EP2622288A2 - Agencement d'échangeur thermique et système de pompe thermique - Google Patents

Agencement d'échangeur thermique et système de pompe thermique

Info

Publication number
EP2622288A2
EP2622288A2 EP11772871.7A EP11772871A EP2622288A2 EP 2622288 A2 EP2622288 A2 EP 2622288A2 EP 11772871 A EP11772871 A EP 11772871A EP 2622288 A2 EP2622288 A2 EP 2622288A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
duct
heat
arrangement according
air
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Withdrawn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
EP11772871.7A
Other languages
German (de)
English (en)
Inventor
Albrecht Wurtz
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.)
Danfoss Varmepumpar AB
Original Assignee
Thermia Varme AB
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 Thermia Varme AB filed Critical Thermia Varme AB
Publication of EP2622288A2 publication Critical patent/EP2622288A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B30/00—Heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels

Definitions

  • the invention relates to a heat exchanger arrangement comprising a heat exchanger, the heat exchanger having a primary side connectable to a fluid circulation system, and a secondary side exposed to a gas.
  • the invention relates to a heat pump system comprising a circuit for circulating a fluid, the circuit comprising a fluid driving section, a warm side heat exchanger, an expansion valve, and a cold side heat exchanger.
  • a refrigerant which can be in liquid and in vapor phase is circulated through a circuit.
  • the vapor In compressor driven systems, the vapor is com- pressed by the compressor. The temperature of the vapor rises. The hot vapor is guided through the warm side heat exchanger. Heat emitted from the warm side heat exchanger can be used for space - or tap water heating. The vapor cools down and changes its phase to a liquid. The liquid is allowed to expand in the expansion valve. The expanded liquid is guided through the cold side heat exchanger. In the cold side heat exchanger the liquid adsorbs heat from air and evaporates.
  • Other systems like absorption or adsorption heat pump systems run without a compressor but still have a cold side heat exchanger and a warm side heat exchanger.
  • the problem underlying the present invention is to operate the heat exchanger with little energy consumption .
  • the secondary side of the heat exchanger is connected to a duct extending downwardly in the direction of gravity.
  • the duct extends in vertical direction. Therefore, the gravity can act on the cold air without any deviation.
  • the duct has a cross section corresponding to an area covering the secondary side of the heat exchanger.
  • all air flowing through the heat exchanger is used to form the volume of cold air which in turn drives the air through the heat exchanger.
  • the cross section decreases in a direction away from the heat exchanger.
  • the air escaping from the duct is accelerated.
  • the suction force driving the air through the heat exchanger is increased.
  • the duct has at least over a part of its length a circular cross section.
  • the relation between the cross section and the length of the surrounding wall in circumferential direction is an optimum in the section of the duct which has a circular cross section. Therefore, the air in the duct is less thermally influenced by the ambient temperature.
  • the duct comprises walls having a thermal insulation. This is an alternative or additional feature to avoid heating of the air within the duct by warmer air outside of the duct. Since the temperature difference between the air inside the duct and the ambient air outside the duct is not very high a rather small thermal insulation is sufficient.
  • the duct has a length of at least 0,5 m.
  • the length of at least 0,5 m relates to the vertical length of the duct in direction of gravity.
  • the secondary side is free of fluid driving devices.
  • the duct allows an operation with less fan energy, i.e. a smaller fan can be used or a fan which is driven with less power. In an optimum configuration the duct is sufficient to drive enough air through the secondary side of the heat exchanger.
  • a spacer arrangement is arranged at the out- let of the duct.
  • the spacer arrangement prevents clos- ing of the duct, in particular keeps a sufficient distance to a base plate on which the duct is erected.
  • the air (or any other gas or liquid) is driven through the cold side heat exchanger with the help of the potential energy of the air which is increased when the duct is used.
  • the cold side heat exchanger is exposed to outdoor ambient air.
  • the outdoor ambient air can be used as heat source for the heat pump sys- tem.
  • Fig. 1 is a schematical illustration of a heat pump system
  • Fig. 2 shows a first embodiment of a heat exchanger arrangement
  • Fig. 3 shows a second embodiment of a heat exchanger arrangement
  • Fig. 4 shows a third embodiment of a heat exchanger arrangement
  • Fig. 1 shows schematically a heat pump system 1 comprising a circuit 2 for circulating a refrigerant.
  • the refrigerant is a fluid which can have a liquid phase and a gaseous phase within the circuit 2.
  • the state of the fluid depends on temperature and pressure condi- tions within certain sections of the circuit 2.
  • the circuit 2 comprises a compressor 3 operating as fluid driving section compressing the gaseous fluid.
  • the energy necessary for this compression is taken from an electrical power supply for example. During compression the temperature of the fluid increases.
