EP1264150B1 - Regulator with receiver for refrigerators and heatpumps - Google Patents

Regulator with receiver for refrigerators and heatpumps Download PDF

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Publication number
EP1264150B1
EP1264150B1 EP01911456A EP01911456A EP1264150B1 EP 1264150 B1 EP1264150 B1 EP 1264150B1 EP 01911456 A EP01911456 A EP 01911456A EP 01911456 A EP01911456 A EP 01911456A EP 1264150 B1 EP1264150 B1 EP 1264150B1
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EP
European Patent Office
Prior art keywords
receiver
evaporator
refrigerant
heat exchanger
heat
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.)
Expired - Lifetime
Application number
EP01911456A
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German (de)
French (fr)
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EP1264150A1 (en
Inventor
Lars Christian Wulff Zimmermann
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Expired - Lifetime 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers

Definitions

  • This invention relates to a refrigeration circuit as described in the first part of Claim 1.
  • a circuit like this is known from U.S. Pat. No.2520045, wherein the flow of refrigerant, between receiver and evaporator, is regulated by the difference between the pressure in the evaporator and the pressure in the receiver, which correspond to the temperature at the exit of the evaporator. In this way the difference in pressure between the evaporator and the receiver correspond to the superheat of the evaporator.
  • This interaction makes a self-balancing effect, because increasing superheat causes increasing flow, which causes decreasing superheat - and contrary. That means that the flow of refrigerant to the evaporator is controlled by the superheat of the evaporator, just like an ordinary, thermal expansion valve.
  • the invention distinct from the above mentioned refrigeration circuit by the features of the characterising part of claim 1.
  • the evaporator is completely inundated and the suction gas is supersaturated, which means that the suction gas leaving the evaporator contains refrigerant in liquid state.
  • the temperature in the receiver is controlled by heat exchange between the liquid from the condenser and the supersaturated suction gas. This causes a self-balancing effect because when the fluid content of the suction gas decreases then the temperature of the receiver increases, whereby the flow to the evaporator increases, and the fluid content of the suction gas increases - and contrary. In this way, the flow of refrigerant to the evaporator is controlled by the fluid content of the suction gas.
  • the SelfCoolingValve as described in first part of Claim 2. It is composed of a capillary tube and a heat exchanger, jointed together as an integrated device and placed at the entry of the evaporator or in a tube placed in continuation of the entry of the evaporator.
  • the technique of cooling refrigerant at the entry of the evaporator is known from U.S. Pat. No. 2956421, where same part of a capillary tube extends into the evaporator, makes an U-turn, and ends up at the entry point, where the discharging refrigerant flows across the capillary tube and cools it.
  • the SelfCoolingValve distinct from U.S. Pat. No. 2956421 by a heat exchanger, placed before the capillary tube, wherein the refrigerant is subcooled, before entering the capillary.
  • the present invention provides a refrigeration system where the evaporator is inundated, the suction gas is superheated before it come to compressor and the liquid from the condenser is sub-cooled. All three factors contribute to increase the Coefficient Of Performance (COP). Calculations confirmed by test show that the COP is increased by more than ten percent.
  • COP Coefficient Of Performance
  • the regulator is composed of four parts:
  • the purpose of the heat exchanger is to transfer heat from the liquid from the condenser to the suction gas.
  • the heat exchanger must have a large heat capacity, to suppress resonance between the evaporator and the receiver.
  • the heat capacity of the heat exchanger must be so large, that the pressure in the receiver reacts slower, than the fluid content of the suction gas, in respond to a change in the flow of refrigerant.
  • An appropriated heat capacity can be obtain by incorporating a reservoir with frost-proof water.
  • Fig. 2 & 3 show an instance composed by three concentric copper tubes.
  • the receiver (19) must be large enough to contain all of refrigerant in the system.

Landscapes

  • 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)
  • Details Of Measuring And Other Instruments (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • External Artificial Organs (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)

Abstract

The regulator is a refrigerant regulator intended for heatpumps and refrigerators. It has a built-in receiver, which automatically absorbs redundant refrigerant. It is a hermetic closed device without removable parts. It is robust and there is no need for adjustment. The regulator is composed of a heat exchanger with large heat capacity, a receiver and two pressure reducing valves. The two valves behave different on boiling fluid flow. One of them, named a heat sensitive valve, restricts fluid flow when the fluid is boiling. In the other valve, named a pressure sensitive valve, the boiling has no influence on the fluid flow. The regulator controls the refrigerant flow from the receiver to the evaporator by means of the pressure in the receiver-and the pressure in the receiver is controlled, via the heat exchanger, by the need of refrigerant in the evaporator. This way of control ensures 100% use of the evaporator, the suction gas is superheated, and the liquid from the condenser is sub-cooled. These factors improve the relation between the cooling capacity and the power consumption with more than 10%.

