EP2052200B1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP2052200B1
EP2052200B1 EP06794262A EP06794262A EP2052200B1 EP 2052200 B1 EP2052200 B1 EP 2052200B1 EP 06794262 A EP06794262 A EP 06794262A EP 06794262 A EP06794262 A EP 06794262A EP 2052200 B1 EP2052200 B1 EP 2052200B1
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EP
European Patent Office
Prior art keywords
heat exchanger
heat exchange
coolant
exchanger according
liquid
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EP06794262A
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English (en)
French (fr)
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EP2052200A1 (de
Inventor
Pierre Bignon
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Individual
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Individual
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Classifications

    • 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
    • F28D7/10—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 being arranged one within the other, e.g. concentrically
    • F28D7/103—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 being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/24—Pumping by heat expansion of pumped fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08—Fluid driving means, e.g. pumps, fans

Definitions

  • the present invention relates to a heat exchanger used to generate a liquid under pressure under the effect of its expansion, in particular in a pump.
  • the hydraulic system thus comprises a hydraulic pump, a hydraulic fluid reservoir and a hydraulic motor.
  • the hydraulic pump comprises at least one pumping piston and a driving piston constituted by two stages of the same differential piston.
  • the pumping piston defines a pumping chamber in a pumping cylinder and the driving piston defines a driving chamber in a driving cylinder.
  • the pumping piston and the driving piston are interconnected by kinematic connecting means so that an increase in the volume of the driving chamber corresponds to a reduction in volume of the pumping chamber and vice versa.
  • the pumping chamber is hydraulically connected to the hydraulic fluid reservoir of the plant and the hydraulic motor of the plant, which is fed by the hydraulic pump.
  • the driving chamber of the pump is hydraulically connected to a tubular heat exchange bundle.
  • a high coefficient of thermal expansion fluid is present in the drive chamber and the heat exchange tubular bundle. This liquid with a high coefficient of thermal expansion is placed in heat exchange relation alternately with a hot source and with a cold source.
  • the liquid with a high coefficient of thermal expansion alternately undergoes thermal expansion and thermal contraction, which respectively causes the volume of the drive chamber to increase to the detriment of that of the pumping chamber, which forces the hydraulic fluid towards the hydraulic motor then to the tank of the installation, or the reduction of the volume of the drive chamber, which causes the aspiration of the hydraulic fluid from the tank of the installation.
  • a pumping effect is then obtained by alternating the discharge and suction movements of the hydraulic fluid.
  • the tubular heat exchange bundle consists of a bundle of vertical tubes closed at their lower end and communicating with each other at their upper end by a manifold into which a connecting pipe with the driving chamber opens.
  • the tubular heat exchange bundle is placed inside a tray divided by a horizontal partition.
  • This partition thermally insulating, is pierced by holes allowing each tube to cross the partition from side to side while ensuring a seal as good as possible between the partition and the tubes.
  • the tank is thus divided into a lower chamber comprising a circulating cold heat transfer fluid and an upper chamber comprising a circulating hot heat transfer liquid.
  • the tubular heat exchange bundle is thus alternately put in heat exchange relation with the cold heat transfer fluid and with the hot heat transfer fluid by vertical displacement back and forth inside the tank. This vertical back and forth movement is provided by a jack.
  • the object of the invention is therefore to provide a heat exchanger for long withstanding strong mechanical stresses.
  • the liquid has a high coefficient of thermal expansion.
  • the outer tube or half-tube, the heat exchange plate (s) and the support cylinder or half-cylinder have decreasing diameters.
  • the first and second cavities are delimited, on the one hand, by one of the heat exchange plates and, on the other hand, by the support cylinder or half-cylinder or the tube or half-tube of external holding, the heat exchange plate (s), the support cylinder or half-cylinder and the external holding tube or half-tube being concentric.
