EP1831631A2 - Agent caloporteur et circuit de thermopompe - Google Patents

Agent caloporteur et circuit de thermopompe

Info

Publication number
EP1831631A2
EP1831631A2 EP05820443A EP05820443A EP1831631A2 EP 1831631 A2 EP1831631 A2 EP 1831631A2 EP 05820443 A EP05820443 A EP 05820443A EP 05820443 A EP05820443 A EP 05820443A EP 1831631 A2 EP1831631 A2 EP 1831631A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
heat
refrigerant
tube
shaped
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Withdrawn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
EP05820443A
Other languages
German (de)
English (en)
Inventor
Kai Schiefelbein
Steffen Smollich
Michael Schaumlöffel
Hubert Nolte
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.)
Stiebel Eltron GmbH and Co KG
Original Assignee
Stiebel Eltron GmbH and Co KG
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
Priority claimed from DE200410061673 external-priority patent/DE102004061673A1/de
Priority claimed from DE102005002282.0A external-priority patent/DE102005002282B4/de
Application filed by Stiebel Eltron GmbH and Co KG filed Critical Stiebel Eltron GmbH and Co KG
Priority to EP12160171.0A priority Critical patent/EP2469208A3/fr
Publication of EP1831631A2 publication Critical patent/EP1831631A2/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Withdrawn legal-status Critical Current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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
    • F24F12/003—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid using a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0096—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater combined with domestic apparatus
    • 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
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/12—Heat pump
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/14—Solar energy
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F24D2200/20—Sewage water
    • 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
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F24D2200/22—Ventilation air
    • 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
    • F24D3/08—Hot-water central heating systems in combination with systems for domestic hot-water supply
    • 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
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/20—Solar thermal
    • 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
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/70—Hybrid systems, e.g. uninterruptible or back-up power supplies integrating renewable energies
    • 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
    • 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]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • 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]
    • Y02B30/56—Heat recovery units

Definitions

  • the present invention relates to a heat exchanger with a piping system for a refrigerant and a piping system for a fluid and a heat pump circuit of a ventilation system with a supercritical refrigerant in the high-pressure region, which has a heat exchanger.
  • Heat exchangers of the type mentioned are known from the prior art in large numbers which are coupled to each other for the transmission of heat energy from one medium to the other.
  • the heat exchanger on a plurality of sections, which are hydraulically connected to each other in parallel or in series.
  • the heat exchanger i.d.R. a plurality of partial sections, which are hydraulically connected to each other in parallel and / or serially while viewing each of a line system.
  • Such heat exchangers are implemented, for example, in a heat pump circuit of a ventilation system, which has a refrigerant which is in the High pressure range is supercritical.
  • a heat exchanger absorbs heat from an outside air flow or from an exhaust air and transmits this to the refrigerant.
  • Such ventilation systems are known for example from DE 197 02 903 A1, DE 199 13 861 C1 or DE 101 03 150 A1.
  • DE 101 03 51 A1 the additional use of the exhaust air emerging from the first heat exchanger is also provided by a waste heat pump.
  • waste heat from exhaust air and / or wastewater has been of particular importance since the EnEV Energy Savings Ordinance entered into force in February 2002.
  • a heating system based on the use of waste heat reduces its primary energy requirements for DHW heating, ventilation and heating very clearly.
  • the system technology used can even have an effect on the granting or non-granting of a building permit.
  • a fluid channel comprises a sheet with approximately U-, V- or W-shaped cross-sectional profile, which at the ends of the U, V or W shape is closed by a metal sheet, wherein the refrigerant is arranged in a tube parallel to the longitudinal axis of the fluid channel in the fluid channel.
  • the shape of the Fluid channel already gives a sub-channel high mechanical stability. At the same time allows the selected shape of the fluid channel by nesting the components of both piping systems with simplified production and the formation of a compact design of the entire, constructed from each other hydraulically interconnected sub-channels heat exchanger.
  • the ratio of the cross-sectional areas of the fluid channel and the tube corresponds to the ratio of the respective k-factors of the refrigerant and the fluid.
  • This design measure is also used to compensate for the amount of heat to be absorbed by the other medium by balancing the amount of heat to be absorbed by the other medium to optimize the overall heat transfer.
