EP3500807B1 - Évaporateur hybride - Google Patents

Évaporateur hybride Download PDF

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Publication number
EP3500807B1
EP3500807B1 EP17748788.1A EP17748788A EP3500807B1 EP 3500807 B1 EP3500807 B1 EP 3500807B1 EP 17748788 A EP17748788 A EP 17748788A EP 3500807 B1 EP3500807 B1 EP 3500807B1
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EP
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Prior art keywords
evaporator
working fluid
working
gas bubbles
fluid
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German (de)
English (en)
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EP3500807A1 (fr
Inventor
Alexander WARLO
Lena Schnabel
Rahel VOLMER
Gerrit FÜLDNER
Jörg Weise
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Fraunhofer Gesellschaft zur Forderung der Angewandten Forschung eV
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Fraunhofer Gesellschaft zur Forderung der Angewandten Forschung eV
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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/026—Evaporators specially adapted for sorption type systems
    • 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
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt

Definitions

  • the invention relates to a hybrid evaporator with an evaporator structure forming a heat transfer surface and a working medium reservoir containing a working fluid, the evaporator structure having a coolant flow and a method for operating such an evaporator.
  • the working liquid is also referred to as the working medium or refrigerant.
  • Such evaporators are used either in refrigerating machines or in heat pumps.
  • the evaporator structure is cooled by the working liquid evaporating at the evaporator structure.
  • the vaporized working liquid is first adsorbed on an adsorber.
  • the loaded adsorber is brought to a higher temperature level, whereupon the working liquid is desorbed again and condensed in a condenser as condensate.
  • the cooling of the evaporator structure is used for a technical application
  • the heating of the condenser and/or the adsorber is used for a technical application.
  • the evaporator structure is therefore also referred to as a heat exchanger or heat exchanger structure.
  • the flow of useful heat can be extracted from the air conditioning machine by a coolant flow through the evaporator structure. A closed circuit of the coolant is realized in this way.
  • Such air conditioning machines which can be designed as adsorption chillers or heat pumps, for example So the working medium cyclically evaporated and adsorbed or desorbed and condensed.
  • chillers can have a sorber and a component that combines condenser and evaporator structure, such as in EP 1 278 028 B1 disclosed.
  • the evaporator structure is then operated alternately as an evaporator and condenser. This means that the working liquid is evaporated at the evaporator and, after adsorption and desorption at the sorber, is condensed again at the evaporator at the condensation temperature in alternating sequence.
  • heat exchangers for evaporation/condensation have been used in adsorption heat pumps and chillers, which work according to the principle of partially flooded pool evaporation, sometimes also in connection with capillary structures, on the surface of which the working liquid evaporates from thin films.
  • air-conditioning machines designed as absorption chillers mostly sprinkled tube bundles are used as an evaporator or heat exchanger structure.
  • the heat exchanger structure is sprinkled or sprayed with refrigerant from above.
  • the refrigerant forms a thin film (trickling film) on the heat exchanger structure, on the surface of which it evaporates.
  • a widely used approach in adsorption chillers and heat pumps is partially flooded operation, such as in the DE 100 33 972 B4 disclosed.
  • the evaporator structure is partially flooded by the working liquid, ie partially immersed in the sump (structural flooding).
  • structural flooding thin films of the working fluid can be produced on the heat transfer surface, which have a low thermal resistance.
  • the wetting of the heat transfer surface with working liquid takes place, for example, in the DE 10 2008 028 854 A1 by utilizing the capillary effect.
  • the heat transfer surface is formed by a low-finned tube and thus forms a capillary structure.
  • the capillary structure fulfills a dual function during the evaporation of the working liquid: on the one hand, it causes an increase in the heat-transferring surface; on the other hand, the capillary effect pulls the refrigerant against the gravitational force onto the capillary structure and distributes it evenly there.
  • the working liquid evaporates from the very thin films created in this way along the so-called 3-phase boundary between vapour, liquid and metal.
  • the DE 10 2011 015 153 A1 discloses an in situ storage of working fluid during the condensation/desorption phase on horizontal heat transfer surfaces, such as exist in lamellar heat exchangers. During the evaporation/adsorption phase, the working liquid present on the structure is evaporated again. The problem with this approach is that the working liquid also condenses in places where it does not form a thin film but completely fills structural areas, partially drips off and can therefore not be thermally activated or can only be activated with a very high thermal resistance.
