Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D3/00—Hot-water central heating systems
  • F24D3/12—Tube and panel arrangements for ceiling, wall, or underfloor heating
  • F24D3/14—Tube and panel arrangements for ceiling, wall, or underfloor heating incorporated in a ceiling, wall or floor
  • F24D3/146—Tubes specially adapted for underfloor heating
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D3/00—Hot-water central heating systems
  • F24D3/18—Hot-water central heating systems using heat pumps
• • 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
  • 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
  • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D7/06—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits having a single U-bend
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
  • Y02B30/12—Hot water central heating systems using heat pumps

Definitions

• the invention relates to a heat pump comprising a compressor for circulating a refrigerant, an evaporator for the evaporation of liquid refrigerant, in heat exchange relationship with an external fluid, and a condensor for the condensation of the evaporated refrigerant.
• a heat pump of this type is characterized in that the evaporator comprises a first tube to be contacted by the external fluid at the outside thereof, which is connected at one end to the suction side of the compressor and is closed at the other end, and a second tube connected to the condensor, which extends substantially coaxially into said first tube from said one end thereof and opens at some distance from the other, closed end of the first tube to form the throttling means of the evaporator.
• said first tube is surrounded by an elongated tubular outer casing forming part of a conduit for circulating the external fluid.
• FIG 1 is a diagrammatic view of a heat pump in accordance with the invention
• FIG 2 is a transparent perspective view of the evaporator and a tube forming an outer casing thereof, which conveys the external fluid.
• the heat pump disclosed in FIG 1 comprises a compressor 10 which pumps a refrigerant such as freon to a condensor 11 and therefrom to an evaporator 12 which is more clearly disclosed in FIG 2.
• the evaporator is arranged inside an outer casing formed by a tube 13, which is closed at one end thereof at 14 and is connected to a circulation pump 15 at the other end thereof.
• a number of tubes 16 of a smaller cross section than the tube 13 are connected at one end thereof to the tube 13.
• tubes 13 and 18 form manifolds for the tubes 16.
• the tubes 13, 16 and 18 preferably are made of a highly durable and flexible synthetic elastomer such as polyvinyl cloride (PVC) in which case they may comprise black PVC tubes of the type used for fresh water networks, or ethylene-propylene-diene-monomer (EPDM). It is essential that the material of the tubes is impervious to corrosion, ultraviolet light and chemi cal deterioration and eliminates freeze-up problems.
• PVC polyvinyl cloride
• EPDM ethylene-propylene-diene-monomer
• the tubes 13, 16 and 18 form a heat exchanger for supplying heat to the evaporator 12, and this heat ex- changer may be located in the ground so that the fluid circulated therein absorbs ground heat, or may be suspended in stands which are located e.g. on a garage or car port roof or on a wall or a fence, so that the fluid circulated therein absorbs air heat.
• the tubes 16 in each group consist of an ab sorber mat which is marketed under the registered trade mark SolaRoll and is manufactured by Bio-Energy Systems, Inc., Ellenville, New York, USA. They can be arranged in the end return configuration shown in FIG 1 but other configurations known in the art may be arranged such as the butterfly type or the grid type.
• a balanced flow as that shown in FIG 1 wherein the circulating fluid has the same flow direction in the tubes 13 and 18 is preferred over the unbalanced flow with opposite flow directions in said tubes.
• the external fluid which has absorbed heat during the passage of the heat exchanger described passes the evaporator 12 in heat exchange relationship therewith to supply the heat necessary for the evaporation of the liquid refrigerant supplied to the evaporator.
• the external fluid usually would have a temperature of 6 to 8°C but the temperature may be as low as 2°C.
• the external fluid passing through the tube 13 in heat exchange relationship with the evaporator 12 such fluid may be heated in a sun collector or be supplied from a remote heating network or it may comprise subsoil water which is pumped from the ground and is re-interfiltered into the ground after having passed the evaporator in heat exchange relationship therewith.
• the heat evaporator 12 comprises a first tube 20 which has end walls 21 and 22 and thus is completely closed against the interior of the tube 13 in which the evaporator is located.
• a second tube 23 passes through the end wall 21 and extends into the first tube 20 substantially coaxially therewith. The inner end of the second tube 23 opens at some distance from the other end wall 22.
• a conduit 24 connects the tube 20 at the end closed by the end wall 21, to the compressor 10 at the suction side thereof, the pressure side being connected to the inlet of the condensor 11 by a conduit 25, and a conduit 26 connects the tube 23 to the outlet of the condensor.
• the condensor is arranged in heat exchange relationship with a second external fluid, such as water, which serves as a heat carrier for distributing the heat recovered in the condensor, e.g. to radiators of a central heating system in a building.
• a second external fluid such as water
• the liquid refrigerant is supplied upstreams of the external fluid passing through the tube 13 to the tube 23 and from the open end of the tube the refrigerant evaporates during absorption of heat from the external fl u i d and then passes through the tube 20 in the opposite flow direction to that of the liquid refrigerant in the tube 23 and the external fluid in the tube 13 to the conduit 24 in order to be sucked-in again by the compressor 10 and to be compressed by said compressor.
• the tube 23 thus forms the throttling means of the evaporator 12.
• the liquid refrigerant supplied through the tube 23 is cooled by the surrounding refrigerant in the tube 20 during its flow towards the. open end of the tube 23 where the refrigerant is evaporated and enters into the tube 20, and by this cooling of the refrigerant supplied the effect described above will be achieved, which means that the flow of refrigerant is adjusted to the amount of heat supplied by the external fluid in the tube 13.
• the tube 13 has an internal diameter of about 40 mm.
• the said first tube 20 of the evaporator 12 has an internal diameter of about 19 mm, while the said second tube 23 has an internal diameter of 4.7 to 4.8 mm.
• the refrigerant is supplied to the tube 23 from the conduit 26 at a temperature of e.g. 40 to 50°C and is cooled in the tube 23 to vaporizing temperature of 10 to 20°C.
• the external fluid used for supplying heat to the evaporator 12 is a circulating fluid as in the embodiment described.
• a length of tube forming the outer casing of the evaporator and having a length of e.g. 15 m may be placed in the ground for heat exchange between the refrigerant and the external fluid received by the tube.
• the external fluid is non-circulating and consists suitably of water.
• the evaporator 12 is located in an outer casing.
• the evaporator may be submerged into the water of a sea, a lake, a river or other natural source of an external fluid suitable for the supply of evaporation heat to the evaporator.