  • each tubular element is closed at each of its ends by a flange, one of said flanges being adapted to allow the circulation of the liquid through the flange and the other flange prohibiting this circulation.
  • each tubular element is closed at each of its ends by a flange, at least one of said flanges being adapted to allow the circulation of (the) heat transfer fluid (s) through the flange.
  • said flanges are adapted to allow the alternating circulation of a heat transfer fluid heated by a hot source and a heat transfer fluid cooled by a cold source.
  • one of the heat exchange plates is provided with a plurality of first fins in contact with the liquid.
  • one of the heat exchange plates is provided with a plurality of first fins in contact with a coolant.
  • one of the heat exchange plates is provided with a plurality of second fins in contact with a coolant.
  • the various tubular elements are parallel to each other.
  • the various tubular elements are held together by means of flanges each enclosing a tubular element and fixed to a threaded rod located between at least two tubular elements.
  • the various tubular elements are held together by means of flanges each enclosing a tubular element and welded together.
  • the various tubular elements are held together by means of flanges each enclosing a tubular element and brazed together.
  • each tubular element or core further comprises heat transfer fluid pipes, as well as spray nozzles adapted to spray the heat transfer fluid from the heat transfer fluid pipes to the heat exchange plate.
  • the pump further comprises a bypass adapted to alternately pass a heat transfer fluid heated under pressure by the hot source and a coolant cooled at atmospheric pressure by the cold source in the tubular elements or cores of the heat exchanger.
  • the heat exchanger comprises a plurality of tubular elements.
  • Each tubular element comprises a support cylinder, at least one curved heat exchange plate separating a first cavity from a second cavity, and an external holding tube.
  • the first cavity contains a liquid and the second cavity receives a heat transfer fluid causing the expansion or thermal contraction of the plate, and thus the compression or the depression of the liquid of the first cavity.
  • the heat exchange plate expands or contracts by contact with the coolant as a function of the temperature of the heat transfer fluid (s) circulating in the heat exchanger, resulting in compression or depression of the heat transfer fluid. first cavity and therefore the liquid contained in this first cavity.
  • the support cylinder and the external retaining tube which are made of materials that are very resistant to pressure and can be poor thermal conductors, can greatly limit the longitudinal expansion of the heat exchanger and thus resist longer to high stresses. mechanical with the heat exchange tubular bundle known in the prior art.
  • the figure 1 represents a perspective view of a tubular element of the heat exchanger according to a first embodiment of the invention.
  • the heat exchanger comprises a plurality of tubular elements.
  • each tubular element 1 comprises a tube 6 containing two outer retaining plates 3 c, 3 f heat exchange, respectively called outer plate and inner plate, which, themselves, contain a support cylinder 2.
  • the plates 3c , 3f of heat exchange are cylindrical.
  • the support cylinder 2 is for example a solid cylinder.
  • the tube 6 of outer retaining the two plates 3 c, 3 f heat exchange and the supporting cylinder 2 are substantially concentric.
  • a first cavity, formed between the two plates 3c , 3f of heat exchange, contains a liquid 4.
  • the liquid 4 has a high coefficient of thermal expansion.
  • the heat exchange plates allow a heat exchange between the coolant and the liquid 4.
  • the liquid 4 expands or contracts depending on the temperature of the coolant (s) circulating in the heat exchanger thermal, which causes the thermal expansion or contraction of the liquid 4.
  • the compression or the depression created is then even greater in the case where the liquid is not at high coefficient of thermal expansion and where the compression or the depression of the liquid 4 is only due to the thermal expansion or contraction of the heat exchange plates.
  • Two other cavities formed respectively between one of the plates 3 c and the tube 6 and outer retaining between the other plate 3f and the supporting cylinder 2, host fluid 5 c hot heat transfer fluid and a heat transfer respectively 5 f cold in the liquid state.