  • an area ratio of approximately 2: 1 is set. If propane is used as refrigerant, an area ratio of approx. 4: 1 to 5: 1 must be set. In one embodiment of the invention, an area ratio of 3: 1 is set.
  • the legs of the approximately U-shaped, V-shaped or W-shaped sheet are at an angle ⁇ to one another via which the abovementioned area ratio can be set within a wide range, while the geometry remains the same.
  • an angle ⁇ of about 67 ° between the legs of the approximately U-, V- or W-shaped plate of the fluid channel is set.
  • the tube is fixed between the legs of the approximately U, V or W-shaped sheet.
  • the tube is fixed to the U-, V- or W-shaped plate in that it is pressed on, soldered, welded and / or lasered.
  • the fixation additionally increases the stability of the arrangement, while the contact of the tube with the approximately U-, V- or W-shaped sheet also results in an additional possibility for heat transfer by heat conduction, that is to say a substantial enlargement of the surface - A -
  • the tube is arranged approximately at the center of gravity of the plane spanned by the legs of the approximately U, V or W-shaped plate.
  • the tube is flowed freely over its entire circumference of the fluid of the fluid channel, which also ensures good heat transfer by forced convection with good surface utilization.
  • various measures are known to those skilled in the art for enlarging the outer surface of the tube, such as e.g. Clamping of sheets or fixing of substantially longitudinally aligned to the flow direction ribs.
  • a sub-section of three elements is constructed, wherein the tube is in the approximately U-, V- or W-shaped plate and the approximately U-, V- or W-shaped plate is arranged on a support plate.
  • the carrier sheet has in one embodiment of the invention, essentially the same surface area as the U, V or W-shaped plate.
  • the U-, V- or W-shaped plate advantageously adjoins perpendicular to its longitudinal axis in the region of a leg to another U-, V- or W-shaped plate, so that in particular in the case of a plurality of U-, V - or W-shaped sheets results in a total of one type of corrugated metal.
  • This structure is flowing meandering through the fluid or can be flowed through by the fluid meandering.
  • a tube is connected at least one end with a similar tube.
  • This arrangement can also be designed as a meandering curved single tube with rectilinear sections.
  • an arrangement of tube, U-, V- or W-shaped sheet metal and carrier sheet is combined as a layer in the heat exchanger.
  • a layer is over another layer with equal arranged so that the carrier sheet of the first layer forms the covering sheet of the second layer.
  • the U-, V- or W-shaped sheet in the area in which it is in superficial contact with the tube, and the support plate in the area in which it with the U, V or W -shaped sheet in superficial contact recesses to enable a common soldering on.
  • a stack of the aforementioned elements is formed, which are connected together in one process step.
  • a production method is used in which a soldering process takes place in a vacuum oven in order to securely solder all of the elements together in a single soldering process.
  • a production method results, according to which a tube is inserted in each case into a valley of a U, V or W-shaped metal sheet and the U, V or W-shaped metal sheet is placed on a carrier sheet, wherein the U-, V- or W-shaped plate is provided with recesses in the contact area with the tube and the carrier plate with recesses in the contact area with the U-, V- or W-shaped plate, solder in each case in a valley of a U-, V- or W-shaped sheet inserted and the said elements are soldered together without further prior pre-fixation.
  • the method thus only includes the steps of stacking and vacuum soldering to obtain a fully connected assembly.
  • the proportion of manual work has thus been reduced to a minimum, as well as the number of different materials and / or auxiliary materials to be used.
  • the recesses in the U-, V- or W-shaped plate and the carrier plate are produced in one embodiment as a perforation, perforation and / or sections of slit.
  • the recesses in the U-, V- or W-shaped sheet and the carrier sheet are preferably produced by punching, drilling and / or lasers.
  • the recesses are formed as slots and / or perforations with dimensions such that they are substantially closed in the course of the common soldering. So then the individual layers are formed fluid-tight against each other within the heat exchanger.
  • the U-, V- or W-shaped sheet is made with periodic continuation perpendicular to a later flow direction by section-wise pressing and / or deep drawing of a sheet.
  • a degree of dimensional stability is achieved which is sufficient, in an assembly of parts before and during soldering, to always form a valley of an upper U, V or W-shaped sheet with a lower U, V, or W-shaped sheet relative to each other in matching position.