Landscapes

• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
• Central Heating Systems (AREA)
• Control Of The Air-Fuel Ratio Of Carburetors (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

Family

ID=20341483

Family Applications (1)

Country Status (15)

Cited By (3)

Families Citing this family (4)

Citations (2)

Family Cites Families (4)

• 1980
  • 1980-07-25 SE SE8005384A patent/SE424772B/sv not_active IP Right Cessation
• 1981
  • 1981-07-17 GB GB08223843A patent/GB2102552B/en not_active Expired
  • 1981-07-17 WO PCT/SE1981/000219 patent/WO1982000511A1/en not_active Ceased
  • 1981-07-17 JP JP56502433A patent/JPS57501141A/ja active Pending
  • 1981-07-17 DE DE813152231T patent/DE3152231A1/de not_active Withdrawn
  • 1981-07-17 NL NL8120274A patent/NL8120274A/nl unknown
  • 1981-07-17 AU AU74111/81A patent/AU7411181A/en not_active Abandoned
  • 1981-07-17 CH CH1789/82A patent/CH649370A5/fr not_active IP Right Cessation
  • 1981-07-22 YU YU01809/81A patent/YU180981A/xx unknown
  • 1981-07-24 FR FR8114445A patent/FR2487488A1/fr active Granted
  • 1981-07-24 CA CA000382456A patent/CA1167653A/en not_active Expired
  • 1981-07-24 BE BE2/59279A patent/BE889732A/fr not_active IP Right Cessation
• 1982
  • 1982-03-19 FI FI820972A patent/FI71835C/fi not_active IP Right Cessation
  • 1982-03-24 NO NO820978A patent/NO151869C/no unknown
  • 1982-03-24 DK DK132882A patent/DK132882A/da not_active Application Discontinuation

Patent Citations (2)

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