  • One of the aims of the heat exchanger according to the invention is to compress or depressurize the liquid 4 by heat exchange of the plates with the fluids 5c , 5 f heat transfer, the liquid however must constantly remain in the liquid state. So that this heat exchange is optimized, especially in time, these plates 3c , 3f are made of material having a very good thermal conductivity, namely metal. This also allows a good heat exchange with the liquid 4, which is important especially when the liquid 4 is high coefficient of thermal expansion.
  • the outer support tube 6 and the support cylinder 2 consist of materials that are very resistant to pressure.
  • they are for example, but not limited to, carbon composite material, filament windings or glass.
  • the materials have the advantage of having a poor thermal conductivity (for example between 0.034 W / mK and 0.045 W / mK), which also makes it possible to greatly limit the heat losses towards the outside of the heat exchanger.
  • the heat losses can be limited by the use of a liquid having a poor thermal conductivity.
  • This plate is thin: it is typically between a few tenths of a millimeter and several millimeters, depending on the nature of the metal constituting the plate and the size of the exchanger depending on the application.
  • the heat exchange rate is increased without weakening the plate because the pressure is exerted mainly radially on it during the expansion (and preferably towards the inside of the tubular element) and not mainly longitudinally as in the prior art.
  • the heat exchanger according to the invention makes it possible to use heat exchange plates of larger diameter for the same thickness, which are much more resistant to strong pressures, which allows to diversify the applications.
  • the diameter of the plates can be increased to a constant thickness either because the pressure is exerted from the outside towards the inside and not from the inside to the outside, or because the plates are helped to resist in their mechanical stresses.
  • the outer support tube 6 or the support cylinder 2 which are made of material resistant to high pressures. If the outer support tube 6 or the support cylinder 2 are metallic, it is necessary to protect them from heat to prevent their expansion, which would reduce the efficiency of the system. It may be envisaged to cool the outside of the holding tube by the fluid 5 f .
  • the outer support tube 6 and the support cylinder 2 are both made of metal, but the tubular element comprises at each of its ends a welded or brazed flange on the tube to allow these two elements 2 , 6 to withstand strong pressures.
  • the fluid 5 c hot coolant is contained between the tube 6 and the outer retaining plate 3c external heat exchange, while the cold heat transfer fluid 5 f is contained between the plate 3 f internal heat exchange and the support cylinder 2.
  • the plate 3 f internal heat exchanger further comprises a plurality of first longitudinal ribs 31 located within the cavity containing the fluid 5 f cold coolant. These first fins 31 make it possible to resist more easily the radial pressure loads exerted on the tubular element under the effect of the expansion of the plate 3 c external heat exchange. These first fins are also used for positioning the support cylinder 2 substantially in the center of the internal plate 3 f .
  • the plate 3 c external heat exchanger also includes a plurality of second longitudinal ribs 32 located within the cavity containing the fluid 5 c hot coolant. These second fins 32 serve in particular to the positioning of the outer plate 3 c substantially in the center of the holding tube 6.
  • the plate 3c has for example a thickness of 3mm and the plate 3f of 1mm.
  • the plate 3c can then contain a pressure of 400 bar by means of the tube 6 of external support.
  • the plate 3 f can contain the same pressure as the plate 3 c despite its lower thickness because the pressure is exerted from the outside to the inside.
  • the plate 3 f cylindrical heat exchange is alternately in contact with the cold coolant 5 f from the cold air source and the fluid when the flow of cold coolant 5 f is stopped.
  • the figure 2 represents a cross-sectional view of the heat exchanger, according to a second embodiment of the invention.
  • the heat exchanger comprises a plurality of tubular elements 1.
  • Each tubular element 1 comprises an external holding tube 6 containing a single heat exchange plate 3 which, itself, contains a cylinder 2 of support.
  • the heat exchange plate 3 is, in a nonlimiting manner, cylindrical.
  • the support cylinder 2 is for example a solid cylinder.
  • the outer support tube 6, the heat exchange plate 3 and the support cylinder 2 are substantially concentric.