  • This arrangement principle, required for the above-described solder joint can guarantee, with sufficient dimensional accuracy of the U, V or W-shaped large unit sheets, that even multi-layered assemblies can be readily joined and sealed in one soldering step. Such a process is then very efficient and economical.
  • a heat exchanger according to the invention is preferably designed as a countercurrent heat exchanger, with carbon dioxide operated in particular as the refrigerant in the supercritical range being selected.
  • the inventively provided pipelines are particularly suitable.
  • tubes with strong pressures are resilient, so that in particular bursting pressure tests of a heat exchanger of the above-mentioned type of construction according to the invention are generally well passed.
  • Water is preferably selected as the fluid, which already points to heat pumps and domestic air conditioning systems as an essential area of application of heat exchangers according to the invention.
  • the tube, the U-, V- or W-shaped plate, the carrier plate and a fluid-tight outer housing are made in embodiments of the invention made of copper or stainless steel.
  • a heat exchanger or a heat exchanger and a second heat exchanger for the overheating of the at least partially evaporated refrigerant is provided, wherein the banksü- bertrager, which is at least traversed by outside air, in the flow direction of the refrigerant in heating operation in front of the second heat exchanger, in heat is transferred from the exhaust air of the ventilation system to the refrigerant and / or that in addition to a heat exchanger, a heat exchanger is arranged as a gas cooler in the outside air flow in front of the ventilation system, in which heat is transferred from the supercritical in a high pressure area refrigerant to the outside air stream.
  • the abovementioned solution therefore comprises the three alternatives of a two-stage subcooling of the refrigerant, a two-stage overheating of the refrigerant, and a combination of two-stage super-cooling and two-stage superheating of the same refrigerant.
  • a two-stage subcooling of the refrigerant the goal of a thermodynamic improvement of the cycle of the heat release circuit is achieved by a second heat exchanger is connected downstream of a first heat exchanger as a gas cooler. This second heat exchanger serves to transfer the remaining heat of the supercritical refrigerant, for example, to the outside air, so that this outside air now reaches temperatures of 0 0 C or more.
  • the second heat exchanger advantageously also simultaneously effects a significant reduction in the heat exchanger outlet temperature of the refrigerant.
  • the power output defined as the quotient of heating power and compressor drive power is significantly increased, because the usable heat and cooling capacity increases without the need for additional electric compressor power.
  • a heat pump circuit to an evaporator of the refrigerant then includes a further heat exchanger in which the refrigerant is safely overheated or re-evaporated to protect the compressor, wherein the refrigerant is operated in the high pressure region of the heat pump cycle in a supercritical region and the heat pump cycle with increased efficiency.
  • the two alternatives mentioned above are combined with each other, resulting in a two-stage overheating and a two-stage super-cooling of the refrigerant in the same heat pump cycle.
  • the advantages listed above are added together with a thermodynamic increase in the efficiency of the refrigerant circuit and an increase in the safety of the operation, which is characterized in particular by a longer service life of the compressor.
  • the second heat exchanger is preferably connected upstream of the outside air input as a heat exchanger designed as an air-to-air heat exchanger.
  • the outside air is preheated by the heat emitted from the second heat exchanger, while at the same time the refrigerant of the heat exchanger circuit is further cooled. This is favorable for the heat pump operation, because it supports the liquefaction of the refrigerant.
  • the second heat exchanger is arranged in the case of overheating of the refrigerant upstream of the heat exchanger provided for heating in the refrigerant flow direction.
  • the second heat exchanger is charged with outside air, while the actually intended for overheating heat exchanger is supplied with exhaust air.
  • the temperature of the exhaust air is greater than that of the outside air. Due to the higher humidity of the exhaust air in comparison to the outside air, the energy content of the exhaust air in connection with its higher temperature is also greater than that of the outside air.
  • a very compact design of the heat exchanger for overheating or re-evaporation of the refrigerant is possible because of the comparatively smaller volume flow of exhaust air and because of the high available external pressure of mechanical ventilation systems.
  • a mechanical ventilation system is coupled to the exhaust air inlet of a heat exchanger.
  • the use of a mechanical ventilation system in combination with an exhaust air heat pump is particularly suitable for the highly thermally insulated and virtually airtight new buildings required by the Energy Saving Ordinance EnEV with a required building density of 0.2 times the free air exchange through building leakages.
