US20110146316A1 - Device and Method for an Efficient Surface Evaporation and for an Efficient Condensation - Google Patents

Device and Method for an Efficient Surface Evaporation and for an Efficient Condensation Download PDF

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Publication number
US20110146316A1
US20110146316A1 US12/976,230 US97623010A US2011146316A1 US 20110146316 A1 US20110146316 A1 US 20110146316A1 US 97623010 A US97623010 A US 97623010A US 2011146316 A1 US2011146316 A1 US 2011146316A1
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Prior art keywords
condenser
evaporator
liquid
operating liquid
laminarizer
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US12/976,230
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English (en)
Inventor
Holger Sedlak
Oliver Kniffler
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Efficient Energy GmbH
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Efficient Energy GmbH
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Assigned to EFFICIENT ENERGY GMBH reassignment EFFICIENT ENERGY GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KNIFFLER, OLIVER, SEDLAK, HOLGER
Publication of US20110146316A1 publication Critical patent/US20110146316A1/en
Priority to US14/085,747 priority Critical patent/US9732994B2/en
Abandoned legal-status Critical Current

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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 evaporating or condensing on surfaces and in particular to an application of evaporating and condensing to surfaces in heat pumps.
  • a liquid layer occurs in an evaporator of a heat pump, executes, due to the typical layering which may be observed with liquids and in particular with water as an operating liquid, a heat distribution which means that in the evaporator the top portion is cooled while the bottom portion of the layer virtually has the same temperature as the operating liquid as it is supplied from a heat source.
  • an evaporator for evaporating an operating liquid may have an evaporator surface on which the operating liquid to be evaporated is to be arranged; and a plurality of turbulence generators which are implemented to generate turbulences in the operating liquid to be evaporated on the evaporator surface.
  • a condenser for condensing an evaporated operating liquid may have a condenser surface on which an operating liquid is to be arranged; a plurality of turbulence generators which are implemented to generate current turbulences in the operating liquid located on the condenser surface; or a laminarizer which is implemented to make a vapor current directed to the condenser surface laminar so that a vapor made laminar by the laminarizer impinges on the operating liquid.
  • Another embodiment may be an evaporator or condenser, wherein the operating liquid is water.
  • a heat pump may have an evaporator for evaporating an operating liquid which may have an evaporator surface on which the operating liquid to be evaporated is to be arranged; and a plurality of turbulence generators which are implemented to generate turbulences in the operating liquid to be evaporated on the evaporator surface; a condenser for condensing an evaporated operating liquid, which may have a condenser surface on which an operating liquid is to be arranged; a plurality of turbulence generators which are implemented to generate current turbulences in the operating liquid located on the condenser surface; or a laminarizer which is implemented to make a vapor current directed to the condenser surface laminar so that a vapor made laminar by the laminarizer impinges on the operating liquid; and a compressor for compressing operating liquid evaporated by the evaporator, wherein the compressor is coupled to the condenser in order to feed compressed vapor into the condenser
  • method for evaporating an operating liquid may have the steps of arranging an operating liquid to be evaporated on an evaporator surface; and generating turbulences in the operating liquid to be evaporated on the evaporator surface.
  • a method for condensing an evaporated operating liquid may have the steps of arranging operating liquid on a condenser surface; generating turbulences in the operating liquid arranged on the condenser surface; or making a vapor current directed to the condenser surface laminar so that vapor made laminar hits the operating liquid.
  • the present invention is based on the finding that the evaporation process may be substantially enhanced by the use of turbulence generators or vortex generators on the evaporator surface onto which an operating liquid to be evaporated is to be arranged.
  • the turbulence generators guarantee that no layering takes place on the operating liquid on the evaporator surface. Instead, the cold liquid layer forming the surface of the operating liquid on the evaporating surface is torn apart and brought to the bottom by the turbulence generators.
  • the warmer bottom layer of the operating liquid is brought to the top, so that it is guaranteed that there is operating liquid at the surface which has a temperature at which, considering the pressure in the evaporator which is below the atmospheric pressure and advantageously even below 50 mbar, an evaporation occurs.
  • the pressure is selected such that the liquid of the bottom layer which is turned up to the top by the turbulence generators is the boiling temperature of the liquid which, as is known, decreases with decreasing pressure.
  • the condensation efficiency is increased by providing turbulence generators also on the condenser surface, and these turbulence generators lead to a layering of the liquid on the condenser surface being prevented or constantly disrupted.
  • the warmer top layer which absorbed heat from the condensation process is brought to the bottom and simultaneously cooler liquid in the condenser is brought to the top to be heated up by the condensing vapor.
