EP2307824B1 - Procédé et dispositif de condensation efficace - Google Patents

Procédé et dispositif de condensation efficace Download PDF

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Publication number
EP2307824B1
EP2307824B1 EP09768974.9A EP09768974A EP2307824B1 EP 2307824 B1 EP2307824 B1 EP 2307824B1 EP 09768974 A EP09768974 A EP 09768974A EP 2307824 B1 EP2307824 B1 EP 2307824B1
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Prior art keywords
condenser
liquid
operating liquid
evaporator
operating
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EP09768974.9A
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German (de)
English (en)
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EP2307824A2 (fr
Inventor
Holger Sedlak
Oliver Kniffler
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Efficient Energy GmbH
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Efficient Energy GmbH
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    • 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 the evaporation of surfaces and in particular to the use of evaporation and condensation on surfaces in heat pumps.
  • WO 92/15839 shows a condensing with a plurality of turbulence generators.
  • 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 the working liquid, a heat distribution, which consists in that the top section is cooled in the evaporator, while the lower portion of the layer has almost the same temperature of the working fluid as that supplied by a heat source.
  • the object of the present invention is to obtain a more efficient concept for surface condenser.
  • the condensation efficiency is increased by 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, which is configured to laminarize the vapor stream directed to the working fluid.
  • 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 arranged to produce a gas flow at least halfway therethrough is turbulent like a gas stream fed to the laminarizer, the condenser being provided with turbulence generators such 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 significant increase in the evaporation efficiency and the condenser efficiency, which increase can either be used to produce a higher performance evaporator or condenser. Alternatively, however, it is preferred to use this substantial increase in efficiency to be able to interpret 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.
  • turbulence generators and laminarizers can be implemented with the simplest means, and the simple measures eliminate all electronic / electrical items.
  • a device for generating vortices is provided on the condenser side.
  • This water vortex generating device the plurality of so-called. "Vortex generator” 40, as shown in Fig. 4a and Fig. 4b shown, results in that the water flow 41, which leads to a liquid layer on a funnel-shaped evaporator 42 or a funnel-shaped condenser 43, 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 is drawn.
  • 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 in Fig. 1 Wire mesh also known as “hare wire” has turbulence cells with a diameter of between 0.5 mm to 3 mm and preferably of 1 mm, the spacing of these turbulence cells being approximately equal to one to ten times the diameter of a turbulence cell or a vortex generator is.
  • Vortex generators are used, such as 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, the in Fig. 4a sketched, constantly “warmer” water is brought to the evaporator surface and colder water, ie water that has already released its energy is mixed down.
  • the vortex generators can be used both in the evaporator and in the condenser, the condenser performance can be increased without vortex generator 40 when a gas flow laminarizer 48 is used.
  • a gas flow laminarizer may be, for example, a honeycomb material in the form of a honeycomb, such as in Fig. 2 shown to be achieved.
  • the temperature gradient as a function of location is very large in the case of non-laminar flow at the liquid surface.
  • 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 laminarizing 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.
  • Fig. 1 is, as has already been stated, as vortex generators a wire mesh is shown, which is surrounded by water, with the result that in the working fluid, which need not necessarily be water, but preferably is water, 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.
  • honeycomb structure for laminarization of the gas flow serves to achieve a gentler 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.
  • Fig. 3 shows turbulent water (fluid) on a condenser to increase condenser performance.
  • FIG. 5 An arrangement of a device, which is also referred to as a gas trap 50, in the condenser 51 is a heat pump in Fig. 5 shown.
  • a heat pump in which the condenser is disposed 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 laminarizer 55 according to the invention, which may be honeycomb-shaped or otherwise, to a condenser water via a condenser water channel 56 via a plate-shaped or funnel-shaped Kondensiererablauf 57 runs to the side.
  • a laminarizer 55 which may be honeycomb-shaped or otherwise, to a condenser water 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 the force of gravity, to the extent 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 Verissueertrichters 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 to capture foreign gas, which is in the upper region 61, so to speak, and mitzusutragen.
  • Fig. 6a shows a schematic diagram of the functionality, based on the heat pump or the heat pump condenser 51 of Fig. 5 has been shown.
  • 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 must, as it is in Fig. 6a is clearly not hermetic, as long as there is a higher probability that foreign gases to the turbulent water vapor, which has been laminarized by the laminarizer 55, however, as shown by arrows 69, with a higher probability the way in the lower area 60th follow, as indicated by an arrow 68, in comparison to the probability that the foreign gases re-enter the upper area 61.
  • an enrichment in foreign gases will take place in the region 60, so that the diffusion effect is effectively reduced out of the gas trap 50 and the efficiency of the gas trap is not significantly impaired.