  • an approximately 0.5-fold air change is required, ie a 0.5-fold replacement of the volume of air contained in the rooms per hour, as he also according to DIN 1946 for housing. required.
  • the currently still common window ventilation in new buildings according to the defined by the EnEV low energy house standard is unsuitable.
  • One of the main disadvantages of window ventilation is that the air exchange varies considerably depending on the wind force and is difficult to estimate in terms of size, and the direction of flow within the dwelling is often unfavorable.
  • the theoretically sensible air vent is not at least at night ⁇
  • a mechanical ventilation system will be provided in corresponding new buildings, can be adjusted by the advantageous manner required here air exchange reliably and safely, with an efficient cross ventilation while preventing the ingress of dust, pollen and insects in the apartment appropriate filtering can be guaranteed.
  • a mechanical ventilation system significantly improves sound insulation of the apartment from the outside world.
  • R744 or CO2 forms the refrigerant.
  • CO2 is characterized by its good availability at comparatively lower prices and its environmental compatibility.
  • the disadvantage of using carbon dioxide as a refrigerant is that carbon dioxide does not show any clear phase transitions. Therefore, it is particularly advantageous when using carbon dioxide as a refrigerant to lead the heat pump process according to the invention clearly in a supercritical range. Accordingly, in the case of a supercritical process control of the refrigerant in the high-pressure region, the heat exchanger provided is designed for evaporation and partial overheating of the refrigerant. In this case, the second heat exchanger is preferably designed for evaporation and reliable overheating of the refrigerant.
  • the refrigerant is exposed between a gas cooling and a heat absorption of a pressure difference between about 40 and about 90 bar.
  • the enthalpy is reduced by about 150 to about 300 kJ / kg and in a second, the first subsequent, gas cooling (3a-3b), the enthalpy falls by less than about 100 kJ / kg, and / or at a pressure between about 20 and about 60 bar at a first heat absorption (5a-5b) increases the enthalpy by about 150 to about 250 kJ / kg and in a subsequent second heat absorption (6a -6b), the enthalpy of the refrigerant increases by less than about 100 kJ / kg.
  • a further advantage is that the first Enthalpieslessnesslessness für enthalpieslessness für apsis (5a-5b) from the outside air and the second Enthalpieslessness für apy) of an exhaust air of a room that has a higher temperature than the outside air and / or that the first falling the enthalpy takes place by heat (2a-2b) of heat to a heating, hot water or ventilation system and the second falling of the enthalpy takes place by heat release (3a-3b) to an outside air flow.
  • the refrigerant is compressed in an advantageous process or process by means of a compressor to a pressure of about 90 - 100 bar, at a temperature of about 80 0 C. From this state, a heat release, wherein the enthalpy of the refrigerant from about 470 kJ / kg falls to about 250 kJ / kg, which isobaric at a pressure of about 95 bar. In a second heat release process, a further decrease in enthalpy from about 250 kJ / kg to 200 kJ / kg occurs at the same pressure. The refrigerant is then expanded to a pressure of about 35 bar, at least as relaxed that the refrigerant is held in the wet steam area.
  • This is followed by another isobaric absorption of energy at the same pressure, at which the refrigerant assumes an enthalpy corresponding to a value outside the wet steam area, in particular an enthalpy of about 440 kJ / kg.
  • the enthalpy may also be slightly smaller, eg approx. 420 kJ / kg at 50 bar, depending on the pressure at which the heat is absorbed. From this state, an increase in pressure takes place again in the compressor to about 95 bar and a temperature of about 80 0 C 1 which corresponds to an enthalpy in the range of 470 kJ / kg and thus the refrigerant process is closed.
  • FIG. 1 shows a perspective view of an opened heat exchanger
  • FIG. 2 shows a side view of the heat exchanger of FIG. 1 in a cutout
  • FIG. 3 shows a sketched sectional view through a heat exchanger according to one of the preceding figures
  • FIG. 4 is a schematic diagram of an embodiment of the invention
  • FIG. 5 a pressure line associated with the heat pump circuit of FIG. 4;
  • Figure 6 is a schematic diagram of an embodiment of the invention.
  • FIG. 7 shows a pressure-enthalpy diagram associated with the heat pump circuit according to FIG. 6;
  • Figure 8 is a schematic diagram of an embodiment of the invention.
