WO2012041474A2 - Heat exchanger arrangement and heat pump system - Google Patents

Heat exchanger arrangement and heat pump system Download PDF

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Publication number
WO2012041474A2
WO2012041474A2 PCT/EP2011/004804 EP2011004804W WO2012041474A2 WO 2012041474 A2 WO2012041474 A2 WO 2012041474A2 EP 2011004804 W EP2011004804 W EP 2011004804W WO 2012041474 A2 WO2012041474 A2 WO 2012041474A2
Authority
WO
WIPO (PCT)
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.)
Ceased
Application number
PCT/EP2011/004804
Other languages
French (fr)
Other versions
WO2012041474A3 (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.)
Thermia Varme 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
Priority to US13/822,459 priority Critical patent/US20130180281A1/en
Priority to CN2011800464763A priority patent/CN103238035A/en
Priority to EP11772871.7A priority patent/EP2622288A2/en
Publication of WO2012041474A2 publication Critical patent/WO2012041474A2/en
Publication of WO2012041474A3 publication Critical patent/WO2012041474A3/en
Anticipated expiration legal-status Critical
Ceased 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.

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  • 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

A heat exchanger arrangement is given comprising a heat exchanger (7), the heat exchanger (7) having a primary side connectable to a fluid circulation system and a secondary side exposed to a gas (13). This heat exchanger arrangement should be operated with little energy consumption. To this end the secondary side is connected to a duct (14) extending downwardly in the direction of gravity, when the duct (14) is connected to a cold side heat exchanger (7), and upwardly, when the duct is connected to a warm side heat exchanger.

Description

"Heat exchanger arrangement and heat pump system"
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.
Furthermore 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.
In a heat pump system a refrigerant which can be in liquid and in vapor phase is circulated through a circuit. 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.
Usually a fan or another driving means is used in order to drive enough air through the cold side heat exchanger. However, such a fan requires additional energy.
Furthermore, the fan is noisy.
The problem underlying the present invention is to operate the heat exchanger with little energy consumption .
This object is solved by a heat exchanger arrangement comprising the features of claim 1.
In particular the secondary side of the heat exchanger is connected to a duct extending downwardly in the direction of gravity.
When heat is absorbed from the air in the cold side heat exchanger the air cools down and the cold air has a higher density than the surrounding air. The idea is to use the potential energy of this heavy air to drive the air flow through the heat exchanger. By means of the duct the maximum available potential energy to drive the air through the heat exchanger is increased. Without the duct the maximum available potential energy comes from the thickness of the exchanger itself. However, if a duct is used the air cooled down by the heat exchanger cannot escape directly to the ambient or surrounding air but falls down in form of a volume which is limited in a direction perpendicular to its movement by the duct. Therefore, a greater volume of cold air is kept together which increases the potential energy.
In a preferred embodiment the duct extends in vertical direction. Therefore, the gravity can act on the cold air without any deviation.
Preferably the duct has a cross section corresponding to an area covering the secondary side of the heat exchanger. In this case 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.
In an advantageous embodiment the cross section decreases in a direction away from the heat exchanger. In this embodiment the air escaping from the duct is accelerated. The suction force driving the air through the heat exchanger is increased. This can be used to drive more air through the heat exchanger than with a constant cross section. Preferably 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.
Preferably 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.
Preferably the duct has a length of at least 0,5 m. The longer the duct the more potential energy is available. The length of at least 0,5 m relates to the vertical length of the duct in direction of gravity.
In a preferred embodiment 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.
Preferably 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 problem is solved with a heat pump system having the features of claim 10.
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.
Preferably the cold side heat exchanger is exposed to outdoor ambient air. In this case the outdoor ambient air can be used as heat source for the heat pump sys- tem. However, there is less or even no power necessary for driving the air through the cold side heat exchanger. This leads to a very good efficiency of the heat pump system. In the following, preferred embodiments of the invention will be described in further details with reference to the drawing, in which:
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, and 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. In 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. In the evaporator 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.
The following description is directed to the 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. In this example, the heat exchanger 7 comprises a plurality of pipe sections 11 through which the fluid of the circuit 2 flows. Furthermore, 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.
However, 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.
According to the embodiment described 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.
To this end 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.
At the bottom of the duct 14 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- duced 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. The greater the length of the duct 14 the more potential energy is available and the better is the efficiency of the heat exchanger 7. A fan can be operated with lower power consumption or a fan can be completely omitted.
In the embodiment of Fig. 2 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.
In Fig. 3 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. However, 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.
The effect of the cone form of the duct 14 that air in the duct 14 is accelerated in a direction downwards. Thus, the suction power of the duct 14 is increased and -lithe efficiency of the heat exchanger 7 is further increased.
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. In this case the cone has a rectangular section.