  • the compressor 3 is followed by a condenser 4 in which heat 5 is emitted to e. g. tap water, radiators, floor heating or the like.
  • heat 5 is emitted to e. g. tap water, radiators, floor heating or the like.
  • the condenser 4 the fluid is cooled and leaves the condenser as a liquid.
  • the liquid is passed through an expansion valve 6 which allows the fluid to expand. After leaving the expansion valve 6 the fluid has a lower pressure.
  • the liquid under a lower pressure runs through an evap orator 7.
  • heat 8 is absorbed from ambient air so that the fluid evaporates.
  • the vapor is again passed to the compressor 3.
  • the system illustrated in Fig. 1 can be replaced by any other heat pump system having a cold side heat exchanger and a warm side heat exchanger, e.g. an absorption heat pump system or an adsorption heat pump system both operating without compressor.
  • the condenser 4 is a warm side heat exchanger and the evaporator 7 is a cold side heat exchanger.
  • Fig. 2 shows the cold side heat exchanger 7.
  • the cold side heat exchanger 7 has a first connection 9 which is or can be connected to the expansion valve 6 and a second connection 10 which is or can be connected to the compressor 3.
  • the heat exchanger 7 comprises a plurality of pipe sections 11 through which the fluid of the circuit 2 flows.
  • the heat exchanger comprises a plurality of fins 12 which are in heat conducting connection with the pipe sections 11 so that heat can be transmitted from the fins 12 to the pipe sections 11.
  • Other types of heat exchangers can be used as well, e.g. "microchannel" heat exchangers where the fluid passes through thin and flat tubes with approximately rectangular cross section.
  • a stream of air 13 (symbolized by an arrow) should be directed through the heat exchanger 7 in order that heat is transmitted from the air 13 to the fluid pass- ing through the heat exchanger 7. This heat is neces ⁇ sary to evaporate the fluid in the heat exchanger 7.
  • the heat exchanger 7 exhibits a certain flow resistance against the stream of air 13 so that usually a fan is necessary to drive the air 13 to the heat exchanger 7.
  • this fan can be omitted or at least driven with less power so that the overall power consumption of the heat exchanger 7 is decreased.
  • the heat exchanger 7 is connected with a duct 14.
  • the duct 14 is arranged below the heat exchanger 7 in the direction of gravity. Preferably it is directed in the direction of gravity.
  • the cross section of the duct 14 corresponds to the area of the heat exchanger 7 through which air 13 flows during the operation.
  • a spacer 15 is arranged so that an opening 16 remains which cannot be closed inad- vertently.
  • the duct comprises walls 17 which have a thermal insulation. Therefore, a heat exchange between the air in the interior of the duct 14 and the ambient air is re- symbolized to a minimum.
  • the heat exchanger 7 uses gravity or natural convection .
  • Ambient air 13 is getting in contact with the heat ex- changer 7 and is cooled down by the heat exchanger 7. Heat is transferred from the air 13 to the fluid in the circuit 2. When the air gets colder the density of the air 13 increases. Therefore, the now colder air 13 will fall down through the heat exchanger 7 and into the duct 14 placed under the heat exchanger 7. The cool and heavy air remains in the duct 14 moving downwardly and drawing ambient air 13 through the heat exchanger 7.
  • the duct 14 has an effective length of at least 0,5 m.
  • the effective length is the length in the direction of gravity. It is more preferred that the length is greater, for example 1 m, 1,5 m or 2 m or even more.
  • a fan can be operated with lower power consumption or a fan can be completely omitted.
  • the duct has the same cross section as the area of the heat exchanger 7 through which the ambient air 13 passes. In other words, if this area of the heat exchanger 7 is rectangular the duct 14 also has a rectangular cross section.
  • Fig. 3 shows an alternative embodiment.
  • Fig. 3a shows a side elevation and
  • Fig. 3b shows a view from the bot- tom.
  • the same elements as in Fig. 2 are marked with the same reference numerals.
  • the duct 14 has a rather large part of it's length in which (Fig. 3b) the cross section of the duct 14 is circular.
  • the area of the cross section of the duct 14 is the same as the effective area of the heat exchanger 7 so that there is basically no change in the flow condition of the ambient air 13 through the heat exchanger 7 and the duct 14.
  • the duct 14 has a wall 17 which is shorter in circumferential direction than with a rectangular cross section as in Fig. 2. In this way the risk of a heat transfer from the ambient air to the air inside the duct 14 is further reduced.
  • a transition section 18 is provided to give a smooth transition from the area of the heat exchanger 7 to the duct 14.
  • Fig. 4 shows a third embodiment. The same elements are designated with the same reference numerals.
  • the duct 14 still has a circular cross section. However, the wall 17 are inclined inwardly in the direction of gravity. So the duct 14 forms a cone having an open- ing 19 forming a kind of nozzle. The opening 19 has a much smaller cross section than the top of the duct 14.
  • a reduction of the effective area of the duct 14 can of course also be used in connection with the embodiment shown in Fig. 2.
  • the cone has a rectangular section.