Description

This invention relates to a refrigeration circuit as described in the first part of Claim 1. A circuit like this is known from U.S. Pat. No.2520045, wherein the flow of refrigerant, between receiver and evaporator, is regulated by the difference between the pressure in the evaporator and the pressure in the receiver, which correspond to the temperature at the exit of the evaporator. In this way the difference in pressure between the evaporator and the receiver correspond to the superheat of the evaporator. This interaction makes a self-balancing effect, because increasing superheat causes increasing flow, which causes decreasing superheat - and contrary. That means that the flow of refrigerant to the evaporator is controlled by the superheat of the evaporator, just like an ordinary, thermal expansion valve.
The invention distinct from the above mentioned refrigeration circuit by the features of the characterising part of claim 1. The evaporator is completely inundated and the suction gas is supersaturated, which means that the suction gas leaving the evaporator contains refrigerant in liquid state. The temperature in the receiver is controlled by heat exchange between the liquid from the condenser and the supersaturated suction gas. This causes a self-balancing effect because when the fluid content of the suction gas decreases then the temperature of the receiver increases, whereby the flow to the evaporator increases, and the fluid content of the suction gas increases - and contrary. In this way, the flow of refrigerant to the evaporator is controlled by the fluid content of the suction gas.
To obtain the mentioned self-balancing effect, it is an indispensable assumption that the flow of refrigerant from the receiver to the evaporator increases/decreases when the temperature in the receiver increases/decreases. Using an ordinary capillary tube between the receiver and the evaporator, like U.S. Pat. No. 2520045, this assumption is only fulfilled when the temperature difference, between evaporator and receiver, is less than three Kelvin. If the difference exceed three Kelvin, the refrigerant is boiling so much, in the capillary tube, that the flow decreases when the temperature difference increases. Boiling refrigerant in the capillary tube can be avoided by subcooling the refrigerant before entering the capillary tube. The subcooling can be realized with a heat exchanger, establishing heat exchange between refrigerant entering the capillary tube and refrigerant leaving the capillary tube.
One way of implementing the mentioned subcooling is a The SelfCoolingValve, as described in first part of Claim 2. It is composed of a capillary tube and a heat exchanger, jointed together as an integrated device and placed at the entry of the evaporator or in a tube placed in continuation of the entry of the evaporator. The technique of cooling refrigerant at the entry of the evaporator is known from U.S. Pat. No. 2956421, where same part of a capillary tube extends into the evaporator, makes an U-turn, and ends up at the entry point, where the discharging refrigerant flows across the capillary tube and cools it. The SelfCoolingValve distinct from U.S. Pat. No. 2956421 by a heat exchanger, placed before the capillary tube, wherein the refrigerant is subcooled, before entering the capillary.
If the time for changing the fluid content of the suction gas is longer, than the time for changing the corresponding pressure in the receiver, it causes resonance between the evaporator and the receiver. This problem can be avoid by assigning an adequate heat capacity to the heat exchanger, which can be achieved by placing the heat exchanger in contact with a water reservoir, like an outer shell filled with water.
The present invention provides a refrigeration system where the evaporator is inundated, the suction gas is superheated before it come to compressor and the liquid from the condenser is sub-cooled. All three factors contribute to increase the Coefficient Of Performance (COP). Calculations confirmed by test show that the COP is increased by more than ten percent.
Explanation of the drawings.
  • Fig. 1 is a diagrammatic view of the SelfCoolingValve. It is composed by an inner tube (1) connected by a capillary tube (2) to en outer shell (3). The flow is from (4) to (5). The outer shell (3) is either the entry of the evaporator or it can be a tube placed in continuation of the entry (5).
  • Fig. 2 is a side view of the heat exchanger. It is build from three concentric tubes (6), (7) and (8). The inner tube (8) is for the suction gas, which flows from (9) to (10).The middle tube (7) makes a shell around the inner tube. It has a connecting-piece at top (11) and bottom (12). Fluid flows from (11) to (12).The outer tube (6) makes a shell around the middle tube. It contains frost-proof water, and is made hatch on the drawing.
  • Fig. 3 is a top view of the heat exchanger. The numbers have the same meaning as in fig. 2.
  • Fig. 4 shows a diagrammatic view of a refrigerating system embodying a compressor (16), a condenser (15), an evaporator (13) and a regulator (14). The regulator is composed by a HeatSensitivValve (17), a heat exchanger (18), a receiver (19) and a PressureSensitivValve (20). The heat exchanger (18) is shown in more details in fig. 2 and 3.
    • Construction
    The regulator is composed of four parts:
  • 17. HeatSensitivValve
  • 18. Heat exchanger with large heat capacity
  • 19. Receiver
  • 20. PressureSensitivValve
    • The numbers refer to fig. 4.
    HeatSensitivValve:
    This valve must comply with two demands:
    • Increasing pressure across the valve - increasing flow of refrigerant
    • Increasing temperature drop across the valve - decreasing flow of refrigerant
    A capillary tube complies with these demands. The diameter and length of the capillary tube can be calculated or found by experiment. Heat exchanger with large heat capacity:
    The purpose of the heat exchanger is to transfer heat from the liquid from the condenser to the suction gas. The heat exchanger must have a large heat capacity, to suppress resonance between the evaporator and the receiver. The heat capacity of the heat exchanger must be so large, that the pressure in the receiver reacts slower, than the fluid content of the suction gas, in respond to a change in the flow of refrigerant.
    An appropriated heat capacity can be obtain by incorporating a reservoir with frost-proof water.
    Fig. 2 & 3 show an instance composed by three concentric copper tubes.
    • The outer tube (6) makes a container with a suitable quantity of frost-proof water.
    • In the middle tube (7) the liquid flows from top (11) to bottom (12)
    • In the inner tube (8) the suction gas flows from top (9) to bottom (10)
    Receiver:
    The receiver (19) must be large enough to contain all of refrigerant in the system.
    PressureSensitivValve:
    This valve must comply with two demands:
    • Increasing pressure across the valve - increasing flow of refrigerant
    • The flow through the valve must not react on temperature change. That can be a capillary tube if the flow is subcooled down to the end temperature, before entering the capillary tube.
      The SelfCoolingValve shown in fig. 1 has this property. Warm refrigerant enters at (4).' In the tube (1), the flow is cooled to the same temperature as outside the tube. The refrigerant flows through the capillary tube (2) without boiling. From the capillary tube, the refrigerant discharges at the bottom of the outer tube (3). The refrigerant flows over the outside of the inner tube and hereby the tube is cooled. The refrigerant is boiling while absorbing heat. Fluid and vapour are flowing into the evaporator at (5).
    Principle of regulation. The numbers are referring to fig. 4.
    • When the refrigeration system starts, the compressor (16) suck in vapour from the evaporator (13). Hereby the pressure in the evaporator drops and the evaporator suck in fluid via the valve (20) from the receiver (19).
    • In the condenser (15) the pressure rises and warm fluid flows through the HeatSensitivValve (17). Caused by the drop i pressure in the valve (17), the refrigerant is boiling and a mixture of fluid and vapour flow into the heat exchanger (18). In the heat exchanger, vapour condenses doing heat ejection into the suction gas and the mass of the heat exchanger, causing the temperature to rise - slowly because of the large heat capacity.
    • As the temperature rises in the heat exchanger, the pressure in the receiver rises too and the flow of refrigerant into the evaporator increases.
    • After some while the evaporator is inundated and the suction gas contains refrigerant in liquid state. The liquid strongly affect the heat exchanger, where the temperature starts to go down - slowly because of the large heat capacity.
    • As the temperature in the heat exchanger falls, the pressure in the receiver falls too, and the flow of refrigerant into the evaporator decreases.
    • When the flow of refrigerant into the evaporator decreases, the fluid content of the suction gas decreases and thereby the cooling effect in the heat exchanger decreases, causing the temperature to rises.
    • The temperature in the receiver stabilizes, when the heat exchanger attains equilibrium between heat from condenser and cooling effect from the suction gas.