  • a laminarization means (means for making laminar) is present which is implemented to make the vapor stream directed to the operating liquid laminar.
  • the present invention relates to an evaporator with an evaporator surface provided with turbulence generators so that a water stream has turbulences on the evaporator surface which include at least 20% of the total water current.
  • the present invention relates to a condenser in a condenser space, wherein the condenser space comprises a laminarizing means to make a gas current directed to a liquid surface in the condenser laminar, the laminarizer being implemented to generate a gas stream on the output side which is at least half as turbulent as a gas stream fed into the laminarizer, the condenser being provided with turbulence generators so that a water stream on the condenser surface comprises turbulences including at least 20% of the total water current.
  • the present invention achieves a substantial increase of the evaporation efficiency and the condenser efficiency, wherein this increase may either be used to manufacture an evaporator or condenser with a higher power.
  • this substantial efficiency increase to construct an evaporator and a condenser substantially smaller and more compact, wherein, however, a certain performance is achieved.
  • This is a great advantage, in particular for an application in a heat pump for heating a building for small and medium-sized buildings, as in buildings, and particularly in residential buildings, space is typically limited.
  • turbulence generators and laminarizers may be implemented with the simplest means, thereby avoiding the use of any electronic/electric elements.
  • FIG. 1 is a top view onto a condenser or evaporator having turbulence generators in the form of a simple wire mesh fence.
  • FIG. 2 is a honeycomb structure for implementing a laminarizer in the condenser
  • FIG. 3 is a top view onto a turbulent operating liquid in a condenser beneath an evaporator
  • FIG. 4 a is a schematical illustration of an evaporator with one embodiment of the present invention.
  • FIG. 4 b is a schematical illustration of a condenser according to an embodiment of the present invention.
  • FIG. 5 is an overview diagram for illustrating a liquefier with a gas removal device according to an embodiment of the present invention
  • FIG. 6 a is a plot for illustrating the functionality of the gas removal device at an inventive condenser
  • FIG. 6 b is a detailed illustration of the gas removal device
  • FIG. 7 is a schematical illustration of a heat pump with an evaporator according to one embodiment of the present invention and/or a condenser according to one embodiment of the present invention
  • FIG. 8 a is a top view onto an evaporator or condenser
  • FIG. 8 b is a longitudinal section of an evaporator
  • FIG. 9 a is a top view onto an evaporator or condenser according to an alternative embodiment of the present invention.
  • FIG. 9 b is a schematical cross-sectional illustration of an evaporator or condenser according to an embodiment of the present invention.
  • FIG. 10 a is a cross-section through a laminarizer according to an embodiment of the present invention.
  • FIG. 10 b is an illustration of the temperature along the path in a laminarizer cell of the laminarizer.
  • a means for generating vortexes is provided on the evaporator side and/or on the condenser side.
  • This water vortex generating means which may comprise a plurality of so-called vortex generators 40 , as is illustrated in FIG. 4 a and FIG. 4 b , leads to the water current 41 leading to a liquid layer on a funnel-shaped evaporator 42 or a funnel-shaped condenser 43 passing across the vortex generators.
  • This leads to the water stream which is to be evaporated or condensed being continuously subjected to turbulence or vortexes.
  • the bottom layer of the water film is continuously mixed with the top layer of the water film.
  • a wire mesh fence for so-called vortex generators, different materials may be used, like, for example, a wire mesh fence, as is schematically illustrated in FIG. 1 .
  • This wire mesh fence is arranged in the water stream or water current so that the wire represents an obstacle for the water current and continuously leads to a division of the flow and, so to speak, to a “folding”, and thus to a vortex generation in the water layer.
  • the wire mesh illustrated in FIG. 1 which is also known as “chicken wire”, comprises turbulence cells with a diameter of between 0.5 mm and 3 mm and 1 mm, wherein the distance between these turbulence cells is approximately one to ten times the diameter of a turbulence cell or a vortex generator.
  • any other vortex generators may be used, like, for example, pyramids arranged on the funnel-shaped evaporator which, so to speak, “cut up” and “fold down” the water current so that water from the bottom area of the liquid film is brought to the top and vice versa. It is thus guaranteed that, on the evaporator side which is plotted in FIG. 4 a , “warmer” water is continuously brought to the evaporator surface and colder water, i.e. water which has already given off its energy, is mixed downwards.
  • the condenser power may be increased also without a vortex generator 40 if a gas current laminarizer 48 is used.