  • Figure 9 a pressure-enthalpy diagram associated with the heat pump cycle of FIG. ⁇ .
  • FIG. 1 shows a perspective view of an opened heat exchanger 1 according to the present invention, wherein a fluid-tight outer housing 2 in the region of a narrow side 3 and a broad side surface 4 is opened.
  • a fluid-tight outer housing 2 in the region of a narrow side 3 and a broad side surface 4 is opened.
  • layers 5, 6, 7, 8 arranged one above the other are visible.
  • the heart of each of the layers 5, 6, 7, 8 is a wave-shaped sheet 9 of copper with a periodic sequence of wave troughs 10 and wave crests 11, which are point symmetrical to each other.
  • a substantially flat sheet 12 is arranged, which has the same outer dimensions as the sheet 9 and closes the space under the crests 11 of the sheet 9 such that a closed Fluidka- channel 13 is formed , While the wide side surface 4 of the fluid-tight outer housing 2 covered in the representation of FIG. 1 covers the sheet 9 of the layer 5, the sheets 12 of each layer 5, 6, 7, 8 likewise cover the corrugated sheets 9 of the respectively underlying layer in the same way 6, 7, 8. Thus, now all rooms of wave troughs 10 of the corrugated sheets 9 of the layers 5, 6, 7, 8 are closed so that they form fluid channels 14.
  • tubes 15, which are to be flowed through by corrugations, are inserted into the wave troughs 10 of the corrugated sheets 9.
  • a real countercurrent heat exchanger is advantageously realized.
  • a fluid channel 14 is thermally in contact with the refrigerant of the tubes 15, depending on the view in countercurrent or direct current across the respective sheet 9.
  • the tubes are formed as a one-piece, meandering coolant coil 18.
  • FIG. 2 shows a section x of the heat exchanger 1 of FIG. 1 in an enlarged side view.
  • the layer 5 has a reduced height compared to the layers 6, 7, 8 with the period length of the wave structure of the sheet 9 remaining the same.
  • the dimensioning and shaping of the coolant coil 18 remains unaffected by these changes, so that in each of the layers 5, 6, 7, 8 relative to adjacent layers, in pairs or even completely the same coolant coils 18 can be used.
  • the ratio of the cross-sectional areas F1 of the fluid channels 13, the cross-sectional areas F3 of the fluid channels 14 and the cross-sectional area F2 of the tube 15 is shown in the figure of Figure 3 with reference to a sketched sectional view through a heat exchanger 1 according to one of the preceding figures.
  • the ratio of the cross-sectional areas F1: F2 is significantly greater than 1: 5.
  • the cross-sectional area F1 forms approximately a triangular area with a point angle ⁇ of less than 90 °.
  • the surfaces F1 and F3 are the same size.
  • the ratio between the areas F1 and F3 can be freely set in a wide range. This freedom may be necessary to avoid, for example, differences in the flow amount of the fluid channels 13, 14 and / or differences in the heat transfer of the fluid channels 13, 14 compensate or deviate in terms of optimizing the heat exchanger performance.
  • Vorrich- device 1 A significant manufacturing advantage of a Vorrich- device 1 according to the invention is also indicated in the sketch of Figure 3:
  • the tubes 15 of a coolant coil 18 form together with the wave-shaped sheet 9 and the sheet 12 disposed thereunder a layer 5, 6, 7, 8.
  • layers 5, 6, 7, 8 can be stacked almost arbitrarily one above the other, so that a heat exchanger constructed in this way is very well scalable.
  • the structure described above also allows a very efficient method for at least partially sealingly connecting the elements of a layer to the corrugated sheet 9 of an underlying layer.
  • recesses 20 are provided in the here V-shaped plate 9 in the area where it is in superficial contact with the tube 15, and in the support plate 12 in the region in which it with the V-shaped plate 9 and i.d.R. with a V-shaped sheet 9 of a subsequent layer is in surface contact.
  • the recesses 20 are formed as slots 21 or holes 22 with dimensions which are substantially closed in the course of the common soldering.
  • slots 21 are provided in the metal sheets 12 and perforations 22 in the form of a perforation in the V-shaped wave plates 9.