    Claims (3)

    1. A refrigeration circuit comprising a compressor (16), a condenser (15), an evaporator (13) and a receiver (19), a heat exchanger (18) exchanging heat between the suction gas from the evaporator to the compressor and the liquid from the condenser to the receiver, and first capillary throttling means (17) between the condenser and the heat exchanger and second capillary throttling means (20) between the receiver (19) and the evaporator (13), characterised in that the second capillary throttling means comprises a heat exchanger for subcooling the refrigerant entering the second capillary throttling means (20), whereby heat exchange takes place between the refrigerant entering the capillary tube and the refrigerant leaving the capillary tube, and the heat exchanger (18) exchanging heat between the suction gas from the evaporator to the compressor and the liquid from the condenser to the receiver whereby the heat exchanger has a large heat capacity.
    2. A closed refrigeration circuit as claimed in claim 1, characterised in that the second capillary throttling means is constructed as a self-cooling valve, comprising an outer shell (3), an inner tube (1) and a capillary tube (2), wound around the inner tube (1), having its entry connected to the outlet of the inner tube and its outlet to the bottom of the outer shell, whereby the refrigerant entering the capillary tube is subcooled by the refrigerant leaving the capillary tube.
    3. A closed refrigeration circuit as claimed in Claim 1, characterised in that the heat exchanger (18) has thermal contact with a reservoir of water, which contribute to the heat capacity of the heat exchanger.
    EP01911456A 2000-03-13 2001-03-05 Regulator with receiver for refrigerators and heatpumps Expired - Lifetime EP1264150B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DK200000398 2000-03-13
    DK200000398A DK174179B1 (en) 2000-03-13 2000-03-13 Circuit with capillary tube droplet and refrigerant tank
    PCT/DK2001/000142 WO2001073360A1 (en) 2000-03-13 2001-03-05 Regulator with receiver for refrigerators and heatpumps