  • a gas current or gas stream laminarizer may, for example, be achieved by a honeycomb-shaped material in the form of a honeycomb, as is illustrated in FIG. 2 . It has turned out that with a honeycomb cell with a diameter of 3 mm and a honeycomb length of 8 mm already a gas stream laminarization is achieved, which leads to the gas stream 49 , as it exits the laminarizer 48 , being a laminar current.
  • the condenser efficiency of this laminar current is substantially higher compared to a situation in which the non-laminarized gas stream hits the liquid film of the funnel-shaped condenser.
  • the reason for this is that overheating effects in the gas which is supplied from the compressor into the condenser, as is illustrated in FIG. 4 b , may be retained.
  • the gradient of the temperature as a function of the location is very high in the case of a non-laminar current at the liquid surface.
  • a smaller gradient is achieved directly at the liquid surface.
  • the energetic ratios of the gas better suit the energetic ratios of the liquid, so that the efficiency of the condensation process is essentially increased.
  • the laminarization means is used together with the vortex generators 40 to achieve an even higher condenser power. However, also without vortex generators on the condenser side or without a laminarizer 48 on the condenser side, the efficiency is already substantially increased.
  • condenser powers may be achieved which are up to 100 times higher than condenser powers without vortex generators and/or laminarizers.
  • a wire mesh is illustrated as a vortex generator which is surrounded by water, which leads to a turbulence generation occurring in the operating liquid, which does not necessarily have to be water, but which is advantageously water. This leads to a very even temperature distribution in the fluid stream flowing off. With a laminar current, i.e. without the wire mesh as an example of a turbulence generator, however only a cooling at the surface takes place.
  • the honeycomb structure illustrated in FIG. 2 for making the gas current laminar serves to achieve a smoother temperature gradient to the fluid surface.
  • a statistically higher probability of finding molecules with the suitable energy amount for condensing at the surface results.
  • a turbulent gas stream is used, as is conventionally provided from a compressor and in particular a turbo compressor, an extremely steep temperature gradient results and condensing is thus strongly obstructed.
  • FIG. 3 shows turbulent water (fluid) on a condenser to increase the condenser power.
  • FIG. 5 An arrangement of a device, which is also referred to as a gas trap 50 , in the liquefier 51 of a heat pump is illustrated in FIG. 5 .
  • FIG. 5 shows a heat pump in which the liquefier is arranged on top of an evaporator although this arrangement does not necessarily have to be used to implemented a gas trap.
  • Water vapor enters a compressor 53 via a first gas channel 52 and is compressed there and output via a second gas channel 54 .
  • the discharged gas i.e.
  • the compressed and thus hot water vapor is advantageously directed to condenser water through an inventive laminarization means 55 which may, for example, be implemented in a honeycomb shape or in another way, wherein the condenser water runs off to the side via a condenser water channel 56 via a plate-shaped or funnel-shaped condenser drain 57 .
  • the condenser drain 57 is typically rotationally symmetric and provided with an inventive turbulence generator 58 to increase the condenser efficiency.
  • a sealing lip 59 is provided which separates the bottom gas area 60 from the top gas area 61 .
  • the sealing lip 59 does not necessarily have to provide a complete sealing. It guarantees, however, that the foreign gas transported by the condenser water on the condenser 57 accumulates below the condenser drain 57 in the area 60 .
  • a diffusion process acts against gravity, insofar as also the foreign gases want to have the same concentration in the area 60 and in the gas trap. This diffusion process thus acts against the gravity effect of the gas trap.
  • the effect of the sealing lip 59 which separates the area above the condenser drain or the condenser funnel 57 from the area below this element 57 , is increased by the fact that the laminarization means 55 is present, as thus the foreign gases, as soon as they meet the water current 56 on the liquefier drain 57 , may not leave again, but are forced, so to speak, to pass in the direction of the sealing lip and below the sealing lip to accumulate in the proximity of the gas trap 50 .
  • This performance is even increased by the turbulence generator 58 as then a more turbulent current exists which also has a higher efficiency, so to speak, to trap and carry foreign gas which is in the top area 61 .
  • FIG. 6 a shows a basic illustration of the functionality which was illustrated in respect of the heat pump or the heat pump liquefier 51 of FIG. 5 .
  • FIG. 6 a it is particularly emphasized how the space 260 below the drain 57 is separated from the top area 61 by the sealing lip 59 .
  • This separation does not have to be hermetic as long as a higher probability exists that foreign gases follow the turbulent water vapor, which was, however, laminarized by the laminarizer 55 , as is illustrated by arrows 69 , on the path into the lower area 60 , as is indicated by an arrow 68 , with a higher probability in comparison to the probability that the foreign gases again enter the top area 61 .