  • this soldering process during stacking of the aforementioned elements is prepared by placing solder 23 of predetermined quantity in the form of a rod in the region of the tubes 15.
  • solder 23 is then liquefied so far that it connects all the elements in the dashed bordered area with each other.
  • a secure and fluid-tight connection of the elements involved over all layers 5, 6, 7, 8 is produced in the contact area bordered by dashed lines in FIG.
  • the method described above requires a certain dimensional accuracy, especially in the case of the present example V-shaped plate 9.
  • the V-shaped plate 9 is produced with periodic continuation perpendicular to a later flow direction by section-wise pressing and / or deep drawing of a previously substantially flat sheet.
  • a section-wise progression of pressing and / or deep-drawing operations a sheet can be fixed or held in an already completed area, wherein deformation and flow processes are not hindered in a straight worked area.
  • good results are achieved in terms of dimensional accuracy, at the same time a rupture of the sheet can be largely excluded.
  • the recesses 22 described above in connection with a final soldering of the individual parts in the V-shaped sheet metal 9 would be disturbing in the just described process of material deformation as crack germs. Therefore, the recesses 22 are preferably made on V-shaped sheets 9 by punching, drilling and / or laser after the material deformation described.
  • the recesses 22 on the i.d.R. level support plate 12 preferably prepared by the same process.
  • FIG. 4 is a schematic diagram of an embodiment of the invention is shown, wherein a dashed line enclosed ventilation system A is coupled together with a solar heating circuit B to a heating and / or service water system C.
  • the ventilation system A has a heat exchanger WT, the air-to-air cross-flow heat exchanger or air-to-air countercurrent heat exchanger 1 f
  • a exhaust air flow AB can be passed from rooms to be heated to the exhaust air inlet of the first heat exchanger WT via a mechanical ventilation system not shown in the drawing. After the transfer of heat energy to a supply air to ZU the exhaust air flow AB is forwarded as exhaust air FO.
  • the sensible heat contained in the exhaust air flow FO is used in a heat pump circuit WPK.
  • this heat pump cycle WPK comprises a compressor 31 for compressing a gaseous refrigerant, a first heat exchanger 32 and a second heat exchanger 33, both of which serve as a gas cooler for the compressed refrigerant and thus for its liquefaction.
  • the liquid refrigerant passes through a controllable expansion valve 34 to an evaporator 35. Behind the evaporator 35, the heat pump circuit WPK closes, wherein the exhaust air flow FO is then finally discharged to the environment after passing through the evaporator 35.
  • the heat exchanger 32 may be used in an advantageous manner as a radiator for the heating of supply air, wherein it is in the supply air or outside air flow.
  • the evaporator 35 thus serves the substantial removal of the still contained in the exhaust air flow FO sensitive heat. It is dimensioned so that the refrigerant is operated at least on entry into the downstream compressor 31 in a supercritical region.
  • the refrigerant is operated in a high pressure region (WPKH) of the heat pump cycle (WPK) between the compressor 31 and the expansion valve 34 in a supercritical state.
  • WPKH high pressure region
  • WPK heat pump cycle
  • the heat absorbed by the exhaust air flow FO in the evaporator 35 is then released again in two stages via the first heat exchanger 32 and a second heat exchanger 33.
  • the heat exchanger 32 as the first condenser downstream of the second heat exchanger 33 in the flow direction of the refrigerant of the heat pump circuit WPK, which in this example case is designed as a fin tube heat exchanger.
  • This second heat exchanger 33 is flowed through on the one hand by the refrigerant of the heat pump circuit WPK and on the other hand by the outside air flow AU, before the outside air flow AU for further heating in the first heat exchanger WT occurs.
  • the liquefied refrigerant has at an output 32b of the condenser 32, a temperature in the order of, for example, 30 0 C. It has been found that at low ambient temperatures, ie low temperatures of the outside air flow AU, in particular below 0 0 C, there is a risk that the First heat exchanger WT frosts or ices and thus largely loses its effect.
  • the second heat exchanger 33 is connected upstream of the outside air inlet of the designed as an air-to-air heat exchanger first heat exchanger WT, wherein the supercritical in the high pressure area (WPKH) refrigerant in the first heat exchanger 32 a larger part Q of the heat to a first heat sink, the heating and / or service water system C, transmits and another heat exchanger 33 transmits a smaller portion q of the heat of the refrigerant at a low temperature level to an outside air flow AU as a second heat sink, so that the freezing of the subsequently traversed by the outside air Air heat exchanger WT is prevented.
