EP2307824A2 - Procédé et dispositif d'évaporation de surface efficace et de condensation efficace - Google Patents

Procédé et dispositif d'évaporation de surface efficace et de condensation efficace

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Publication number
EP2307824A2
EP2307824A2 EP09768974A EP09768974A EP2307824A2 EP 2307824 A2 EP2307824 A2 EP 2307824A2 EP 09768974 A EP09768974 A EP 09768974A EP 09768974 A EP09768974 A EP 09768974A EP 2307824 A2 EP2307824 A2 EP 2307824A2
Authority
EP
European Patent Office
Prior art keywords
condenser
evaporator
working fluid
turbulence
liquid
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.)
Granted
Application number
EP09768974A
Other languages
German (de)
English (en)
Other versions
EP2307824B1 (fr
Inventor
Holger Sedlak
Oliver Kniffler
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.)
Efficient Energy GmbH
Original Assignee
Efficient Energy GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Efficient Energy GmbH filed Critical Efficient Energy GmbH
Publication of EP2307824A2 publication Critical patent/EP2307824A2/fr
Application granted granted Critical
Publication of EP2307824B1 publication Critical patent/EP2307824B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/182—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing especially adapted for evaporator or condenser surfaces
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/04—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases
    • F25B43/043—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases for compression type systems