  • an accumulation of foreign gases will take place, so that the diffusion effect is, so to speak, reduced from the gas trap 50 and the efficiency of the gas trap is not substantially affected.
  • the gas trap has a relatively long neck 70 which extends between the accumulation container 71 and an existing inlet area 72 which may be funnel-shaped. However, it is not the length of the neck 70 that is important, but that at least the bottom part of the accumulation container 10 is arranged in a cold area, like, for example, the evaporator 2 of the heat pump. This means that warm water vapor from the area 60 of the liquefier comes into contact with a cold surface of the accumulation container 1 , which leads to a condensation of the water vapor.
  • a continuous water vapor current into the funnel 72 along the neck 70 into the accumulation container results, as the water vapor in the area 50 condenses at the cold wall of the accumulation container arranged in the evaporator 2 .
  • the thus resulting current into the gas trap serves, on the one hand, to carry also foreign gases into the accumulation container and at the same time serves to accumulate water in the accumulation container which may then be heated up by the pressure generating means 1 in the form of a heating coil to cause the vapor output.
  • a laminarization means 73 is arranged, like, for example, in the form of a honeycomb-shaped structure in order to improve the efficiency of the gas trap.
  • the implementation of arranging a wall of the accumulation container 10 in the evaporator, or, generally speaking, at a cold location of the system, is especially advantageous when the heat pump is implemented such that the liquefier is arranged above the evaporator.
  • the neck 70 reaches through the liquefier downwards into the evaporator to provide a cold condensation wall which, on the one hand, leads to a continuous gas stream into the gas trap and, on the other hand, causes water to be present in the gas trap, which may be heated to increase the pressure in the accumulation container such that at certain events a discharge of foreign gas may take place.
  • FIG. 7 shows a schematical illustration of a heat pump for heating a building.
  • the heat pump for heating a building is implemented such that detached houses or small apartment houses may be heated.
  • the heat pump for heating buildings according to one embodiment of the present invention is to be implemented to heat small apartment houses with less than 10 apartments and advantageously less that 5 apartments.
  • the heat pump includes an evaporator with an evaporator housing 42 ′ with turbulence generators. The vapor generated in the evaporator is supplied via a vapor line 100 to a compressor 102 .
  • the compressor 102 compresses the vapor and leads the compressed vapor via a vapor line for compressed vapor, designated by 104 , into an inventive condenser having a condenser housing 43 ′ which comprises either turbulence generators or a laminarizer or advantageously both means to acquire a more efficient condensation.
  • the evaporator receives the liquid to be evaporated via a supply line 106 and the condenser discharges the condensed liquid via a discharge line 108 .
  • the condenser 43 comprises a forward flow 110 a with temperatures, for example, in a range of 40° for floor heating and a return flow 110 b from the heating system of the building.
  • the same liquid may flow as in the condenser without a heat exchanger being provided.
  • a heat exchanger may be provided so that the forward flow 110 a and the return flow 100 b lead to a heat exchanger not illustrated in FIG. 7 and not into an actual radiator.
  • the discharge line 108 in the case of an open system, may lead into an open water reservoir, like, for example, ground water, sea water, saline water, river water, etc.
  • the supply line 106 may come from underground water, sea water, river water, saline water, etc.
  • a closed system may be used, as is indicated by the dashed connecting lines to a connecting element 110 .
  • the connecting element 110 guarantees that the liquid condensed in the condenser is again supplied into the evaporator, wherein corresponding pressure differences are considered.
  • the liquid 106 in the supply line carries heat from the underground water, it is not underground water, wherein in this case a heat exchanger is arranged in an underground water reservoir to heat up the circulating liquid in the line 106 , which is then implemented as a go and return line so that the heat transmitted by the underground water is brought into the heating forward flow 110 a via the heat pump process.
  • the operating liquid in the evaporator and in the condenser is water.
  • other operating liquids may be used, like, for example, heat-carrier liquids provided especially for heat pumps.
  • Water is, however, advantageous due to its special suitability for the process.
  • a further substantial advantage of water is that it is carbon neutral.
  • the evaporator 42 is provided with an evaporator housing which is implemented to maintain a pressure in the evaporator at least in the environment of the evaporator surface at which the water flowing in the supply line 106 evaporates. If water is used as the operating liquid, pressures in the evaporator will be below 30 mbar and even in a range below 10 mbar.
  • pressures will be at more than 40 mbar and below 200 or 150 mbar.
  • a condenser housing is implemented to maintain the respective pressures. Pressures at condensation temperatures of 30° C. or below or 22° C. or below are advantageous.
