for each section in the evaporator/condenser.
  • the partition into many parallel nozzles does not provide any problems at the collection of refrigerant from many condenser sections, but the distribution of refrigerant to many evaporator sections could be a problem in that some nozzles are supplied much liquid while others are supplied are supplied much vapour. This problem is solved by requirement of a turbulent flow in the heat exchanger which ensures a homogeneous mixture of liquid and vapour, which can then be distributed to many nozzles without problems.
  • Compressor SC21CNX2 is for R290 and has a power of 750 Watt at the evaporation temperature ⁇ 25 Celsius and condensation temperature 45 Celsius, corresponding to a flow of mass of 3 gram/second.
  • Both capillary tubes have a diameter of 1 mm and a length 1000 mm, corresponding to a capacity of 27.4 litre of nitrogen per minute.
  • FIG. 3 shows that the heat exchanger at maximum must transfer 50% of the refrigeration power, here 400 W, at a temperature difference of 30 Kelvin, which requires an area of 90 cm2.
  • the diameter of the suction line is 10 mm, so 90 cm2 corresponds to the surface of about 30 cm of the suction line.
  • the heat exchanger consists of two concentric copper tubes with length 300 mm.
  • the inner tube is the suction line having an outer diameter of 10 mm, and the outer tube is chosen with an inner diameter of 10.4 mm so that the distance between the tubes becomes 0.2 mm.
  • the opening between the tubes becomes 6 mm2, and from this it can be calculated that Reynolds' number lies in the range 3200 and 6000, which ensures turbulent flow.
  • the direction of flow of the refrigerant can be changed so that the evaporator and condenser changes function.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

A regulator of refrigerant for a refrigeration circuit with flooded evaporator. The refrigerant can be distributed to many separate evaporator channels. The flow of refrigerant can be changed so that the evaporator and condenser change functions. This provides the opportunity for a fast defrosting of the evaporator or the evaporator can alternately be applied for cooling and heating. The regulator functions independently of the gravitational field and therefore it can be applied for air-conditioning systems in aeroplane and space crafts. The regulator is without movable parts. It has two throttling steps, e.g. two capillary tubes separated by a suction-gas heat exchanger. It requires neither adjustment nor maintenance and therefore it can be placed at inaccessible places or it can be embedded completely in insulation foam.