Definitions

  • the present invention relates to evaporation or condensation on surfaces and in particular to an application of evaporation and condensation to surfaces in heat pumps.
  • a liquid layer such as occurs in an evaporator of a heat pump, due to the typical stratification, which is observed in liquids and in particular water as working fluid, a heat distribution, which consists in that is cooled in the evaporator of the uppermost portion, currency -
  • the lower portion of the layer has almost the same temperature of the working fluid, as it is supplied from a heat source.
  • the object of the present invention is to provide a more efficient concept for surface evaporation or surface condensation. This object is achieved by an evaporator according to claim 1, a condenser according to claim 13, a heat pump according to claim 30, a method for vaporizing according to claim 31 or a method for condensing according to claim 32.
  • the present invention is based on the finding that the evaporation process can be considerably increased by the use of turbulence generators on the evaporator surface, on which a working liquid to be evaporated is to be arranged.
  • the turbulence generators ensure that there is no stratification on the working fluid on the evaporator surface. Instead, the cold liquid layer forming the surface of the working fluid on the evaporating surface is ruptured by the turbulence generators and brought down.
  • the lower, warmer layer of the working liquid is brought upwards, so that it is ensured that there is always working liquid on the surface which has a temperature, in view of the pressure in the evaporator, which is below the atmospheric pressure and preferably even below 50 mbar, evaporation will occur.
  • the pressure is selected so that the liquid of the lower layer, swept up by the turbulence generators, is the boiling temperature of the liquid which, as is known, also decreases with decreasing pressure.
  • the condensation efficiency is increased by also providing turbulence generators on the condenser surface, and these turbulence generators cause stratification of the liquid on the condenser surface to be avoided or constantly disrupted.
  • the upper warm layer which has absorbed heat from the condensation process, is brought down and, at the same time, colder liquid is brought up in the condenser to be warmed up by the condensing vapor.
  • a laminarizer is provided on the condenser side configured to laminarize the vapor stream directed to the working fluid.
  • the present invention relates to an evaporator having an evaporator surface which is provided with turbulence generators, so that a water flow on the evaporator surface has turbulences, which preferably comprise at least 20% of the total water flow.
  • the present invention relates to a condenser in a condenser space, the condenser space having laminarizing means for laminarizing a gas flow directed onto a liquid surface in the condenser, the laminarizer being configured to produce a gas stream at least is as turbulent as a gas stream fed to the laminarizer, the condenser being provided with turbulence generators so that a water stream on the condenser surface has turbulence, preferably comprising at least 20% of the total water flow.
  • the present invention achieves, with the simplest measures, a considerable increase in the evaporation efficiency and the condenser efficiency, which increase can either be used to produce a higher power evaporator or condenser. Alternatively, however, it is preferred to use this substantial increase in efficiency to design an evaporator and a condenser much smaller and more compact, while still achieving a certain performance. This is particularly advantageous for use in a heat pump for building heating for smaller and medium-sized buildings, because in buildings, and in particular in residential buildings, the space is typically limited.
  • FIG. 1 shows a plan view of a condenser or evaporator with turbulence generators in the form of a simple wire mesh fence.
  • FIG. 2 shows a honeycomb structure for implementing a laminarizer in the condenser
  • Fig. 3 is a plan view of a turbulent working fluid in a condenser under an evaporator
  • FIG. 4a is a schematic representation of an evaporator with an exemplary embodiment of the present invention.
  • FIG. 4a is a schematic representation of a condenser according to a preferred embodiment of the present invention.
  • FIG. 5 shows an overview diagram for illustrating a condenser with a gas removal device according to an embodiment of the present invention
  • FIG. 6a shows a sketch for illustrating the functionality of the gas removal device on a condenser according to the invention
  • Fig. 6b is a detailed illustration of the gas removal device
  • FIG. 7 shows a schematic representation of a heat pump with an evaporator according to an exemplary embodiment of the present invention and / or a condenser according to an exemplary embodiment of the present invention
  • Fig. 8a is a plan view of a preferred evaporator or condenser
  • Fig. 8b is a longitudinal section of a preferred evaporator
  • 9a is a plan view of an evaporator or condenser according to an alternative embodiment of the present invention
  • 9b is a schematic cross-sectional view of an evaporator or condenser according to an embodiment of the present invention
  • FIG. 10a shows a cross section through a laminarizer according to an embodiment of the present invention.
  • 10b shows a representation of the temperature along the path in a laminarizer cell of the laminarizer.
  • a device for generating vortices is provided on the evaporator side and / or on the condenser side.
  • This vortex generating device which may have a multiplicity of so-called “vortex generators" 40, as shown in FIGS. 4 a and 4b, results in that the water flow 41 leading to a liquid layer on a funnel-shaped evaporator 42 or a funnel-shaped condenser 43 leads, via the vortex generator or "vortex generator” runs.
  • the water flow from which it is intended to evaporate or into which it is to be condensed is continuously subjected to turbulence.
  • the lower layer of the water film is continuously mixed with the upper layer of the water film.
  • Vortex generators various materials can be used, such as a chain link fence, as shown schematically in Fig. 1.
  • This chain link fence is arranged in the water flow, in such a way that the wire is an obstacle to the flow of water and constantly leads to a division of the flow and in a sense to a "refolding" and thus to a vortex generation in the water layer.
  • the wire mesh shown in FIG. 1, which is also known as “hare wire”, has turbulence cells with a diameter between 0.5 mm to 3 mm and preferably 1 mm, the spacing of these turbulence cells being approximately equal to one to ten times that of the Diameter of a turbulence cell or a vortex generator is.