  • a first cavity is formed between the heat exchange plate 3 and the external holding tube 6 and a second cavity is formed between the heat exchange plate 3 and the support cylinder 2.
  • One of these cavities accommodates a liquid 4 while the other cavity accommodates a coolant 5.
  • the liquid 4 has for example a high coefficient of thermal expansion. It then allows a higher compression of the liquid with respect to the expansion only of the heat exchange plate, as explained above.
  • the heat exchange plate 3 is made of a material having a very good thermal conductivity, namely of metal so as to optimize the heat exchange.
  • the outer support tube 6 and the support cylinder 2 are made of materials resistant to high pressures and having a poor thermal conductivity such as, for example, a composite material made of carbon or with filament windings or glass.
  • coolant heat and cold fluid is injected alternately into the cavity for receiving said fluid.
  • the liquid 4 is contained between the outer holding tube 6 and the heat exchange plate 3, while the coolant 5 is contained between the heat exchange plate 3 and the support cylinder 2.
  • the heat exchange plate 3 further comprises a plurality of longitudinal first fins 31 located inside the cavity containing the liquid 4. These first fins 31 make it possible to increase the heat exchange surface.
  • the heat exchange plate 3 also comprises a plurality of second longitudinal fins 32 located inside the cavity containing the coolant 5. These second fins 32 serve, on the one hand, to position the support cylinder 2 substantially in the center of the plate 3 and, on the other hand, to withstand more easily large deformations that could result from pressure stresses exerted transversely to the pressure. tubular element under the effect of the expansion of the plate 3.
  • the tubular elements are substantially parallel to each other, and preferably vertical. They are preferably arranged in contact with each other, so as to limit energy losses, and for example so that their axes form trihedrons.
  • This arrangement of the tubular elements, as well as and their method of attachment described below, can also be applied to the tubular elements 1 according to the first and third embodiments of the invention.
  • Each tubular element 1 is enclosed by a flange, not shown, which is fixed to a threaded rod 7 located in the center of the trihedron.
  • the flanges are welded or brazed together.
  • each tubular element 1 is closed at each of its ends by a flange, not shown. Only one of said flanges must allow to circulate the liquid 4 through said flange. In particular, the flanges adapted to circulate the liquid 4 must all be arranged on the same side of the various tubular elements constituting the heat exchanger.
  • the figure 3 is a longitudinal sectional view of the heat exchanger according to a third embodiment of the invention.
  • the heat exchanger comprises a plurality of tubular elements 1.
  • Each tubular element 1 comprises an external holding tube 6 containing a single heat exchange plate 3 which, itself, contains a cylinder 2 of support.
  • the heat exchange plate 3 is vertical and, in a nonlimiting manner, cylindrical.
  • the support cylinder 2 is for example a solid cylinder.
  • the outer support tube 6, the heat exchange plate 3 and the support cylinder 2 are substantially concentric.
  • a first cavity is formed between the heat exchange plate 3 and the external holding tube 6 and a second cavity is formed between the heat exchange plate 3 and the support cylinder 2.
  • One of these cavities accommodates a liquid 4 while the other cavity accommodates a coolant 5.
  • the liquid 4 has for example a high coefficient of thermal expansion. It then allows a higher compression of the liquid with respect to the expansion only of the heat exchange plate, as explained above.
  • the heat exchange plate 3 is made of a material having a very good thermal conductivity, namely of metal so as to optimize the heat exchange.
  • the liquid 4 is contained between the outer holding tube 6 and the heat exchange plate 3, while the coolant 5 is received between the heat exchange plate 3 and the support cylinder 2.
  • the heat exchanger further comprises between the support cylinder 2 and the cavity containing the coolant 5 two pipes 8, 9 bringing the fluid coolant hot or cold from the hot or cold source in the heat exchanger.
  • These pipes are thermally insulated from one another by a first separator 10 and are thermally insulated from the cavity containing the coolant by a second separator 11.