Landscapes

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

Abstract

La présente invention concerne un agencement d'échangeur thermique qui comprend un échangeur thermique (7), l'échangeur thermique (7) comportant un côté primaire qui peut être raccordé à un système de circulation de fluide et un côté secondaire exposé à un gaz (13). Cet agencement d'échangeur thermique nécessite peu de consommation d'énergie pour son fonctionnement. Dans ce but, le côté secondaire est raccordé à une conduite (14) qui s'étend vers le bas dans la direction de la gravité, lorsque la conduite (14) est raccordée à un échangeur thermique de côté froid (7), et vers le haut, lorsque la conduite est raccordée à un échangeur thermique de côté chaud.
EP11772871.7A 2010-09-27 2011-09-26 Agencement d'échangeur thermique et système de pompe thermique Withdrawn EP2622288A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA201000874 2010-09-27
PCT/EP2011/004804 WO2012041474A2 (fr) 2010-09-27 2011-09-26 Agencement d'échangeur thermique et système de pompe thermique

Publications (1)

Publication Number Publication Date
EP2622288A2 true EP2622288A2 (fr) 2013-08-07

Family

ID=44983478

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11772871.7A Withdrawn EP2622288A2 (fr) 2010-09-27 2011-09-26 Agencement d'échangeur thermique et système de pompe thermique

Country Status (4)

Country Link
US (1) US20130180281A1 (fr)
EP (1) EP2622288A2 (fr)
CN (1) CN103238035A (fr)
WO (1) WO2012041474A2 (fr)

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JPS55143390A (en) * 1979-04-24 1980-11-08 Pioneer Electronic Corp Natural convection type radiator
JPS57182041A (en) * 1981-04-30 1982-11-09 Sharp Corp Heat pump type air conditioner
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DE3226804A1 (de) * 1982-07-17 1984-01-19 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur beheizung von einzelraeumen
US4495777A (en) * 1983-01-10 1985-01-29 Babington Thomas G Load shaving system
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JP2605994B2 (ja) * 1991-04-16 1997-04-30 ダイキン工業株式会社 空気調和機
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US20030182955A1 (en) * 1999-06-07 2003-10-02 Toyotaka Hirao Vehicular air conditioner
CA2455582C (fr) * 2001-08-10 2010-11-02 Queen's University At Kingston Systeme d'energie thermique a rincage par ecoulement inverse passif
BR0301427A (pt) * 2003-05-15 2004-12-21 Multibras Eletrodomesticos Sa Arranjo para circulação de ar por convecção natural em refrigerador
US7036559B2 (en) * 2003-07-08 2006-05-02 Daniel Stanimirovic Fully articulated and comprehensive air and fluid distribution, metering, and control method and apparatus for primary movers, heat exchangers, and terminal flow devices
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TWI251666B (en) * 2004-12-06 2006-03-21 Ind Tech Res Inst Method for measuring average velocity pressure
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Also Published As

Publication number Publication date
CN103238035A (zh) 2013-08-07
WO2012041474A3 (fr) 2012-06-07
WO2012041474A2 (fr) 2012-04-05
US20130180281A1 (en) 2013-07-18

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