  • Vortex generators are used, such as arranged on the funnel-shaped evaporator pyramids, which effectively “cut” and “fold” the water flow, so that water from the lower portion of the liquid film is brought up and vice versa. This ensures that on the evaporator side, which is outlined in Fig. 4a, constantly “Warmer” water is brought to the evaporator surface and colder water, ie water that has already released its energy is mixed down.
  • the condenser output can be increased even without a vortex generator 40 if a gas flow laminarizer 48 is used.
  • a gas flow laminarizer may be formed, for example, by a honeycomb material in the form of a honeycomb, e.g. shown in Fig. 2 can be achieved.
  • the gradient of the temperature as a function of the location in the case of a non-laminar flow at the liquid surface is very large.
  • laminarization of the gas flow according to the invention however, a smaller gradient is achieved directly on the liquid surface.
  • the energetic conditions of the gas better match the energetic conditions of the liquid, so that the efficiency of the condensation process is significantly increased.
  • the laminarizer is used with the vortex generators 40 to achieve even higher condenser performance. however Even without vortex generator on the condenser side or without laminator 48 on the condenser side, the efficiency is already sustainably increased.
  • both the vortex generators 40 in the liquid layer on the condenser side and thus also the laminarizer 48 for laminating the flow of the gas.
  • Capacitor performance can be achieved that is up to 100 times higher than capacitor powers without vortex generators and / or laminators.
  • a wire mesh is shown as vortex generators, which is surrounded by water, with the result that in the working fluid, which does not necessarily have to be water, but preferably water, a turbulence generation occurs. This leads to a very uniform temperature distribution in the outflowing fluid stream. In a laminar flow, ie without the wire mesh as an example of turbulence generator, however, only a cooling takes place on the surface.
  • the honeycomb structure shown in Fig. 2 for laminarization of the gas flow serves to achieve a smoother temperature gradient to the fluid surface. This results in a statistically higher probability of finding molecules with the right amount of energy to condense on the surface.
  • a turbulent gas stream such as is usually supplied by a compressor, and in particular a turbo-compressor, is used, an extremely steep temperature gradient is produced and condensation is thereby hindered.
  • Figure 3 shows a turbulent water (fluid) on a condenser to increase condenser performance.
  • FIG. 5 An arrangement of a device, also referred to as a gas trap 50, in the condenser 51, a heat pump is shown in FIG.
  • Figure 5 shows a heat pump in which the condenser is located above an evaporator, although this arrangement does not necessarily have to be used to implement a gas trap.
  • the steam enters via a first gas channel 52 in a compressor 53 and is compressed there and ejected via a second gas passage 54.
  • the gas discharged there is preferably directed by a laminarizing device 55 according to the invention, which may be honeycomb-shaped or otherwise, to a condenser water which is conveyed via a condenser water channel 56 via a plate shaped or funnel-shaped Kondensiererablauf 57 runs to the side.
  • a laminarizing device 55 which may be honeycomb-shaped or otherwise, to a condenser water which is conveyed via a condenser water channel 56 via a plate shaped or funnel-shaped Kondensiererablauf 57 runs to the side.
  • the condenser outlet 57 is typically rotationally symmetrical and is preferably provided with a turbulence generator 58 according to the invention in order to increase the condensing efficiency.
  • a sealing lip 59 is provided, which separates the lower gas region 60 from the upper gas region 61.
  • the sealing lip 59 does not necessarily provide a complete seal. However, it ensures that the foreign gas transported by the condenser water on the condenser 57 accumulates in the region 60 below the condenser outlet 57.
  • the foreign gases because they are heavier than water vapor, fall into the gas trap 50 due to gravity.
  • a diffusion process acts against gravity, so that the foreign gases in the region 60 and in the gas trap also want the same concentration. This diffusion process therefore counteracts the gravitational effect of the gas trap.
  • the effect of the sealing lip 59 which separates the area above the condenser outlet and the Veriqueertrichters 57 from the area below this element 57 is reinforced by the fact that the laminarizer 55 is present, since the foreign gases, as soon as they affect the water flow 56 on the Condenser expire 57, can not go away, but to a certain extent be forced to run in the direction of the sealing lip and under the sealing lip to accumulate in the vicinity of the gas trap 50.
  • This behavior is further enhanced by the turbulence generator 58, as a result of which a more turbulent flow is present, which is also a has higher efficiency in order to capture and carry along foreign gas, which is in the upper region 61.
  • FIG. 6a shows a schematic representation of the functionality that has been illustrated with reference to the heat pump or the heat pump condenser 51 of FIG. 5.
  • Fig. 6a is particularly emphasized how the space 260 is separated below the drain 57 by the sealing lip 59 of the upper portion 61.
  • This separation need not be hermetic, as long as there is a higher likelihood that extraneous gases will be the turbulent water vapor that has been laminarized by the laminarizer 55, as shown by arrows 69, with a higher probability to follow the path in the lower portion 60, as indicated by an arrow 68, in comparison to the probability that the foreign gases enter the upper portion 61 again.
  • An enrichment in foreign gases will thus take place in the area 60, so that the diffusion effect is reduced to a certain extent out of the gas trap 50 and the efficiency of the gas trap is not significantly impaired.
  • the gas trap has a relatively long neck 70 which extends between the sump 71 and a preferably present inlet region 72, which may be funnel-shaped. It is not essential, however, the length of the neck 70, but that at least the lower part of the collecting container 10 in a cold area, such as the evaporator 2 of the heat pump is arranged. This means that warm water vapor from the area 60 of the condenser enters into contact with a cold surface of the collecting container 1, which leads to a condensation of the steam.
  • a lamination device 73 for example in the form of a honeycomb-shaped structure, is also arranged at the funnel opening in order to improve the efficiency of the gas trap.