  • FIG. 8A shows a top view onto an evaporator or condenser with wire sections as turbulence generators
  • FIG. 8B shows a longitudinal section of the evaporator, which, analogous to this, may also be the condenser if corresponding forward/return lines, etc. are considered and the condenser liquid is not externally supplied and drained but circulates.
  • the evaporator includes an evaporator surface or condenser surface 80 arranged on the turbulence generators 40 .
  • the turbulence generators 40 are individual wire sections, together implemented, for example, as a spiral 82 . Simultaneously, the turbulence generators may also be more or less concentric wire rings separate from each other, but the use of a spiral is easier with regard to handling and assembly.
  • adjacent wire sections 84 a, 84 b which each have a diameter of d are spaced apart by a distance D d , wherein the distance D d is greater than the diameter d of a wire section and advantageously smaller than three times the diameter.
  • the wire sections in FIG. 8A are plotted having a circular cross-section, the cross-section of the wire sections is arbitrary.
  • FIG. 8B shows a funnel-shaped evaporator or condenser or a funnel-shaped evaporator surface or condenser surface 80 .
  • the wire sections are mounted directly on this surface 80 .
  • the wire sections may also be spaced apart, as long as a relative positioning of the turbulence generators 40 with respect to the surface 80 is provided which is such that it acts upon the operating liquid present on the surface 80 by means of the turbulence generators, so that turbulences result.
  • the surface 80 both for the evaporator and also for the condenser, is shaped such that the operating liquid which is supplied via an operating liquid supply line 86 not only stands still on the surface 80 , which would be the case if the surface were completely horizontal and a virtually non-existing supply line were present, but that the operating liquid also flows on the surface due to gravity.
  • the surface 80 includes at least one inclined plane.
  • the surface is funnel-shaped and the supply opening 86 is in the center or arranged with respect to the operating surface such that the operating liquid is not only drained at one side with respect to the supply opening, but flows off to all sides.
  • a level area exists which is arranged as an inclined plane and where, at the highest point, the intake or supply line 86 is arranged so that the operating liquid is not on several sides of the intake but basically in a limited sector, like, for example, 30°, 60° or 90° with respect to the intake on the surface, in order to cause an effect there by the turbulence generators 40 .
  • the operating surface may also be pyramid-shaped or conical or uneven or curved in its cross-section as long as the operating liquid, in the operating position of the evaporator or condenser, overcomes a height difference due to the effect of gravity.
  • FIGS. 9A and 9B show a top view onto an alternative surface 80 of an evaporator or condenser, wherein no wire sections as in FIG. 8A exist but elevations or indentations exist in the operating surface.
  • FIG. 9B only elevations are illustrated.
  • the indentations will be implemented similarly but, so to speak, “negatively” with respect to the illustrated elevations.
  • the turbulence generators 40 protrude from the surface or are set back from the surface, i.e. practically as “holes” in the surface 80 , wherein the turbulence generators 40 protrude so far over the surface that they protrude, at least with their tip, beyond a level of the operating liquid 41 on the surface 80 .
  • the turbulence generators 40 may have any shape, as indicated in FIG. 9B .
  • the turbulence generators may also be implemented to achieve, using special forms, a “separation” and “folding” of the water current.
  • the turbulence generators may, for example, also be implemented by elements reaching into the operating liquid, like, for example, bars, etc. which are not firmly connected to the surface 80 but are suspended above the surface 80 , for example. These bars may also be moved, depending on the implementation, to generate extremely strong turbulences. Turbulences may thus be generated in many ways, wherein turbulence generators, in order to generate these turbulences, may be firmly connected with the operating surface 80 or also be positioned in a static or dynamic way with respect to the operating surface as long as, advantageously, at least 20% of the overall water current is provided with turbulences.
  • FIG. 10A shows a cross-section through a laminarizing means having different laminarizing cells 120 .
  • turbulent vapor with a temperature ⁇ D exists, as is schematically indicated by the undirected vapor arrows 122 .
  • vapor 122 made laminar is illustrated 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 ⁇ w .
  • ⁇ w is lower than ⁇ D .
  • the temperature of the undirected vapor ⁇ D may be far higher than the temperature of the water ⁇ w . Still, no vapor coolers, etc. are needed, as the laminarizer 48 with the individual laminarizer cells 120 separated from each other by walls 121 enforces the temperature distribution illustrated in FIG. 10 b .
  • the laminarizer is honeycomb-shaped or made of a tube material, as long as individual laminarizer cells 120 exist which are directed in a more or less parallel way and are smooth on the inside and which cause a laminarization as is illustrated by the directed vapor current 124 .