  • WPKH high pressure area
  • the outside air flow AU is preheated, which counteracts a tire and / or icing of the first heat exchanger 1.
  • the refrigerant of the heat pump circuit (WPK) located in the high-pressure region of the (WPKH) is cooled even further. This is favorable for the heat pump operation because the heating power is increased without increasing the electrical power consumption in the compressor 1.
  • the solar heat cycle B comprises a solar collector S, a pump P and a heat exchanger WTS, which is adapted by its dimensions to the heat quantities occurring in a solar circuit.
  • the so-called solar heat exchanger WTS transfers heat obtained in the solar collector S into the heating and / or service water installation C, which in addition to an electrical rule after reheating N also includes the heat exchanger 32 of the heat pump circuit WPK the ventilation system A as a heat source.
  • further heat exchangers can be provided here in the heating circuit of the heating and / or service water installation C.
  • the heat fed to the illustrated three heat exchangers WTS, 32, N heat can now be divided either via pumps and controllable valves on a heating circuit HK and a hot water circuit with a hot water tank WB.
  • the heating circuit HK supplies radiators and / or underfloor heating systems with heating water.
  • the introduced via a heat exchanger in the hot water tank WB heat can be stored and used not shown on the additional heat exchanger as needed for heating or at least for the preheating of drinking water.
  • Drinking water can also be kept at a pre-set temperature by means of a circulating system for hot water.
  • a waste heat recovery from wastewater not shown in FIG. 4 can also be operated additionally or alternatively with preheating of fresh water.
  • FIG. 5 shows a pressure-enthalpy diagram associated with the heat pump circuit of FIG. 1 for carbon dioxide CO2 or R744 as refrigerant.
  • Compressor 31, first heat exchanger 32, second heat exchanger 33, controllable expansion valve 34 and heat exchanger 36 are characterized as elements of the heat pump circuit WPK by their respective inputs a and outputs b in the circuit within the p-h diagram. It can be clearly seen in the p-h diagram that the working point in the transition from the outlet 36b of the evaporator 35 to the inlet 31a of the compressor 31 is clearly beyond the dew line.
  • FIG. 6 shows a schematic representation of a second embodiment of the invention. Accordingly, heat sources of different eigen- economically optimally used by two heat exchangers each adapted to heat exchangers are used as evaporators for heat absorption.
  • the evaporator 36 charged with exhaust air FO is preceded by an evaporator 35.
  • the evaporator 35 uses a cold temperature level for additional absorption of heat, for which purpose it is acted upon as heat exchanger with outside air AU.
  • the embodiment according to the present invention therefore includes a heat pump cycle in conjunction with a ventilation unit, where the refrigerant after the heat exchanger 35 in a further heat exchanger 36 is overheated or post-evaporated against the exhaust air of the ventilation unit.
  • the temperature of the exhaust air FO is greater than that of the outside air AU. Due to the higher humidity of the exhaust air FO in comparison to the outside air AU, the energy content of the exhaust air FO, in conjunction with its higher temperature, is greater than the energy content of the outside air AU.
  • a very compact design of the heat exchanger 36 for overheating or re-evaporation of the refrigerant is possible.
  • a further heat exchanger 36 is arranged as a superheater, in which the refrigerant CO 2 is overheated or post-evaporated. Overheating or re-evaporation takes place against the exhaust air FO of the first heat exchanger WT, in which the supply air ZU of a building is heated against the exhaust air AB.
  • the second heat exchanger 36 is designed for evaporation and superheating of the refrigerant, and reliable after-evaporation or overheating is ensured with a heat source which always has a higher temperature level than the heat source of the primary evaporator 35 ,
  • the refrigerant can now be partially evaporated in the second heat exchanger 36 as a superheater and safely overheated, but it can also be vaporized in the first heat exchanger 35 as an evaporator and partially overheated.
  • FIG. 4 shows a pressure-enthalpy diagram associated with the heat pump circuit according to FIG.