  • the system can be implemented if the heat pump is designed so that the condenser is located above the evaporator.
  • the throat 70 passes down through the condenser and into the evaporator to create a cold wall of condensation which on the one hand leads to a continuous flow of gas into the gas trap and on the other hand always ensures that there is water in the gas trap. which can be heated to increase the pressure in the sump, such that at certain events a foreign gas discharge can take place.
  • Fig. 7 shows a schematic representation of a heat pump for building heating.
  • the heat pump for building heating is preferably designed so that single-family homes or smaller apartment buildings can be heated.
  • the heat pump for building heating according to an embodiment of the present invention is intended to heat smaller residential buildings with less than 10 housing units and preferably less than 5 housing units.
  • the heat pump comprises an evaporator with an evaporator housing 42 'with turbulence generators. The steam generated in the evaporator is fed via a steam line 100 to a compressor 102.
  • Compressor 102 compresses the vapor and supplies the compressed vapor via a vaporized vapor line labeled 104 into a condenser according to the present invention having a condenser housing 43 'having either turbulence generators or a laminarizer, or preferably both, to more efficiently condense produce.
  • the evaporator receives the liquid to be evaporated via a feed line 106, and the condenser discharges the condensed liquid via a discharge line 108.
  • the condenser 43 has a flow 110a with temperatures, for example in the range of 40 ° for underfloor heating and a return 110b of the building heating.
  • the same liquid can flow as in the condenser, without a heat exchanger is provided.
  • a heat exchanger may be provided, so that the flow 110a and the return 1 10b go to a heat exchanger not shown in Fig. 7 and do not go into an actual radiator.
  • drain line 108 may lead to an open water reservoir, such as groundwater, seawater, brine, river water, etc.
  • supply line 106 may be groundwater, seawater, river water, brine, etc.
  • a closed system can be used, as indicated by the dashed connecting lines to a connecting element 110.
  • the connector 110 ensures that the liquid condensed in the condenser is fed back into the evaporator, taking into account corresponding pressure differences.
  • the liquid 106 in the feed line carries heat from the groundwater but is not groundwater, in which case a heat exchanger is placed in a groundwater reservoir to circulate the then circulating liquid in the line 106 , which is then designed as a return line to warm up, so that the heat transferred from the groundwater through the heat pump process in the heating flow HOa is brought.
  • the working fluid in the evaporator and in the condenser is water.
  • other working fluids may be used, such as heat transfer fluids specially designed for heat pumps.
  • water is preferred because of its particular suitability for the process. Another significant benefit of water is that it is climate neutral.
  • the evaporator 42 In order to evaporate water at temperatures of about 10 ° C, the evaporator 42 is provided with an evaporator housing, which is designed to hold a pressure in the evaporator at least in the vicinity of the evaporator surface, in which the water flowing in the feed line 106 evaporates , If water is used as the working fluid, pressures in the evaporator will be below 30 mbar and even below 10 mbar.
  • pressures will be more than 40 mbar and less than 200 or 150 mbar.
  • a condenser housing is formed to hold these respective pressures. Pressures that are preferred to condensation temperatures of 30 ° C or below or 22 ° C or below are preferred.
  • FIG. 8A shows a plan view of an evaporator or condenser with wire sections as turbulence generators
  • FIG. 8B shows a longitudinal section of the evaporator, which analogously could also be the condenser, if corresponding feed / return lines etc. are taken into account and the condenser liquid not externally supplied and discharged, but would circulate.
  • the evaporator comprises an evaporator surface or condenser surface 80 on which turbulence generators 40 are arranged.
  • the turbulence generators 40 are individual wire sections which are formed together, for example, as a spiral 82. At the same time, turbulence generators could also function as separate or ger concentric wire rings be formed, however, the use of a spiral in the handling and assembly is easier.
  • adjacent wire sections 84a, 84b which each have a diameter d, spaced by a distance Dd, wherein the distance D d greater than the diameter d of a wire section and is preferably less than three times the diameter.
  • the wire portions in Fig. 8A are drawn in a circular cross section, the cross section of the wire portions may be arbitrary.
  • FIG. 8B shows a funnel-shaped evaporator or condenser or a funnel-shaped evaporator surface or condenser surface 80 in longitudinal section.
  • the wire sections are directly fastened to this surface 80.
  • the wire portions may also be spaced as long as relative positioning of the turbulence generators 40 to the surface 80 is provided, such that it engages the working fluid present on the surface 80 with the turbulence generators to cause turbulence.
  • the surface 80 for both the evaporator and the condenser is preferably shaped so that the working fluid supplied via a working fluid inlet 86 does not only stand on the surface 80, as would be the case if the surface were completely horizontal and an almost non-existent inflow would be present, but that the working fluid flows on the surface due to gravity.
  • the surface 80 comprises at least one inclined plane.
  • the surface is funnel-shaped and the inflow port 86 is centrally located relative to the working surface such that the working fluid does not flow off only on one side with respect to the supply port, but flows off to all sides.
  • an implementation would also be useful for certain applications where e.g.
  • a flat surface which is arranged as an inclined plane and is arranged at the highest point of the inlet 86, so that the working fluid is not on several sides of the inlet, but substantially in a limited sector, such as 30 °, 60 ° or 90 ° with respect to the inlet flows on the surface, there to engage with the turbulence generators 40.
  • the working surface may also be pyramidal or cone-shaped or uneven or curved in cross-section, as long as in the working position of the evaporator or condenser the working fluid copes with a height difference from the force of gravity.
  • Figures 9A and 9B show a plan view of an alternative surface 80 of an evaporator or condenser having no wire sections as in Figure 8A, but with elevations or depressions in the work surface. In Fig. 9B, only elevations are shown.