  • the separators are made of material with very low thermal conductivity, to avoid losses of heat.
  • Spray nozzles 12, 13 make it possible to spray the hot or cold heat transfer fluid through capillary channels passing through the separators 10, 11 from the pipes 8, 9 to the cavity initially filled with air and intended to contain the coolant. 5 hot or cold. These capillary channels allow the atmospheric pressure to stop the heat transfer fluids just at the discharge port when the latter are liquid, and to reduce the flow path of the fluids from the control valves to the exchange plate 3 thermal. This spraying is substantially radial and allows rapid and complete spraying of the heat exchange plate 3.
  • the figure 4 represents a cross-sectional view of the heat exchanger according to a fourth embodiment of the invention.
  • the heat exchanger comprises a plurality of cores 101.
  • Each core 101 comprises two elements 107 symmetrical to each other. The two elements 107 are joined to each other in a sealed manner at a junction 100.
  • Each core 101 comprises two half-tubes 106 for maintaining oriented with their concave face towards the outside of the core. The two half-tubes 106 therefore turn their backs.
  • Each retaining tube 106 contains a heat exchange plate 103 which itself contains a support half-cylinder 102. In this embodiment, the heat exchange plate 103 is semi-cylindrical. The heat exchange plate 103 is inserted in abutment against a shoulder 114 in a holding half-tube 106 and held against this shoulder by a holding means 115, for example a weld.
  • a first cavity is formed between the heat exchange plate 103 and the holding half-tube and a second cavity is formed between the heat exchange plate 103 and the support half-cylinder 102.
  • One of these cavities accommodates a liquid 104 while the other cavity accommodates a fluid 105 coolant.
  • the liquid 104 has for example a high coefficient of thermal expansion. It then allows a higher compression of the liquid with respect to the expansion only of the heat exchange plate, as explained above.
  • the heat exchange plate 103 is made of a material having a very good thermal conductivity, namely of metal so as to optimize the heat exchange.
  • the liquid 104 is contained between the holding half-tube and the heat exchange plate 103, while the coolant fluid 105 is sprayed onto the heat exchange plate 103 by a spraying device contained in the half carrier cylinder 102.
  • each support half-cylinder 102 comprises two conduits 108, 109 bringing the hot or cold heat transfer fluid from the hot or cold source into the heat exchanger. These pipes are thermally insulated from one another and are thermally insulated from the cavity receiving the coolant. Spray nozzles 112, 113 make it possible to spray the hot or cold heat transfer fluid from the pipes 108, 109 on the heat exchange plate 103. This spraying is substantially radial and allows a rapid and total spraying of the exchange plate 103. thermal.
  • the perimeter of the heat exchange plate is not circular, or cylindrical. Lobed shapes suggesting those of a mold charlotte or ogival form allow to benefit from an increased length of the perimeter, thus participating in a greater linear expansion of the heat exchange plate, and therefore to its displacement in compression liquid located in the cavity 104.
  • the fluids 5, 5 c . 5 f coolant are for example water and the liquid 4 is for example ethanol.
  • the thermal expansion coefficient of the ethanol is 1.1.10 -3 K -1.
  • the fluid 5 c hot coolant is heated by a cold source and the fluid 5 f cold coolant is cooled by a cold source.
  • the hot source is for example a solar collector.
  • the energy flow produced by the hot source is modest, it is particularly important to minimize the heat losses in order to save the available energy.
  • the heat exchanger according to the invention is intended to be installed in a pump further comprising a pumping piston adapted to actuate a control means by the movement of a fluid (hydraulic liquid or gas), a motor piston connected by means of kinematic means to the pumping piston and adapted to be actuated by a movement of the liquid 4 from the heat exchanger described above, by a hot source and a cold source.
  • a fluid hydroaulic liquid or gas
  • a motor piston connected by means of kinematic means to the pumping piston and adapted to be actuated by a movement of the liquid 4 from the heat exchanger described above, by a hot source and a cold source.