  • the WO 2016/059777 A1 discloses a sealed container having various sections. These are designed as adsorbers, evaporators and condensers for the working fluid in the sealed container.
  • the EP 1 645 819 A1 relates to a vacuum sorption device comprising a sorber which periodically adsorbs or desorbs a refrigerant, an evaporator and a condenser which are arranged together in a vacuum housing. According to this disclosure, it is provided that the vacuum housing has an at least double-walled area that forms the capacitor.
  • a hybrid evaporator according to the preamble of claim 1 and a method for operating a hybrid evaporator in which a refrigerant is provided in a reservoir of an evaporator device of a single-stage or multi-stage refrigeration system and a fluid to be cooled is cooled by using a heat exchanger of Evaporator device for cooling a cooling heat transfer from the fluid to be cooled to the refrigerant takes place, and the refrigerant evaporates at least partially on the heat exchanger due to the cooling heat transfer.
  • the vaporized refrigerant is fed to a liquefaction device.
  • the evaporation of the working liquid takes place by still boiling, which is understood to mean boiling without the formation of bubbles.
  • silent (convective) boiling with refrigerant films larger than 1 mm the heat transfer during evaporation is essentially limited by the transport of heat through the refrigerant film.
  • the greater the film thickness the greater the heat transfer resistance to be overcome.
  • the thermal resistances are very high, since only the water surface contributes to the evaporation. For the best possible heat transfer Therefore, very small film thicknesses of the working liquid on the heat transfer surface of the evaporator structure are sought.
  • the evaporation of water as a pure substance takes place in a temperature range from 0°C to 30°C.
  • the pressures are correspondingly low in the range from 0.006 bar (0°C) to 0.042 bar at 30°C.
  • water as a pure substance is cyclically transferred from the solid to the gaseous phase in a temperature range from ⁇ 10° C. to 0° C.
  • the density difference between the liquid and the vapor phase is very large. At 10°C the density of the liquid phase is 999.7 kg/m 3 , that of the gaseous phase 0.0094 kg/m 3 . This results in a density quotient of around 100,000.
  • the large density quotient in particular must be taken into account by designs in which boiling is not carried out in the flow but in a free volume in order to keep pressure losses low and to avoid the blockage of the heat exchanger with vapor cushions that do not escape due to the high pressure loss.
  • water as the working fluid in the pressure and temperature range described requires wall superheating of more than 20 K on smooth surfaces and at least 7 K on structured surfaces in order to set continuous nucleate boiling with high heat transfer coefficients.
  • Wall overheating of the magnitude mentioned cannot be implemented in heat pump or refrigeration technology applications, since high wall overheating is synonymous with increased cold water temperatures or reduced boiling pressures, which have an unfavorable effect on the required compression ratio or the sorption pressure and thus on the efficiency of the cycle process. This is in particular for water, the freezing point is another limiting operating variable.
  • the object of the present invention is to provide a hybrid evaporator and a method for operating a hybrid evaporator which reduces the disadvantages of the prior art, with the intention in particular to enable an improvement in performance with driving temperature differences comparable to the prior art.
  • gas bubble means a vapor bubble generated by the bubble generation structure in the reservoir of the working liquid and rising in the working liquid.
  • the heat exchanger concept implemented according to the invention serves as an evaporator, particularly in refrigeration machines and heat pumps, and can therefore be used, for example, in sorption systems in low-pressure applications, but also for distributing trickling films, for example in absorption processes.
  • a thin liquid film of the working liquid can thus be formed on the heat transfer surface of the evaporator structure, which can be evaporated almost completely and offers a low thermal resistance between the heat transfer surface and the adjacent surface of the working liquid.
  • heat can be introduced into the working liquid sump, which leads to the formation of gas bubbles locally.
  • the refrigerant sprayed as a result i.e.
  • the working liquid hits the evaporator structure and forms the desired thin liquid film there.
  • the formation of bubbles in the working liquid sump and thus the evaporation capacity can be adjusted by controlling a heating output. If the pressure is low, there may be a strong splashing of the working liquid.
  • the heat output can be brought in, for example, by constant basic heating and regulation by a second, additional heat source and/or by spot heating, e.g. an electrical resistance.
  • the evaporator structure can thus be structurally separate from the bubble generation structure in such a way that the energy introduced by the bubble generation structure into the working medium reservoir to generate the gas bubbles is at least essentially is independent of the temperature of the cooling liquid in the cooling liquid passage of the evaporator structure and/or can be controlled.