  • the turbulence generators 40 protrude from the surface or are recessed with respect to the surface, so to speak “holes” in the surface 80, and preferably the turbulence generators 40 are so strong protrude over the surface that they protrude at least with their tip over a level of the working fluid 41 on the surface 80.
  • the turbulence generators 40 may have any shapes, as indicated in Fig. 9B. The more abrupt the shapes are, the more turbulence is generated, but at the same time the turbulence generators can also be designed to "split" and "fold over” the water flow with special shapes.
  • the turbulence generators may also be e.g. be implemented by projecting into the working fluid elements, such as bars, etc., which are not firmly connected to the surface 80, but e.g. suspended above the surface 80.
  • these rods can also be moved to generate particularly strong turbulence.
  • Turbulence can thus be generated in many different ways, with turbulence generators being able to be firmly connected to the work surface 80 to generate this turbulence, or else being positioned statically or dynamically relative to the work surface, as long as, preferably, at least 20%. the entire water flow are provided with turbulence.
  • FIG. 10A shows a cross-section through a laminarization device with various laminarization cells 120.
  • Above the laminarizer cells 120 is turbulent vapor at a temperature 9-Q, as indicated schematically by the non-directional vapor arrows 122.
  • Below the laminarizer cells 120 laminarized vapor 124 is shown, which, due to the fact that it is close to the liquid of the condenser on the condenser surface 80, has a temperature of about equal to $ w. 9w is lower than 9D
  • the temperature of the undirected steam $ D may be much higher than the temperature of the water $ w. Nevertheless, no steam coolers etc. are required because the laminarizer 48 with the individual laminarizer cells 120 separated by walls 121 enforces the temperature distribution shown in Fig. 10b.
  • the laminarizer is honeycomb-shaped or made of a tube material as long as there are individual more or less collimated and preferably smooth laminator cells 120 which effect a laminarization, as represented by the directed vapor flow 124.
  • the laminator does not necessarily have to achieve perfect 100% laminarization as long as the gas stream at the exit of the laminarizer is less turbulent than the gas stream at the entrance of the laminarizer.
  • the laminarizer cells or the laminarizer as a whole are designed such that the output laminarized steam flow is at least half as turbulent as the input-side turbulent steam flow.
  • the length of a laminarizer cell 120 be about 10 mm long when the diameter of the laminarizer cell is 5 mm.
  • the length is longer than 1 mm.
  • Other favorable example dimensions are: if the Diameter greater than 5 mm, the length is greater than 10 mm, and if the diameter is smaller than 5 mm, the length is smaller than 10 mm.
  • the distance D L between the exit of the laminarizer cells 120 and the surface of the liquid is relatively small and in particular less than 50 mm preferably less than 25 mm, or preferably less than 6 mm.
  • This also forces the gas or the vaporized working fluid, when leaving the laminarizer cells 120, to have a temperature which is almost equal to or only slightly higher than the temperature of the water. This ensures that the steam particles in the flow do not "bounce off” from the water or in turn have a steam-generating effect, but are absorbed by condensation into the water, since only in this way does particularly efficient heat transfer take place from the steam to the water.
  • the laminarizer according to the invention provides a considerable increase in the efficiency of condensation.
  • the higher the temperature of the steam relative to the temperature of the condensing liquid the efficiency in power per area has greatly decreased. So you can say that with a superheating of the steam of 10 ° only 10% condensing capacity was possible.
  • a considerably greater power is achieved with the same area, which, depending on the implementation, can be 40-200 kW / m 2 or even more. This means at least a twentyfold increase in efficiency with simple measures.
  • Another advantage is that the efficiency is relatively independent of the temperature of the non-directional steam. Therefore, it is according to the invention readily possible to condense a vapor having a temperature of for example above 150 ° C with a water, which is for example at 40 ° C.
  • the laminarizer therefore provides a decoupling of the condensing efficiency from the steam temperature at the outlet of the compressor.
  • the compressor can be dimensioned according to its requirements and it no longer has to be taken into account in the dimensioning of the compressor according to the present invention, which thermal conditions are necessary for condensing.
  • the turbulence generators and the laminarization device can not be formed as two separate elements but also by one and the same element.
  • the turbulence generators and the laminarization device can not be formed as two separate elements but also by one and the same element.
  • the liquid flows around the fibers, creating turbulence.
  • the flooded fibers are the turbulence generators.
  • the non-lapping fibers project beyond the liquid, on the other hand, constitute the laminarizer.
  • the friction of the vapor on the fibers results in laminarization of the vapor.
  • the material of the fibers is plastic or metal, and the fiber fabric is for example metal wool or especially steel wool.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un évaporateur ou un condensateur (43) comprenant une surface, sur laquelle un fluide de travail (41) est placé. De plus, des générateurs de turbulences (40) sont conçues pour produire des turbulences dans le fluide de travail se trouvant sur la surface de travail. Un dispositif de laminage (48) est placé dans le condensateur alternativement ou en plus, ce qui permet de laminer le courant de vapeur produit par le dispositif de compression. Côté évaporateur, l'efficacité de l'évaporation est améliorée, et côté condensateur, l'efficacité de condensation est également améliorée, ce qui est très utile pour une réduction considérable de la taille sans perte de performances de ces composants, en particulier pour une pompe à chaleur servant à chauffer des bâtiments.
EP09768974.9A 2008-06-23 2009-06-23 Procédé et dispositif de condensation efficace Active EP2307824B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008029597 2008-06-23
DE102008031300 2008-07-02
PCT/EP2009/004519 WO2009156125A2 (fr) 2008-06-23 2009-06-23 Procédé et dispositif d'évaporation de surface efficace et de condensation efficace