  • the laminarizer does not necessarily have to achieve a perfect 100% laminarization as long as the gas current at the output of the laminarizer is less turbulent than the gas stream at the input of the laminarizer.
  • the laminarizer cells or the whole laminarizer is implemented so that the output vapor current made laminar is at least half as turbulent as the turbulent vapor current on the input side.
  • the length of a laminarizer cell 120 For use in a condenser for a heat pump operated with water as the operating liquid, it is advantageous for the length of a laminarizer cell 120 to be approximately 10 mm long if the diameter of the laminarizer cell is 5 mm. The larger the diameter of an individual cell, the longer also the length L ought to be, so that also with larger diameters a sufficient laminarization is achieved. At the same time, with smaller diameters there is a lower limit of the length in order to prevent a nozzle effect occurring which may lead to a de-laminarization. To keep the flow resistance for the vapor as low as possible, it is advantageous to provide a large laminarizer area and to implement the thickness of the walls 121 between the laminarizer cells 120 in FIG. 10A as low as possible.
  • the length is longer than 1 mm.
  • Other favorable exemplary dimension are: if the diameter is 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 output of the laminarizer cells 120 and the surface of the liquid is advantageous to be relatively small and in particular smaller than 50 mm, advantageously smaller than 25 mm or advantageously smaller than 6 mm. It is thus also enforced that the gas or the evaporated operating liquid when it leaves the laminarizer cells has a temperature which is virtually equal to or only slightly higher than the temperature of the water. It is thus guaranteed that the vapor particles in the current do not “bounce off” the water or again act as vapor generators but are integrated into the water by condensation, as only in this way an especially efficient heat transmission from vapor to water may take place.
  • the inventive laminarizer provides a substantial increase of the efficiency when condensing.
  • the efficiency of power per area strongly decreased the higher the temperature of the vapor with respect to the temperature of the condenser liquid. It may thus be said that, when overheating the vapor by 10°, only 10% of the condenser power was possible. This consequently led to condenser powers of 2-3 kW per m 2 for a typical surface condensation or evaporation.
  • condenser powers of 2-3 kW per m 2 for a typical surface condensation or evaporation.
  • With the same area a substantially higher power is achieved depending on the implementation of 40-200 kW/m 2 or even more. This means increasing the efficiency by a factor of 20 with simple means.
  • a further advantage is that the efficiency is relatively independent of the temperature of the undirected vapor.
  • the compressor may be dimensioned according to its requirements, and it does not have to be considered in the dimensioning of the compressor according to the present invention which thermal conditions are needed for condensing.
  • the turbulence generators and the laminarizing means may not be implemented as two separate elements but also as one and the same element.
  • a fiber tissue or a fiber mat advantageously made of non-absorbent fibers may be placed onto the evaporator surface or the condenser surface, wherein the surface of the fiber tissue protrudes from the level of the liquid, advantageously by more than 3 mm and in particular by more than 5 mm.
  • the liquid flows around the fibers, whereby turbulences are generated.
  • the washed-around fibers represent the turbulence generators.
  • the fibers protruding from the liquid which are not washed-around do, however, represent the laminarization means.
  • the friction of the vapor at the fibers leads to a laminarization of the vapor.