Claims

Claims
Heat exchanger arrangement comprising a heat exchanger (7), the heat exchanger having a primary side connectable to a fluid circulation system (2) and a secondary side exposed to a gas (13), charac terized in that the secondary side is connected to a duct (14) extending downwardly in the direction of gravity.
Heat exchanger arrangement according to claim 1, characterized in that the duct (14) extends in ver tical direction.
3. Heat exchanger arrangement according to claim 1 or 2, characterized in that the duct (14) has a cross section corresponding to an area covering the sec- ondary side of the heat exchanger (7).
Heat exchanger arrangement according to claim 3, characterized in that the cross section decreases in the direction away from the heat exchanger (7).
Heat exchanger arrangement according to any of claims 1 to 4, characterized in that the duct (14) has at least over a part of its length a circular cross section.
Heat exchanger arrangement according to any of claims 1 to 5, characterized in that the duct (14) comprises walls (17) having a thermal insulation.
Heat exchanger arrangement according to any of claims 1 to 6, characterized in that the duct (14) has a length of at least 0,5 m.
Heat exchanger arrangement according to any of claims 1 to 7, characterized in that the secondary side is free of fluid driving devices.
Heat exchanger arrangement according to any of claims 1 to 8, characterized in that a spacer arrangement (15) is arranged at the outlet of the duct (14) .
Heat pump system (1) comprising a circuit (2) for circulating a fluid, the circuit (2) comprising a fluid driven section (3), a warm side heat exchang er (4), an expansion valve (6), and a cold side heat exchanger (7), characterized in that the cold side heat exchangers (7) is part of a heat exchang er arrangement according to any of claims 1 to 9.
Heat pump system according to claim 10, characterized in that the cold side heat exchanger (7) is exposed to outdoor ambient air.
PCT/EP2011/004804 2010-09-27 2011-09-26 Heat exchanger arrangement and heat pump system Ceased WO2012041474A2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US13/822,459 US20130180281A1 (en) 2010-09-27 2011-09-26 Heat exchanger arrangement and heat pump system
CN2011800464763A CN103238035A (en) 2010-09-27 2011-09-26 Heat exchanger arrangement and heat pump system
EP11772871.7A EP2622288A2 (en) 2010-09-27 2011-09-26 Heat exchanger arrangement and heat pump system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA201000874 2010-09-27
DKPA201000874 2010-09-27

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WO2012041474A2 true WO2012041474A2 (en) 2012-04-05
WO2012041474A3 WO2012041474A3 (en) 2012-06-07

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PCT/EP2011/004804 Ceased WO2012041474A2 (en) 2010-09-27 2011-09-26 Heat exchanger arrangement and heat pump system

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US (1) US20130180281A1 (en)
EP (1) EP2622288A2 (en)
CN (1) CN103238035A (en)
WO (1) WO2012041474A2 (en)

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WO2012041474A3 (en) 2012-06-07
US20130180281A1 (en) 2013-07-18
EP2622288A2 (en) 2013-08-07

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