  • the evaporator structure of the air conditioning machine according to the invention thus contains at least two structural areas, one structural area being flooded or at least partially flooded as a bubble generation structure in the working medium reservoir and being designed in such a way that nucleate boiling can be initiated on the outside of the structure. Due to the high density quotient between liquid and vapor, gas bubbles generated as vapor bubbles reach a large volume, which leads to a strong entrainment of the working liquid when the gas bubbles detach and rise.
  • the working fluid Due to the nucleate boiling, the working fluid squirts out of the working fluid reservoir and, in the second structural area designed as an evaporator structure, hits its heat transfer surface, which is designed as the outside of a heat exchanger, which is designed due to its geometric structure in such a way that the working fluid is distributed over a large area and from the resulting thin films.
  • the evaporator structure to be wetted in this way can be arranged above the bubble generation structure or also to the side of it. It can be fully or partially immersed in the working fluid sump. In the event of partial immersion, at least if capillary active distribution structures are present on the surface of the evaporator structure, additional suction of the working liquid from the working medium sump can be effected. No pump is required within the vacuum system, ie the system in which the working liquid is evaporated. As a result, no mechanically moving components have to be present, so that a long service life can result. Furthermore, a simple regulation of the air conditioning machine via the energy supply of the bubble generation structure.
  • Controllable wetting of the heat transfer surface with thin working liquid films is made possible, so that high heat transfer coefficients can be achieved. No pump and no capillary refrigerant distribution structure is required for this.
  • This provides an evaporator with high power density at low driving temperature differences, in particular for water as the working fluid and other low-pressure working fluids, such as methanol.
  • the results that can be achieved with the air conditioning machine according to the invention with the evaporation of thin, trickling, ie generated from the sprayed working fluid, water films achieve at least 15% higher performance compared to capillary generated water films with comparable driving temperature differences.
  • gas bubbles are generated with a small proportion of the energy required for operation and/or energy extracted from a coolant, the task of which is to distribute coolant, ie working fluid, on the evaporator structure(s).
  • the targeted generation of gas bubbles in the working liquid can be achieved by designing structures or by only supplying energy in phases.
  • the bubble generation structure advantageously has a fluid guide tube for generating the gas bubbles by nucleate boiling.
  • a cooling liquid can be guided through the fluid-guiding tube, from which heat is withdrawn in order to generate the gas bubbles.
  • This can be the same cooling liquid that is conducted through the cooling liquid passage of the evaporator structure. such Heat is withdrawn from the cooling liquid both during the generation of bubbles and during the evaporation of the working liquid.
  • the hydraulic connection of the two fluid-carrying structures ie the cooling liquid passage of the evaporator structure and the fluid-carrying tube of the bubble generation structure, can be implemented either in series or in parallel.
  • the fluid-guiding pipe and the cooling liquid passage are arranged in series in a cooling liquid circuit.
  • the fluid guide tube is first flowed through by the cooling liquid, so that the cooling liquid temperature there is higher than in the cooling liquid passage.
  • the energy for the formation of the gas bubbles i.e. for the formation of bubbles, is thermally supplied to the working medium reservoir by the flow of the cooling liquid circuit formed by the cooling liquid, e.g. a cold water circuit.
  • the thermal energy for generating the gas bubbles is thus introduced directly via the cooling liquid circuit by running through it in series, i.e. the greatest temperature difference between the cooling liquid and the working liquid is then present in the bubble generation structure.
  • a heat exchanger can be used as the bubble formation structure, which is designed in such a way that its cold water inlet area enables bubble-forming overheating.
  • the bubble generation structure can have electrical heating means and/or a heat pipe and/or mechanical means for generating the gas bubbles.
  • the energy for bubble formation can then additionally or alternatively to the thermal supply through the flow of eg cold water circuit or other heat-transporting fluid circuits, by electrical heating elements such as electrical resistors or initiating microwaves and / or heat pipes and / or be supplied by mechanical methods such as shaking and/or introducing ultrasound.
  • electrical heating elements such as electrical resistors or initiating microwaves and / or heat pipes and / or be supplied by mechanical methods such as shaking and/or introducing ultrasound.
  • the wall overheating i.e. the temperature of the outer wall of the bubble generation structure that is in contact with the working liquid, is that of the heat transfer surface of the evaporator structure through which the cooling liquid circuit, e.g. a cold water circuit, is conducted is significantly exceeded, the bubble generation structure is thermally well insulated from the evaporator structure.