  • the material of the fibers is plastic or metal, and the fiber tissue is, for example, metallic wool or, in particular, 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)
US12/976,230 2008-06-23 2010-12-22 Device and Method for an Efficient Surface Evaporation and for an Efficient Condensation Abandoned US20110146316A1 (en)

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EP (1) EP2307824B1 (fr)
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110100032A1 (en) * 2008-01-18 2011-05-05 Holger Sedlak Apparatus and Method for Removing a Gas from a System, System for Vaporizing and Heat Pump
US20110107789A1 (en) * 2008-04-01 2011-05-12 Holger Sedlak Liquefier for a Heat Pump and Heat Pump
US9732994B2 (en) 2008-06-23 2017-08-15 Efficient Energy Gmbh Device and method for an efficient surface evaporation and for an efficient condensation
US20180363960A1 (en) * 2016-03-02 2018-12-20 Efficient Energy Gmbh Heat pump having a foreign gas collection chamber, method for operating a heat pump, and method for producing a heat pump
US20220120477A1 (en) * 2019-07-08 2022-04-21 Efficient Energy Gmbh Cooling device, method for manufacturing a cooling device, and transport device having a cooling device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008016627A1 (de) * 2008-04-01 2009-10-08 Efficient Energy Gmbh Verflüssiger für eine Wärmepumpe, Wärmepumpe und Verfahren zum Herstellen eines Verflüssigers
GB2540425B (en) * 2015-07-17 2017-07-05 Sage & Time Llp A gas conditioning system
DE102017205020A1 (de) * 2017-03-24 2018-09-27 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Reaktionsvorrichtung mit Wärmetauscher und deren Verwendung

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2321964A (en) * 1941-08-08 1943-06-15 York Ice Machinery Corp Purge system for refrigerative circuits
US3175962A (en) * 1961-02-28 1965-03-30 Gen Electric Falling film evaporator
US3279525A (en) * 1964-05-06 1966-10-18 Takahashi Taiichi Falling fluid heat exchanger and evaporator
US5992512A (en) * 1996-03-21 1999-11-30 The Furukawa Electric Co., Ltd. Heat exchanger tube and method for manufacturing the same
US6018963A (en) * 1994-07-01 2000-02-01 Hitachi, Ltd Refrigeration cycle
US20040231351A1 (en) * 2003-05-19 2004-11-25 Wyatt William Gerald Method and apparatus for extracting non-condensable gases in a cooling system
US20050274139A1 (en) * 2004-06-14 2005-12-15 Wyatt William G Sub-ambient refrigerating cycle
US7121328B1 (en) * 2000-01-18 2006-10-17 General Electric Company Condenser
US20070245759A1 (en) * 2006-04-04 2007-10-25 Holger Sedlak Heat pump
US20090217680A1 (en) * 2005-07-11 2009-09-03 Stefan Petersen Method for discharging a gas from a heat pump, and heat pump
US20110100032A1 (en) * 2008-01-18 2011-05-05 Holger Sedlak Apparatus and Method for Removing a Gas from a System, System for Vaporizing and Heat Pump

Family Cites Families (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH378290A (de) * 1960-01-29 1964-06-15 Wiegand Apparatebau Gmbh Verfahren und Vorrichtung zur gleichmässigen Verteilung der einzudampfenden Flüssigkeit auf die Heizrohre eines Fallstromverdampfers
US3438711A (en) * 1964-01-21 1969-04-15 Beckman Instruments Inc Burner system with heated spray chamber for spectroscopic analysis
DE2417163C3 (de) * 1974-04-09 1981-08-13 Ludwig Taprogge Reinigungsanlagen für Röhren-Wärmeaustauscher, 4000 Düsseldorf Kondensator für eine Dampfan-Wasser-Kondensation
DE2422096A1 (de) * 1974-05-07 1975-11-20 Kraftwerk Union Ag Verfahren zur kondensation von dampf und einrichtung zur durchfuehrung des verfahrens
JPS60147067A (ja) * 1984-01-10 1985-08-02 協和醗酵工業株式会社 ヒ−トポンプ
US4898152A (en) * 1984-12-18 1990-02-06 Kahl Karl H Dual sequence solar water heater
DD245032A1 (de) 1985-12-23 1987-04-22 Inst Energieversorgung Einrichtung zum entlueften von behaeltern, vorzugsweise in absorptionsanlagen
JPS62156208A (ja) 1985-12-27 1987-07-11 Mitsui Toatsu Chem Inc 強磁性金属粉末
JPS62156208U (fr) * 1986-03-26 1987-10-03
US5428966A (en) * 1988-01-21 1995-07-04 Alsenz; Richard H. Refrigeration system utilizing an expansion device in the evaporator
JPH01217168A (ja) 1988-02-24 1989-08-30 Hitachi Ltd 冷凍機の不凝縮ガス抽気装置
JPH01305292A (ja) * 1988-05-31 1989-12-08 Toshiba Corp 直接接触式凝縮器
FR2654502A1 (fr) * 1989-11-14 1991-05-17 Pechiney Recherche Procede et dispositif d'echange thermique avec film ruisselant.