  • thermodynamic efficiency of the cycle of the CO 2 heat pump or the heat pump circuit WPK was in the embodiment of the heat exchanger 32 as a gas cooler 31 of the heat pump, in which the heating water is heated, inter alia, in the heating and service water C, a second heat exchanger 33rd connected as additional gas cooler. This serves to transfer the remaining heat of the supercritical CO2 refrigerant to the outside air AU.
  • the additional gas cooler 33 causes not only a significant reduction in the gas cooler outlet temperature of the refrigerant but also a preheating of the outside air AU, so that these temperatures of 0 0 C or more reached, so that a freezing of the cross-countercurrent heat exchanger is avoided.
  • this leads to a significant increase in the coefficient of performance, because the usable heat or cooling capacity increases without additional compressor power having to be used.
  • a CO2 heat pump process of -10 0 C evaporating temperature and gas cooler pressure of 80 bar can so the heat output number of 2.7 at a gas Cooling outlet temperature of 3O 0 C to 3.2 at a gas cooler outlet temperature of 20 0 C can be improved.
  • this first-described device can be well combined with a refrigerant after evaporation by means of exhaust air FO according to an embodiment of the invention.
  • a combination of ventilation unit and heat pump is provided.
  • the heat of the second gas cooler is transmitted at low temperature level to the outside air sucked by the ventilation unit and thus increases the coefficient of performance of the heat pump cycle;
  • the remaining energy of the exhaust air of the ventilation unit is used to ensure safe re-evaporation of the refrigerant coming from the suction side collector and thus to allow a control technically stable refrigerant circuit and a long compressor life.
  • Figure 9 shows a pressure-enthalpy diagram associated with the heat pump cycle of Figure 8.
  • the characteristics described above for the first two embodiments have been exactly adopted.
  • the heat exchanger shown in FIGS. 1 to 3 can be used, for example, as a heat exchanger 32 according to FIGS. 4, 6 or 8.
  • the embodiments according to FIGS. 4 to 9 represent a possible use of the heat exchanger according to FIGS. 1 to 3. LIST OF REFERENCES
  • Gas cooler / heat exchanger 33a Input of the gas cooler 33b Output of the gas cooler

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

La présente invention concerne un agent caloporteur doté d'un système de conduits destiné à un agent réfrigérant et d'un système de conduits destiné à un fluide, ces systèmes étant thermiquement couplés aux fins de transmission de l'énergie thermique d'un agent à l'autre agent. A cet effet, l'agent caloporteur présente une pluralité de sections partielles hydrauliquement raccordées respectivement en parallèle et/ou en série. L'invention vise à créer un agent caloporteur du type susmentionné ayant un transfert de chaleur amélioré dans une construction compacte et un procédé de production rationnel d'un tel agent caloporteur. A cet effet, dans cette section partielle, respectivement un canal de fluide comprend une tôle qui a un profil en travers approximativement en U, en V ou en W et qui est fermée par une tôle aux extrémités du U, du V ou du W. L'agent réfrigérant est placé dans le canal de fluide dans un tube parallèle à l'axe longitudinal du canal de fluide.
EP05820443A 2004-12-22 2005-12-22 Agent caloporteur et circuit de thermopompe Withdrawn EP1831631A2 (fr)

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EP12160171.0A EP2469208A3 (fr) 2004-12-22 2005-12-22 Caloporteur et circuit de pompe à chaleur

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DE200410061673 DE102004061673A1 (de) 2004-12-22 2004-12-22 Wärmeübertrager
DE102005002282.0A DE102005002282B4 (de) 2005-01-18 2005-01-18 Wärmepumpenkreis einer Lüftungsanlage
PCT/EP2005/013950 WO2006066953A2 (fr) 2004-12-22 2005-12-22 Agent caloporteur et circuit de thermopompe

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FR3005154B1 (fr) * 2013-04-26 2015-05-15 Commissariat Energie Atomique Four a chauffage par induction electromagnetique, utilisation du four pour la fusion d'un melange de metal(ux) et d'oxyde(s) representatif d'un corium
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CN107180450B (zh) * 2017-06-06 2020-09-18 南宁师范大学 一种基于dem的河谷横断面形态的算法
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EP2469208A3 (fr) 2014-08-27
WO2006066953A3 (fr) 2006-12-07
JP4808732B2 (ja) 2011-11-02
JP2008524550A (ja) 2008-07-10
EP2469208A2 (fr) 2012-06-27

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