  • the gas trap be similar to FIG. 6b train.
  • 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 laminarizing device 73 such as 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 passes the compressed vapor through a compressed vapor steam line, labeled 104, into a condenser of the invention having a condenser housing 43 'having either turbulence generators or a laminarizer, or preferably both, for more efficient condensing to create.
  • 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 also be provided a heat exchanger, so that the flow 110a and the return 110b to a in Fig. 7 not shown heat exchanger go 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 is brought into the heating flow 110a via the heat pump process.
  • 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 could also be analogous to the condenser, if appropriate flow / return lines, etc. are taken into account and the Kondensierer crampkeit is not externally supplied and sensed, 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, the turbulence generators could also be separated as more or less be formed concentric wire rings, however, the use of a spiral in the handling and assembly is easier.
  • adjacent wire portions 84a, 84b which each have a diameter d, spaced by a distance D d , wherein the distance D d is greater than the diameter d of a wire portion and preferably is less than three times the diameter.
  • the wire sections in Fig. 8A drawn with circular cross section the cross section of the wire sections may be arbitrary.
  • Fig. 8B shows in longitudinal section a funnel-shaped evaporator or condenser or a funnel-shaped evaporator surface or Kondensiererober formula 80.
  • the wire sections are directly attached.
  • 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 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.
  • Figs. 9A and 9B show a plan view of an alternative surface 80 of an evaporator or condenser, in which no wire sections as in FIG Fig. 8A are present, but elevations or depressions are present in the work surface.
  • Fig. 9B only increases are shown. However, the pits will be implemented similarly, but in a sense "negative” to the increases shown.
  • the turbulence generators 40 protrude from the surface or are set back relative to the surface, so to speak "holes" in the surface 80, wherein preferably the turbulence generators 40 protrude so strongly over the surface that they at least with their tip on a state of the working fluid 41 on protrude the surface 80.
  • the turbulence generators 40 may have any shapes as shown in FIG Fig. 9B is indicated. The more abrupt the shapes are, the more “swirls” or turbulences are created. At the same time, however, the turbulence generators can also be designed to achieve "splitting" and "folding" of the water flow with special forms.
  • 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 create these turbulences, or else being positioned statically or dynamically relative to the work surface, as long as, preferably, at least 20% of the total Water flow are provided with turbulence.
  • turbulence generators as close to the entire working surface of the evaporator or condenser as possible so that between 90% and nearly 100% of the total flow is turbulent or more than 80% of surface area 80% and more than 90% of the liquid on the surface 80 are in turbulence.
  • Fig. 10A shows a cross-section through a laminarizer with various laminarization 120.
  • Laminarisiererzellen 120 Above the Laminarisiererzellen 120 is turbulent vapor at a temperature ⁇ D , as it is schematically indicated by the non-directional steam arrows 122.
  • laminarized vapor 124 Below the laminarization cells 120, however, there is shown laminarized vapor 124, 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 ⁇ D.
  • the temperature of the non-directional steam ⁇ D may be much higher than the temperature of the water ⁇ w . Nevertheless, no steam coolers, etc. are required, since the laminarizer 48 with the individual laminarizer cells 120, which are separated by walls 121, the in Fig. 10b forced temperature distribution enforces.
  • the laminarizer is honeycomb or tubing, as long as there are individual laminar cells 120 more or less parallel and internally preferably smooth, causing laminarization, as shown by directional 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 vaporized working fluid, as it leaves the laminarizer cells 120, to have a temperature that is nearly 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 again 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.
  • a fiber web or a fiber mat of preferably non-absorbent fibers may be laid on the evaporator surface or the condenser surface, wherein the surface of the fiber fabric projects beyond the level of the liquid, preferably more than 3 mm and in particular more than 5 mm.
  • 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.
  • Embodiments relate to an evaporator 42 for evaporating a working fluid 41, having the following features: an evaporator surface 80, on which the working fluid to be evaporated is to be arranged; and a plurality of turbulence generators 40 configured to generate turbulence in the working fluid to be evaporated on the evaporator surface 80.
  • An embodiment of the evaporator includes an evaporator housing 42 'in which the evaporator surface 80 is disposed, and configured to maintain a pressure in the evaporator housing at the evaporator surface 80 that is such that the working fluid reaches when the working fluid reaches the evaporator surface , has a boiling temperature or a temperature which is in a range which extends from a temperature equal to the boiling point -10 Kelvin to a temperature equal to the boiling temperature + 10 Kelvin.