Publications (2)

Publication Number Publication Date
EP2307824A2 true EP2307824A2 (fr) 2011-04-13
EP2307824B1 EP2307824B1 (fr) 2016-04-06

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Country Status (6)

Country Link
US (2) US20110146316A1 (fr)
EP (1) EP2307824B1 (fr)
JP (3) JP2011525607A (fr)
ES (1) ES2575686T3 (fr)
PL (1) PL2307824T3 (fr)
WO (1) WO2009156125A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018172048A1 (fr) * 2017-03-24 2018-09-27 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Dispositif de réaction comprenant un échangeur de chaleur et son utilisation

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US11247188B2 (en) 2017-03-24 2022-02-15 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Reaction device with heat exchanger and use thereof

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US20140075978A1 (en) 2014-03-20
ES2575686T3 (es) 2016-06-30
EP2307824B1 (fr) 2016-04-06
WO2009156125A3 (fr) 2010-06-10
US20110146316A1 (en) 2011-06-23
JP5722930B2 (ja) 2015-05-27
PL2307824T3 (pl) 2016-12-30
JP2011525607A (ja) 2011-09-22
WO2009156125A2 (fr) 2009-12-30
US9732994B2 (en) 2017-08-15
JP6106633B2 (ja) 2017-04-05
JP2013076566A (ja) 2013-04-25
JP2014206372A (ja) 2014-10-30

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