Description

    TECHNICAL FIELD
  • The invention relates to a refrigerant circuit with a compressor (A), a condenser (D), a evaporator (C) and a suction-gas heat exchanger wherein the refrigerant is capillary-tube throttled in two steps, firstly from the condenser to the suction-gas heat exchanger (F) and then from the suction-gas heat exchanger to the evaporator (E).
  • The purpose of such a circuit is to distribute the refrigerant so that the evaporator is flooded, and that the suction gas at the compressor inlet is overheated.
    • BACKGROUND ART
  • Such a circuit is known from DK174179 wherein the suction-gas heat exchanger condenses the vapour which reaches the fluid container so that only pure liquid is conducted further. Simultaneously the heat exchanger regulates the pressure in the container—and thereby regulates the magnitude of the flow of refrigerant to the evaporator. The magnitude of this flow of refrigerant controls the extent of flooding (or overheating) of the suction gas which controls how strong the suction-gas heat exchanger cools the condensate between the two throttling steps. The process is self-adjusting, and when equilibrium is reached, the evaporator is flooded.
    • BRIEF DESCRIPTION OF FIGURES
  • FIG. 1: Compressor (A), 4-way valve (B) wherein the direction of the flow of refrigerant can be changed. Evaporator/condenser (C,D) is symmetrical and connected through two nozzles, e.g. two identical capillary tubes (E,F) which meets in the suction-gas heat exchanger (H), and heat exchanger with the suction line (G).
  • FIG. 2 shows a regulator for multichannel evaporator/condenser. In the figure there is shown 3 capillary tubes (E) for connection to the evaporator and 2 capillary tubes (F) for connection to the condenser. The suction line (G) is guides through the external jacket (H) which exhibits channels for the capillary tubes.
  • FIG. 3 shows the temperatures in the suction-gas heat exchanger. Te is the temperature of the suction gas at the inlet of the heat exchanger, and Tx is the “almost” constant temperature at the liquid side. Tc shows how the temperature of the condenser lies with respect to the heat exchanger.
  • FIGS. 4 and 5 show calculations of the circuit in an enthalpy-log(pressure)-diagram. The refrigerant is R290, the evaporation temperature is −25° C. and the condensing temperature is 45° C. The circuit in FIG. 4 has a larger load of refrigerant than the circuit in FIG. 5, which pulls the evaporator (EF) further to the left. The line segment CD is enthalpy transferred by the heat exchanger, and the line segment (FG) is the corresponding shift of the evaporator towards lower enthalpy. In FIG. 4 the evaporator contains almost 3 times so much refrigerant as the evaporator in FIG. 5.
    Figure US20110154849A1-20110630-P00001
    •  DISCLOSURE OF THE INVENTION
  • The invention differs from DK 174179 in that the liquid container is lacking. Instead the amount of circulated refrigerant is adjusted to the load conditions by binding excess refrigerant in the evaporator. This happens by the excess of refrigerant, through the suction-gas heat exchanger, lowers the enthalpy at the inlet of the evaporator whereby the ratio between vapour and liquid is shifted—so that the density of the refrigerant is increased.
  • The construction is symmetric and the flow of refrigerant can be changed so that the evaporator and condenser exchange their functions. This provides the opportunity for defrosting of the evaporator—or that the evaporator can be applied for both cooling and heating. The method is independent of the gravitational field and it can function in aeroplanes wherein the system is turned up side down, and in space crafts completely without gravitational field.
  • The method is self-adjusting and without movable parts, and therefore it can be placed in inaccessible places or it can be embedded completely in insulation foam.
  • The invention can be applied with all sizes of systems and with most refrigerants—albeit not zeotropic mixtures with large temperature slip, because in this case, the regulation of the enthalpy of the evaporator would imply large fluctuations of the temperature of the evaporator.
    • The New Technical Means (Claim 1):
  • The throttling means consists of two throttling steps separated by a suction-gas heat exchanger wherein the flow velocity through the suction-gas heat exchanger is so high that liquid and gas are not separated.
  • The two throttling steps can be established by two nozzles, e.g. two capillary tubes, and the suction-gas heat exchanger by two concentric tubes which fulfil the following two requirements:
  • The heat transfer property must be sufficient for removing all fluid refrigerants from the suction gas, under all operational conditions.
  • The flow velocity, at the condenser side, must be so high that liquid and gas are not separated. This is fulfilled at turbulent flow defined by Reynolds's number being larger than 3000.
    • The Technical Effect (Claim 1):
  • The condensate passes the suction-gas heat exchanger as a mixture of liquid and vapour wherein there is thermodynamic equilibrium between pressure and temperature. When the suction gas removes enthalpy from the condensate, some of the vapour condensates—but no significant change of the pressure appears and therefore no change in the temperature either. The suction gas passes the condensate in counter current and is heated to a temperature close to the temperature of the condensate.
  • This process is self-adjusting
  • Proof:
  • When the refrigeration circuit has an excess of refrigerant, this results in a drop in enthalpy at the outlet of the evaporator. The change of enthalpy cannot pass the heat exchanger since the suction-gas temperature after the exchanger is “almost” constant—and the drop in enthalpy will therefore be transferred to the condenser side, where the enthalpy at the inlet of the evaporator drops correspondingly.
  • A drop in enthalpy at the evaporator inlet implies a larger density in the evaporator—and thereby a binding of the refrigerant—which reduces the cause—which was excess of circulating refrigerant.
  • Similarly, when the circuit lacks refrigerant:
  • This causes an increase of the enthalpy at the outlet of the evaporator. The change of enthalpy cannot pass by the heat exchanger because the suction-gas temperature after the heat exchanger is “almost” constant—and the increase in enthalpy will therefore be transferred to the condenser side where the enthalpy at the inlet of the evaporator increases correspondingly.
  • An increase in enthalpy at the inlet of the evaporator implies less density in the evaporator—and thereby the refrigerant is released—which reduces the cause—which was a deficit of circulating refrigerant.
  • The construction is symmetrical and the flow of the refrigerant can be changed so that the evaporator and condenser exchange function.
  • Figure US20110154849A1-20110630-P00002
    • The New Technical Means (Claim 2):
  • The invention can easily be extended to regulate systems wherein the evaporator and/or the condenser are partitioned into several sections.
  • The nozzles to and from the suction-gas heat exchanger can be replaced by more parallel nozzles so that there is a separate nozzle for each section in the evaporator/condenser.
    • The Technical Effect (Claim 2):
  • The partition into many parallel nozzles does not provide any problems at the collection of refrigerant from many condenser sections, but the distribution of refrigerant to many evaporator sections could be a problem in that some nozzles are supplied much liquid while others are supplied are supplied much vapour. This problem is solved by requirement of a turbulent flow in the heat exchanger which ensures a homogeneous mixture of liquid and vapour, which can then be distributed to many nozzles without problems.
    • EXAMPLE
  • Compressor SC21CNX2 is for R290 and has a power of 750 Watt at the evaporation temperature −25 Celsius and condensation temperature 45 Celsius, corresponding to a flow of mass of 3 gram/second. Both capillary tubes have a diameter of 1 mm and a length 1000 mm, corresponding to a capacity of 27.4 litre of nitrogen per minute.
  • FIG. 3 shows that the heat exchanger at maximum must transfer 50% of the refrigeration power, here 400 W, at a temperature difference of 30 Kelvin, which requires an area of 90 cm2. The diameter of the suction line is 10 mm, so 90 cm2 corresponds to the surface of about 30 cm of the suction line.
  • The heat exchanger consists of two concentric copper tubes with length 300 mm. The inner tube is the suction line having an outer diameter of 10 mm, and the outer tube is chosen with an inner diameter of 10.4 mm so that the distance between the tubes becomes 0.2 mm. The opening between the tubes becomes 6 mm2, and from this it can be calculated that Reynolds' number lies in the range 3200 and 6000, which ensures turbulent flow.
    • SUMMARY OF ADVANTAGES OF THE INVENTION
  • It is as simple and robust regulator of refrigerant for systems with flooded evaporator, including multichannel evaporators with several parallel sections.
  • The direction of flow of the refrigerant can be changed so that the evaporator and condenser changes function.
  • It does not require adjustment or maintenance and it can be placed at inaccessible places.
  • It functions independently of the gravitational field and it can be applied in aeroplanes and space crafts.