  • the evaporator housing 42 in one embodiment, the evaporator housing 42 'includes a working fluid inlet 106 and a working fluid vapor discharge opening 100, wherein the discharge opening 100 is adapted to be coupled to an input of a compressor 102 for compressing the vapor.
  • the evaporator surface 80 is inclined in a working position, the working fluid being supplied to the evaporator surface 80 such that the working fluid flows from a supply 86a to a drain 86b from the evaporator surface 80 due to gravity.
  • the evaporator surface is pyramidal, conical, funnel-shaped or in the form of an inclined plane, wherein the inclined plane is flat or not plan.
  • a feed for the working fluid from the evaporator surface 80 is surrounded so that the working fluid flows on several sides of the feed over the evaporator surface 80 83.
  • the turbulence generators 40 are formed by a component 82 separated from the evaporator surface or by elevations or depressions 90 on the evaporator surface 80.
  • the turbulence generators 40 are formed by wire sections 84a, 84b on the evaporator surface, which are fixed relative to the evaporator surface and arranged such that a flow direction 83 of the working fluid intersects a direction in which the wire sections are located.
  • the turbulence generators are formed as interconnected helical wire sections, wherein a distance between two adjacent wire sections in the flow direction 83 of the working fluid is greater than the diameter of a wire section and less than three times the diameter of the wire section.
  • the elevations 90 or the depressions are dimensioned such that an impinging working fluid can be put into turbulence.
  • the protrusions 90 have a height at which they extend over the surface 80, which is higher than a level of the working fluid on the evaporator surface 80 in an operation of the evaporator.
  • the turbulence generators are configured such that a stream of water on the evaporator surface has turbulences, which preferably comprise at least 20% of the total liquid flow on the evaporator.
  • the working fluid is water.
  • One embodiment relates to a method for vaporizing 42 a working fluid 41 comprising the following steps: arranging a working fluid to be evaporated on an evaporator surface 80; and generating turbulence 40 in the working fluid to be evaporated on the evaporator surface 80.

Claims (15)

  1. Condenseur pour condenser un liquide de travail évaporé, aux caractéristiques suivantes:
    une conduite de gaz (54) destinée à alimenter de la vapeur comprimée chaude vers le condenseur;
    une conduite d'évacuation du condenseur (57) destinée à évacuer le liquide de travail du condenseur;
    une surface de condenseur (80) sur laquelle doit être disposé un liquide de travail (41), la surface de condenseur (80) étant inclinée dans une position de travail, le liquide de travail étant alimenté vers la surface du condenseur (80) de sorte que le liquide de travail circule par suite de la gravité d'une conduite d'alimentation (56) de liquide de travail vers la surface de condenseur vers la conduite d'évacuation de condenseur (57) depuis la surface du condenseur; et
    une pluralité de générateurs de turbulence qui sont conçus pour générer des turbulences d'écoulement dans le liquide de travail se trouvant sur la surface de condenseur (80);
    le condenseur étant conçu pour orienter un flux de vapeur (124) éjecté du canal de gaz (54) sur le liquide de travail (41) avant que le liquide de travail ne s'écoule à travers la conduite d'évacuation de condenseur (57).
  2. Condenseur selon la revendication 1, aux caractéristiques suivantes:
    un boîtier de condenseur (43') dans lequel est disposée la surface de condenseur (80) et conçu pour maintenir dans le boîtier de condenseur à la surface de condenseur une pression qui est telle qu'un liquide de travail condensé présente une température minimale prédéterminée.
  3. Condenseur selon la revendication 2, dans lequel la température minimale est supérieure ou égale à 22°C.
  4. Condenseur selon la revendication 1, dans lequel la surface de condenseur est de forme pyramidale, conique, en forme d'entonnoir ou sous forme d'un plan incliné qui est plan ou non plan.
  5. Condenseur selon l'une des revendications 1 ou 4, dans lequel une conduite d'alimentation du liquide est entourée vers la surface de condenseur par la surface de condenseur de sorte que le liquide circule de plusieurs côtés de la conduite d'alimentation (41) sur la surface de condenseur (80).
  6. Condenseur selon l'une des revendications 1 à 6, présentant tant les générateurs de turbulence (40) qu'un moyen d'écoulement laminaire (48) qui est conçu pour écouler de manière laminaire le flux de vapeur (124) éjecté de la conduite de gaz (54) et dirigé vers la surface de condenseur (80) de sorte qu'une vapeur écoulée de manière laminaire par le moyen d'écoulement laminaire (48) arrive sur le liquide de travail (41), le moyen d'écoulement laminaire étant disposé de sorte que la vapeur écoulée de manière laminaire (124) arrive sur les turbulences du liquide générées par les générateurs de turbulence (40) sur la surface de condenseur (80).