    Publications (2)

    Publication Number Publication Date
    EP1264150A1 EP1264150A1 (en) 2002-12-11
    EP1264150B1 true EP1264150B1 (en) 2005-08-31

    Family

    ID=8159318

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP01911456A Expired - Lifetime EP1264150B1 (en) 2000-03-13 2001-03-05 Regulator with receiver for refrigerators and heatpumps

    Country Status (8)

    Country Link
    US (1) US20030097856A1 (en)
    EP (1) EP1264150B1 (en)
    AT (1) ATE303566T1 (en)
    AU (1) AU2001240471A1 (en)
    DE (1) DE60113072T2 (en)
    DK (1) DK174179B1 (en)
    NO (1) NO325992B1 (en)
    WO (1) WO2001073360A1 (en)

    Families Citing this family (9)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    FR2836542B1 (en) * 2002-02-26 2007-06-29 Valeo Climatisation RELIEF DEVICE FOR VEHICLE AIR CONDITIONING LOOP
    EP1422486A3 (en) * 2002-11-25 2004-11-17 Tempia Co., Ltd. Combined regeneration heating and cooling system
    DK176026B1 (en) * 2003-09-22 2005-12-19 Lars Zimmermann Circuit with two-stage capillary tube throttle and refrigerant container
    CN1942979B (en) 2005-02-18 2010-05-05 住友电气工业株式会社 Circulation cooling system for cryogenic cable
    DK176868B1 (en) * 2008-09-16 2010-02-01 Lars Christian Wulf Zimmermann Symmetrical refrigerant regulator for flooded multi-channel evaporator
    US20140116083A1 (en) * 2012-10-29 2014-05-01 Myungjin Chung Refrigerator
    JP2020034248A (en) * 2018-08-31 2020-03-05 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． refrigerator
    WO2020045868A1 (en) 2018-08-31 2020-03-05 Samsung Electronics Co., Ltd. Refrigerator
    CN114165964A (en) * 2020-08-21 2022-03-11 苏州三星电子有限公司 Series-parallel connection refrigerator and pipeline assembly thereof

    Family Cites Families (8)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    US2183346A (en) * 1937-04-01 1939-12-12 Westinghouse Electric & Mfg Co Refrigeration apparatus and method
    US2482171A (en) * 1945-10-04 1949-09-20 Gen Engineering & Mfg Company Flow control device for refrigeration apparatus
    US2530648A (en) * 1946-09-26 1950-11-21 Harry Alter Company Combination accumulator, heat exchanger, and metering device for refrigerating systems
    US2520045A (en) * 1947-01-09 1950-08-22 Carrier Corp Refrigeration system, including capillary tube
    US2797554A (en) * 1954-01-06 1957-07-02 William J Donovan Heat exchanger in refrigeration system
    US2956421A (en) * 1957-04-04 1960-10-18 Borg Warner Capillary refrigerating systems
    US4313315A (en) * 1980-02-19 1982-02-02 U.S. Philips Corporation Compressor refrigeration circuits
    EP0604593A4 (en) * 1991-09-19 1994-08-17 Mayer Holdings Sa Thermal inter-cooler.

    Also Published As

    Publication number Publication date
    WO2001073360A1 (en) 2001-10-04
    DE60113072D1 (en) 2005-10-06
    DE60113072T2 (en) 2006-06-14
    US20030097856A1 (en) 2003-05-29
    DK174179B1 (en) 2002-08-19
    NO20024334D0 (en) 2002-09-11
    EP1264150A1 (en) 2002-12-11
    AU2001240471A1 (en) 2001-10-08
    NO325992B1 (en) 2008-09-01
    DK200000398A (en) 2001-09-14
    NO20024334L (en) 2002-09-11
    ATE303566T1 (en) 2005-09-15

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