  • the pump contains for example several heat exchangers.
  • the pump to operate also comprises a bypass for alternately passing a hot heat transfer fluid heated by the hot source and a cold heat transfer liquid cooled by the cold source in the tubular elements 1 of the heat exchanger so as to create a alternation of dilations and thermal contractions to actuate the engine piston.
  • the pump according to the invention is intended to be installed in an installation further comprising a control means, for example a motor, and a fluid reservoir.
  • a control means for example a motor, and a fluid reservoir.
  • the installation is for example an air conditioner.
  • the pumping chamber sucks and compresses gas and serves as a compressor.
  • the hot source is for example one or more solar panel (s) or an isothermal pit hot heat transfer fluid storage used during the night.
  • the cold source is for example a pleasure pool or a swimming pool.
  • the installation is a hydraulic plant producing domestic electricity.
  • the control means is a hydraulic motor.
  • the hot source is for example one or more solar collector (s) and / or an isothermal pit for hot heat transfer fluid storage that can be used during the night period.
  • the cold source is for example a pit, an ornamental pond or a swimming pool.
  • the installation is a hydraulic plant producing domestic electricity from geothermal energy.
  • the hydraulic pump operates a hydraulic motor that drives an electricity generator.
  • the hot spring is then constituted by hot water from geothermal energy.
  • the cold source is for example constituted by the natural environment, namely a reservoir of hilly water, a river, the sea, etc ...
  • the pressure in the circuit of the hot heat transfer fluid must be relatively high in order to maintain the fluid (for example water) in the liquid state, a parsie of the pressure generated by the installation is used to reinject the fluid into the solar collector. Otherwise, the water evaporates.
  • the pressure in the cold coolant circuit may be the ambient pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Power Steering Mechanism (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Claims (18)

  1. Wärmetauscher, umfassend eine Vielzahl von rohrförmigen Elementen oder Kernen (1, 101), jeweils umfassend:
    - einen Tragzylinder oder -halbzylinder (2, 102),
    - mindestens eine gekrümmte Wärmeaustauschplatte (3, 3c, 3f, 103), wobei jede Platte einen ersten Hohlraum von einem zweiten Hohlraum trennt, wobei der erste Hohlraum eine Flüssigkeit (4, 104) enthält und der zweite Hohlraum ein Wärmetauscherfluid (5, 5c, 5f, 105) empfängt, das die Wärmeausdehnung oder Wärmekontraktion der Platte, und damit jeweils die Komprimierung bzw. Ausdehnung der Flüssigkeit in dem ersten Hohlraum, verursacht,
    - ein äußeres Halterohr oder -halbrohr (6, 106).
  2. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, dass die Flüssigkeit (4) einen hohen Wärmeausdehnungskoeffizienten aufweist.
  3. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das äußere Halterohr oder -halbrohr (6, 106), die Wärmeaustauschplatte oder -platten (3, 3c, 3f, 103) und der Tragzylinder oder -halbzylinder (2, 102) kleiner werdende Durchmesser aufweisen.
  4. Wärmetauscher nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der erste und der zweite Hohlraum auf einer Seite durch eine der Wärmeaustauschplatten (3, 3c, 3f, 103) und auf der anderen Seite durch den Tragzylinder oder -halbzylinder (2, 102) oder das äußere Halterohr oder -halbrohr (6, 106) begrenzt sind, wobei die Wärmeaustauschplatte(n) (3, 3c, 3f, 103), der Tragzylinder oder -halbzylinder (2, 102) und das äußere Halterohr oder -halbrohr (6, 106) konzentrisch sind.
  5. Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass jedes rohrförmige Element (1) an jedem seiner Enden durch einen Flansch geschlossen ist, wobei einer dieser Flansche geeignet ist, das Zirkulieren der Flüssigkeit (4) durch den Flansch zu ermöglichen und der andere Flansch dieses Zirkulieren verhindert.