  7. Condenseur selon la revendication 6, dans lequel tant les générateurs de turbulence (40) que le moyen d'écroulement laminaire (48) sont formés par un même élément.
  8. Condenseur selon la revendication 7, dans lequel l'élément présente un tissu de fibres qui s'élève au-dessus d'un niveau de liquide sur la surface de condenseur.
  9. Condenseur selon la revendication 8, dans lequel le tissu de fibres est une laine plastique à fibres non absorbantes ou une laine métallique.
  10. Condenseur selon l'une des revendications 6 à 9, dans lequel une distance du moyen d'écoulement laminaire (48) au liquide de travail sur la surface de condenseur (80) que doit parcourir la vapeur écoulée de manière laminaire est inférieure à 25 mm.
  11. Condenseur selon la revendication 10, qui est réalisé en un matériau en nid d'abeilles ou en un matériau tubulaire avec des cellules d'écoulement laminaire (120), dans lequel une longueur d'une cellule d'écoulement laminaire en comparaison avec un diamètre de la cellule d'écoulement laminaire (120) est réalisée de sorte que du côté de la sortie soit généré un flux de gaz qui est au moins deux fois moins turbulent qu'un flux de gaz qui est alimenté vers le moyen d'écoulement laminaire (48).
  12. Condenseur selon la revendication 11, dans lequel une cellule d'écoulement laminaire (120), lorsqu'elle présente un diamètre supérieur à 5 mm, présente une longueur supérieure à 10 mm et, lorsqu'elle présente un diamètre inférieur à 1 mm, présente une longueur supérieure à 1 mm.
  13. Condenseur selon l'une des revendications 1 à 12, dans lequel est présent un réservoir de liquide dans lequel est introduit le liquide s'écoulant de la surface de condenseur (80), et peut être alimenté à partir du liquide plus froid comparé au liquide écoulé comme flux de liquide (41) de la surface de condenseur (80).
  14. Pompe à chaleur, aux caractéristiques suivantes:
    un évaporateur (42) destiné à évaporer un liquide de travail (41), aux caractéristiques suivantes:
    une surface d'évaporateur (80) sur laquelle doit être disposé le liquide de travail à évaporer; et
    une pluralité de générateurs de turbulence (40) formés de manière à générer des turbulences dans le liquide de travail à évaporer sur la surface d'évaporateur (80);
    un condenseur (43) selon l'une des revendications 1 à 13; et
    un compresseur (102) destiné à comprimer le liquide de travail évaporé par l'évaporateur (42), le compresseur (10) étant couplé au condenseur (43) pour alimenter de la vapeur comprimée vers le condenseur (43), et
    le condenseur (43') présentant par ailleurs une entrée de chauffage (110a) destinée à fournir du liquide de chauffage chaud et un retour de chauffage (110b) destiné à fournir un liquide de chauffage froid au condenseur (43').
  15. Procédé pour condenser un liquide de travail évaporé, aux étapes suivantes consistant à:
    disposer du liquide de travail (41) sur une surface de condenseur (80), la surface de condenseur (80) étant inclinée dans une position de travail, le liquide de travail étant alimenté vers la surface de condenseur (80) de sorte que le liquide de travail circule par suite de la gravité d'une conduite d'alimentation du liquide de travail vers la surface de condenseur vers une conduite d'écoulement du liquide de travail depuis la surface de condenseur;
    générer des turbulences (40) dans le liquide de travail disposé sur la surface de condenseur (80); et
    orienter un flux de vapeur (124) éjecté d'une conduite de gaz (54) vers le liquide de travail (41) avant que le liquide de travail ne s'écoule à travers une conduite d'évacuation de condenseur (57).
EP09768974.9A 2008-06-23 2009-06-23 Procédé et dispositif de condensation efficace Active EP2307824B1 (fr)

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DE102008016663A1 (de) 2008-04-01 2009-10-08 Efficient Energy Gmbh Verflüssiger für eine Wärmepumpe und Wärmepumpe
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PL2307824T3 (pl) 2016-12-30
WO2009156125A2 (fr) 2009-12-30
US9732994B2 (en) 2017-08-15
US20140075978A1 (en) 2014-03-20
EP2307824A2 (fr) 2011-04-13
JP5722930B2 (ja) 2015-05-27
ES2575686T3 (es) 2016-06-30
JP2014206372A (ja) 2014-10-30
JP2013076566A (ja) 2013-04-25
JP6106633B2 (ja) 2017-04-05
JP2011525607A (ja) 2011-09-22
US20110146316A1 (en) 2011-06-23

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