Claims (4)

1. A refrigeration circuit comprising: a compressor, an evaporator, a condenser, a suction-gas heat exchanger, and a throttling means composed of a pressure -reducing nozzle connecting the bottom of said condenser to said suction-gas heat exchanger, and a pressure-reducing nozzle connecting said suction-gas heat exchanger to said evaporator, wherein the flow of refrigerant through said suction-gas heat exchanger is turbulent at the side of the condensate.
2. A refrigeration circuit according to claim 1 wherein the evaporator and/or the condenser are partitioned in several sections, and wherein each section is connected to the heat exchanger through a separate pressure-reducing nozzle.
3. A refrigeration circuit according to claim 1 further comprising a means (B) for changing the direction of the flow of refrigerant through the evaporator and condenser.
4. A refrigeration circuit according to claim 2 further comprising a means (B) for changing the direction of the flow of refrigerant through the evaporator and condenser.
US13/061,631 2008-09-16 2009-09-13 Symmetric refrigerant regulator for flooded multichannel evaporator Abandoned US20110154849A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DKPA200801298 2008-09-16
DKPA200801298A DK176868B1 (en) 2008-09-16 2008-09-16 Symmetrical refrigerant regulator for flooded multi-channel evaporator
PCT/DK2009/050238 WO2010031402A1 (en) 2008-09-16 2009-09-13 Symmetric refrigerant regulator for flooded multichannel evaporator

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WO (1) WO2010031402A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11369125B2 (en) * 2017-06-28 2022-06-28 Guangzhou Guangshen Electric Produce Co., Ltd Pre-cooling and freshness-preserving cooling control device employing dual throttling systems for ice-cream machine, cooling control method, and ice-cream machine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2785540A (en) * 1953-09-30 1957-03-19 Westinghouse Electric Corp Heat pumps
US4106308A (en) * 1977-05-19 1978-08-15 The Singer Company Heating and cooling system with capillary control means
US5167275A (en) * 1989-12-06 1992-12-01 Stokes Bennie J Heat exchanger tube with turbulator
USRE37630E1 (en) * 1995-03-14 2002-04-09 Hussmann Corporation Refrigerated merchandiser with modular evaporator coils and EEPR control

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Publication number Priority date Publication date Assignee Title
JP3322292B2 (en) * 1995-10-23 2002-09-09 日立電線株式会社 Heat transfer tube
DK174179B1 (en) * 2000-03-13 2002-08-19 Lars Zimmermann Circuit with capillary tube droplet and refrigerant tank
CN1389677A (en) * 2002-07-10 2003-01-08 邹自才 Improved air conditioner
JP3811123B2 (en) * 2002-12-10 2006-08-16 松下電器産業株式会社 Double tube heat exchanger
CN1752610A (en) * 2004-09-24 2006-03-29 乐金电子(天津)电器有限公司 Overcooling structure for air conditioner
JP3982545B2 (en) * 2005-09-22 2007-09-26 ダイキン工業株式会社 Air conditioner
JP2008070053A (en) * 2006-09-14 2008-03-27 Samsung Electronics Co Ltd Air conditioner

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2785540A (en) * 1953-09-30 1957-03-19 Westinghouse Electric Corp Heat pumps
US4106308A (en) * 1977-05-19 1978-08-15 The Singer Company Heating and cooling system with capillary control means
US5167275A (en) * 1989-12-06 1992-12-01 Stokes Bennie J Heat exchanger tube with turbulator
USRE37630E1 (en) * 1995-03-14 2002-04-09 Hussmann Corporation Refrigerated merchandiser with modular evaporator coils and EEPR control

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11369125B2 (en) * 2017-06-28 2022-06-28 Guangzhou Guangshen Electric Produce Co., Ltd Pre-cooling and freshness-preserving cooling control device employing dual throttling systems for ice-cream machine, cooling control method, and ice-cream machine

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DK176868B1 (en) 2010-02-01
WO2010031402A1 (en) 2010-03-25

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