  6. Wärmetauscher nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass jedes rohrförmige Element (1) an jedem seiner Enden durch einen Flansch geschlossen ist, wobei mindestens einer dieser Flansche geeignet ist, das Zirkulieren des Wärmetauscherfluids oder der Wärmetauscherfluide (5, 5c, 5f) durch den Flansch zu ermöglichen.
  7. Wärmetauscher nach Anspruch 6, dadurch gekennzeichnet, dass diese Flansche geeignet sind, das abwechselnde Zirkulieren eines Wärmetauscherfluids, das durch eine Wärmequelle erwärmt wird, und eines Wärmetauscherfluids, das durch eine Kältequelle gekühlt wird, zu ermöglichen.
  8. Wärmetauscher nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass eine der Wärmeaustauschplatten (3) mit einer Vielzahl von ersten Lamellen (31) in Kontakt mit der Flüssigkeit (4) ausgestattet ist.
  9. Wärmetauscher nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass eine der Wärmeaustauschplatten (3) mit einer Vielzahl von ersten Lamellen (31) in Kontakt mit einem Wärmetauscherfluid (5f) ausgestattet ist.
  10. Wärmetauscher nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass eine der Wärmeaustauschplatten (3, 3c) mit einer Vielzahl von zweiten Lamellen (32) in Kontakt mit einem Wärmetauscherfluid (5, 5c) ausgestattet ist.
  11. Wärmetauscher nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die verschiedenen rohrförmigen Elemente (1) zueinander parallel sind.
  12. Wärmetauscher nach Anspruch 11, dadurch gekennzeichnet, dass die verschiedenen rohrförmigen Elemente (1) mithilfe von Laschen zusammengehalten werden, die jeweils ein rohrförmiges Element festhalten und an einer Gewindestange (7) befestigt sind, die sich zwischen mindestens zwei rohrförmigen Elementen befindet.
  13. Wärmetauscher nach Anspruch 11, dadurch gekennzeichnet, dass die verschiedenen rohrförmigen Elemente durch Laschen zusammengehalten werden, die jeweils ein rohrförmiges Element festhalten und aneinander geschweißt sind.
  14. Wärmetauscher nach Anspruch 11, dadurch gekennzeichnet, dass die verschiedenen rohrförmigen Elemente (1) durch Laschen zusammengehalten werden, die jeweils ein rohrförmiges Element festhalten und aneinander gelötet sind.
  15. Wärmetauscher nach Anspruch 11, dadurch gekennzeichnet, dass jedes rohrförmige Element oder jeder rohrförmige Kern (1, 101) außerdem Wärmetauscherfluidleitungen (8, 9; 108, 109) und Sprühdüsen (12, 13; 112, 113) umfasst, die zum Sprühen des Wärmetauscherfluids aus den Wärmetauscherfluidleitungen (8, 9; 108, 109) auf die Wärmeaustauschplatte (3, 103) geeignet sind.
  16. Pumpe, umfassend:
    - einen Pumpkolben, der zum Betätigen eines Steuerungsmittels über die Bewegung eines Fluids geeignet ist,
    - einen Antriebskolben, der durch ein kinematisches Mittel mit dem Pumpkolben verbunden und geeignet ist, durch eine Bewegung der Flüssigkeit (4) des Wärmetauschers nach einem der Ansprüche 1 bis 15 betätigt zu werden,
    - eine Wärmequelle,
    - eine Kältequelle.
  17. Pumpe nach Anspruch 16, dadurch gekennzeichnet, dass die Pumpe außerdem einen Bypass umfasst, der zum abwechselnden Zuführen eines Wärmetauscherfluids, das unter Druck durch die Wärmequelle erwärmt wird, und eines Wärmetauscherfluids, das bei Atmosphärendruck durch die Kältequelle abgekühlt wird, in die rohrförmigen Elemente oder Kerne (1) des Wärmetauschers geeignet ist.