HU206409B (en) 1990-07-18 1992-10-28 Energiagazdalkodasi Intezet Mixing condensator
WO1992015833A1 (fr) * 1991-03-11 1992-09-17 Modine Manufacturing Company Condenseur a passage d'ecoulement de diametre hydraulique reduit
JPH04316972A (ja) 1991-04-15 1992-11-09 Hitachi Ltd 冷凍機の抽気ガス純化装置
US5458191A (en) * 1994-07-11 1995-10-17 Carrier Corporation Heat transfer tube
US5590537A (en) 1995-09-07 1997-01-07 The Perkin-Elmer Corporation Dry gas curtain for cryogenic surface
JP3050795B2 (ja) * 1996-03-21 2000-06-12 古河電気工業株式会社 伝熱管
JP2000227265A (ja) * 1999-02-03 2000-08-15 Denso Corp 受液器一体型冷媒凝縮器
JP2001050618A (ja) 1999-08-06 2001-02-23 Mitsubishi Heavy Ind Ltd 不凝縮ガス抽気装置及びこれを有する冷凍機
JP3592976B2 (ja) 1999-11-26 2004-11-24 三菱重工業株式会社 抽気装置、及び、吸収冷凍機
US6655207B1 (en) * 2000-02-16 2003-12-02 Honeywell International Inc. Flow rate module and integrated flow restrictor
US20040010913A1 (en) * 2002-04-19 2004-01-22 Petur Thors Heat transfer tubes, including methods of fabrication and use thereof
DE10310748B3 (de) 2003-03-10 2004-08-05 Viessmann Werke Gmbh & Co Kg Verfahren zum Entfernen von Fremdgasen aus einer Vakuum-Sorptionsvorrichtung sowie eine Vakuum-Sorptionsvorrichtung zur Durchführung des Verfahrens
JP2004293872A (ja) 2003-03-26 2004-10-21 Tokyo Electric Power Co Inc:The ヒートポンプ及び熱利用装置
KR100971060B1 (ko) * 2005-10-18 2010-07-20 캐리어 코포레이션 물 가열을 위한 절약형 냉매 증기 압축 시스템
US20120180987A1 (en) * 2007-09-19 2012-07-19 Carrier Corporation Condenser having a sub-cooling unit
EP2307824B1 (fr) 2008-06-23 2016-04-06 Efficient Energy GmbH Procédé et dispositif de condensation efficace

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2321964A (en) * 1941-08-08 1943-06-15 York Ice Machinery Corp Purge system for refrigerative circuits
US3175962A (en) * 1961-02-28 1965-03-30 Gen Electric Falling film evaporator
US3279525A (en) * 1964-05-06 1966-10-18 Takahashi Taiichi Falling fluid heat exchanger and evaporator
US6018963A (en) * 1994-07-01 2000-02-01 Hitachi, Ltd Refrigeration cycle
US5992512A (en) * 1996-03-21 1999-11-30 The Furukawa Electric Co., Ltd. Heat exchanger tube and method for manufacturing the same
US7121328B1 (en) * 2000-01-18 2006-10-17 General Electric Company Condenser
US20040231351A1 (en) * 2003-05-19 2004-11-25 Wyatt William Gerald Method and apparatus for extracting non-condensable gases in a cooling system
US20050274139A1 (en) * 2004-06-14 2005-12-15 Wyatt William G Sub-ambient refrigerating cycle
US20090217680A1 (en) * 2005-07-11 2009-09-03 Stefan Petersen Method for discharging a gas from a heat pump, and heat pump
US20070245759A1 (en) * 2006-04-04 2007-10-25 Holger Sedlak Heat pump
US20110100032A1 (en) * 2008-01-18 2011-05-05 Holger Sedlak Apparatus and Method for Removing a Gas from a System, System for Vaporizing and Heat Pump

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110100032A1 (en) * 2008-01-18 2011-05-05 Holger Sedlak Apparatus and Method for Removing a Gas from a System, System for Vaporizing and Heat Pump
US20110107789A1 (en) * 2008-04-01 2011-05-12 Holger Sedlak Liquefier for a Heat Pump and Heat Pump
US8978408B2 (en) 2008-04-01 2015-03-17 Efficient Energy Gmbh Liquefier for a heat pump and heat pump
US9709305B2 (en) 2008-04-01 2017-07-18 Efficient Energy Gmbh Liquefier for a heat pump and heat pump
US9732994B2 (en) 2008-06-23 2017-08-15 Efficient Energy Gmbh Device and method for an efficient surface evaporation and for an efficient condensation
US20180363960A1 (en) * 2016-03-02 2018-12-20 Efficient Energy Gmbh Heat pump having a foreign gas collection chamber, method for operating a heat pump, and method for producing a heat pump
US11079146B2 (en) * 2016-03-02 2021-08-03 Efficient Energy Gmbh Heat pump having a foreign gas collection chamber, method for operating a heat pump, and method for producing a heat pump
US20220120477A1 (en) * 2019-07-08 2022-04-21 Efficient Energy Gmbh Cooling device, method for manufacturing a cooling device, and transport device having a cooling device

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US20140075978A1 (en) 2014-03-20
ES2575686T3 (es) 2016-06-30
EP2307824B1 (fr) 2016-04-06
EP2307824A2 (fr) 2011-04-13
WO2009156125A3 (fr) 2010-06-10
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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