  • the bubble generation structure can advantageously have a pipe deflection and/or surface structures to increase heat transfer to the working liquid and/or to improve bubble detachment of the gas bubbles.
  • Surface structures serving to support the formation of gas bubbles and to support the detachment of gas bubbles can form gaps and/or cavities.
  • the fluid-guiding tube can have an inhomogeneous surface finish, in particular partial surface insulation and/or alternating hydrophilic and hydrophobic areas.
  • the gas bubbles forming at the bubble generation structure can grow to a considerable size, e.g., several centimeters. Depending on the installation space, this can cause strong spattering and pronounced convection when the bubble breaks off.
  • bubbles can often be attributed locally to gaps at the structure edge of the bubble generation structure with a gap width of less than 1 mm or to microstructures with good thermal conductivity, e.g. fibers and/or grooves.
  • Such surface structures serve to improve bubble detachment and/or bubble formation.
  • the working liquid can be sprayed, for example, by a targeted geometric arrangement of fluid-carrying pipes or channels of the bubble generation structure and/or structures applied or incorporated into the heat-transferring surface of the bubble generation structure, such as e.g. B. pins, pins, grooves, fabric, perforated films, fibers, sponges, etc. are reinforced.
  • a targeted geometric arrangement of fluid-carrying pipes or channels of the bubble generation structure and/or structures applied or incorporated into the heat-transferring surface of the bubble generation structure such as e.g. B. pins, pins, grooves, fabric, perforated films, fibers, sponges, etc. are reinforced.
  • the working medium is overheated locally at points such as pipe deflections, so that vapor bubbles form there more quickly and working medium sprays out of the working medium reservoir.
  • a further possibility for improving the generation of vapor bubbles is the introduction of poorly thermally conductive materials at the interface between the working liquid and the outer surface of the bubble generation structure, for example a structure through which
  • the bubble generation structure has means for introducing a two-phase flow of the working liquid containing the gas bubbles into the working medium reservoir.
  • the gas bubbles required to spray the working liquid can also be generated by introducing a two-phase flow, which is generated, for example, from the pressure difference in the working liquid between a condenser and the evaporator structure by means of a throttle element.
  • the two-phase mixture forming the two-phase flow flows into the coolant pool, ie the working medium reservoir, from below.
  • the gas bubbles then rising in the working liquid generate the entrainment of the liquid refrigerant, i.e. the working liquid.
  • the evaporator structure advantageously has fins (cooling fins or lamellae) and/or the coolant passage is at least partially plate-shaped for this purpose and/or the coolant passage is at least partially constructed as tubes running parallel to one another.
  • the heat exchanger structure ie the evaporator structure, onto which refrigerant, ie working fluid, is sprayed by the gas bubbles formed, is arranged in such a way that it is easily accessible for the sprayed coolant. This can be implemented, for example, in the form of lamellae aligned vertically or laterally over the working medium reservoir, plates through which flow occurs, or tubes arranged in alignment one above the other.
  • an staggered arrangement of the structure can be formed in the uppermost structural row of an evaporator structure formed in several structural rows arranged one above the other.
  • a terraced arrangement of the rows of structures can also be provided, so that refrigerant flowing off is collected and further distributed evenly.
  • a surface structure and/or a hydrophilic coating and/or a porous layer is applied to the heat transfer surface of the evaporator structure, an improvement in the distribution of the working liquid can be achieved.
  • the heat transfer surface to be wetted is characterized by very good wetting behavior. This can be done either by a surface structuring formed by mechanical structuring in the form of grooves, pins, etc. in a targeted manner, porous layers with a structure height of less than 1 mm and/or by a hydrophilic or contact angle-reducing surface coating and/or chemical pretreatment of the heat transfer surface happen.
  • the heat transfer surface on which the thin film of the working liquid, eg a film of water, evaporates can also have properties that contribute to an even distribution of the working liquid on the one hand, but also to increasing the residence time and mixing of the working liquid on the other.
  • This can be, for example, herringbone-like corrugated structures and/or also structural specifications that can be determined with the design of embossed grooves or applied porous structures, eg fibers, fabric, sponges.
  • Porous particles can be introduced into the working liquid.
  • Such particles embedded in the liquid refrigerant are, in particular, inert, highly porous and good thermally conductive. Due to convection in the working fluid reservoir, these particles are repeatedly thrown to the surface of the working fluid, where they can quickly evaporate refrigerant due to their very large contact area with the vapor space above the working fluid reservoir. The heat required for this is first withdrawn from the particle, which, after entering the liquid, withdraws it from the working liquid and thus, for example, from a cold water circuit. The particles mixed with the refrigerant are moved strongly due to the formation of bubbles. If these particles are inert, highly porous and good thermal conductors, they can quickly release the refrigerant stored in them in the vapor space.