  18. System, umfassend:
    - die Pumpe nach einem der beiden Ansprüche 16 und 17,
    - einen Fluidvorratsbehälter,
    - ein Steuerungsmittel.
EP06794262A 2006-08-02 2006-08-02 Wärmetauscher Active EP2052200B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/FR2006/001870 WO2008015314A1 (fr) 2006-08-02 2006-08-02 Echangeur thermique

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EP2052200A1 EP2052200A1 (de) 2009-04-29
EP2052200B1 true EP2052200B1 (de) 2010-02-24

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CN (1) CN101568789B (de)
AT (1) ATE458977T1 (de)
AU (1) AU2006346920A1 (de)
CA (1) CA2659181A1 (de)
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JP5212987B2 (ja) * 2009-03-05 2013-06-19 株式会社Ｌｉｘｉｌ ポンプユニット、ポンプ及びポンプ装置
IE20100266A1 (en) * 2009-04-27 2010-11-10 Kingspan Holdings Irl Ltd A solar collector
JP2012013004A (ja) * 2010-06-30 2012-01-19 Mitsubishi Heavy Ind Ltd 地熱発電システム
US20120199326A1 (en) * 2011-02-03 2012-08-09 Visteon Global Technologies, Inc. Internal heat exchanger
US9260191B2 (en) 2011-08-26 2016-02-16 Hs Marston Aerospace Ltd. Heat exhanger apparatus including heat transfer surfaces
EP3008310B1 (de) * 2013-06-14 2021-08-04 Raytheon Technologies Corporation Gekrümmte platte und rippenwärmetauscher
CN104180117A (zh) * 2014-08-28 2014-12-03 孙金福 液压油管用散热装置
ES2728556T3 (es) * 2016-07-08 2019-10-25 Technip France Intercambiador de calor para enfriar el gas de reacción

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US813918A (en) * 1899-12-29 1906-02-27 Albert Schmitz Tubes, single or compound, with longitudinal ribs.
US872175A (en) * 1906-02-19 1907-11-26 Brewery Equipment & Supply Co Cooling apparatus.
US2703921A (en) * 1949-04-14 1955-03-15 Brown Fintube Co Method of making internally finned tubes
US4096616A (en) * 1976-10-28 1978-06-27 General Electric Company Method of manufacturing a concentric tube heat exchanger
EP0071659B1 (de) * 1981-08-05 1985-08-07 John Ronald Pain Wärmetauscher
DE3742892A1 (de) * 1987-12-17 1989-06-29 Bayerische Motoren Werke Ag Gasturbinenanlage
DE19909368C1 (de) * 1999-03-03 2000-08-10 Hde Metallwerk Gmbh Wärmetauscherrohr
KR20040045407A (ko) * 2001-06-27 2004-06-01 누 엘리먼트 인코포레이티드 모듈러 마이크로 반응기 아키텍쳐 및 유체 처리 장치를위한 방법
US20030044331A1 (en) * 2001-08-31 2003-03-06 Mcdermott Technology, Inc. Annular heat exchanging reactor system
FR2851796B3 (fr) * 2003-02-28 2005-04-22 Pierre Bignon Pompe hydraulique et installation hydraulique comportant une telle pompe.
CN2771785Y (zh) * 2005-02-07 2006-04-12 邹昌校 套管式换热器

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DE602006012560D1 (de) 2010-04-08
WO2008015314A1 (fr) 2008-02-07
US20090139700A1 (en) 2009-06-04
CN101568789B (zh) 2011-07-27
CN101568789A (zh) 2009-10-28
CA2659181A1 (fr) 2008-02-07
AU2006346920A1 (en) 2008-02-07
JP2009545718A (ja) 2009-12-24
ATE458977T1 (de) 2010-03-15
EP2052200A1 (de) 2009-04-29

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