  • the heat extracted from the particle is returned to it as soon as the particle re-enters the working liquid sump and can thus be withdrawn from the cooling liquid circuit, eg a cold water circuit, via the working liquid sump.
  • the evaporator structure can also be integrated into the bottom or the sides of the working medium reservoir.
  • a partially incorporated bubble generation structure is thermally easy to insulate.
  • Fabric structures and/or wire structures can be arranged in the working medium reservoir. If the evaporator structure is partially immersed in the working fluid reservoir, at least if capillary active distribution structures are present on the surface of the evaporator structure, additional suction of the working fluid from the working fluid sump can be effected. With this approach, open-pored fabric or wire structures can be used to distribute the working fluid.
  • the structure carrying the cooling liquid e.g. cold water, can also be incorporated directly into the fabric structure.
  • Beneficial can a working medium conveying tube, which dips into the working medium reservoir with an open end.
  • the distributor structure forms part of the evaporator structure.
  • a funnel-shaped working fluid delivery pipe with the working fluid delivery pipe with an open end, in the case of the funnel shape the wide funnel filling end, immersing itself in the working fluid reservoir, rising gas bubbles can pump the working fluid, i.e. refrigerant, through the working fluid delivery pipe against the force of gravity, so that the Spray area can be increased above the evaporator structure, for example.
  • the working fluid i.e. refrigerant
  • the spray area can be increased above the evaporator structure, for example.
  • liquid refrigerant can be distributed from above onto the heat transfer surface.
  • the liquid coolant can be conveyed to a level above the heat exchanger by means of a narrowing of the cross section of the working medium conveying pipe or other fluid guiding structures and from there can be distributed to the evaporator structure by gravity.
  • a pump is implemented that conveys the liquid refrigerant in a targeted manner to the higher-lying evaporator structure.
  • the mechanical energy required for this is drawn from the thermally driven formation of bubbles and the resulting increase in volume of the refrigerant. This practically does not reduce the efficiency of the evaporation process, since the mechanical energy required to pump a quantity of refrigerant to be evaporated is only a negligible fraction of the heat quantity converted. For example, 1 gram of water lifted 0.1 meter requires 0.001 joules of mechanical energy compared to 2400 joules/gram of vaporization enthalpy. A combination of wetting the evaporator structure from below and above can also be carried out.
  • the driving force of the rising gas bubbles is used to sprinkle the evaporator structure with working liquid from above.
  • a distribution network as a distribution structure that ends in a targeted manner above the evaporator structure or its parts that form the heat transfer surface and is acted upon from above.
  • the distributor structure should be sufficiently porous to allow the vapor of the working liquid present in the gas bubbles to flow to the adsorber without liquid entrainment.
  • elements such as valves, flaps, flow carriers can also be moved.
  • the desorbed working liquid condenses on the evaporator structure is, can on an additional, a capacitor training module can be omitted.
  • the operation of the evaporator structure of an air conditioning machine according to the invention is possible both as a pure evaporator and as a combined evaporator/condenser in one component. In the latter mode of operation, the working liquid condenses on the structures through which fluid actively flows, ie the cooling liquid passage, of the evaporator structure, with excess condensate being able to drip off the non-flooded evaporator structure and collecting in the working medium reservoir in which the second structure, ie the bubble generation structure, is located.
  • An advantage of this design is that even with increasing refrigerant liquefaction, a constant condensation surface is available and all working liquid, even if it condenses in undesired places, can be reactivated or evaporated, since the working medium reservoir is preferably located on the bottom of a component that Working liquid and its vapor includes spatially.
  • a cooling liquid circuit for example a cold water circuit
  • the bubble generation structure by means of which the nucleate boiling is generated, is characterized in that a high heat flow density in the form of wall overheating of more than 10 Kelvin can be applied locally in a very limited manner.
  • the flow of heat and/or energy generated in this way from the bubble generation structure into the working liquid can be generated by thermal or electrical energy or by measures such as shaking, ultrasound, or microwaves.
  • the energy supply is designed in such a way that the heat input into the liquid refrigerant remains low and is limited to the creation of the bubbles.
  • available heat for gas bubble formation can alternatively or additionally be supplied at other temperature levels, ie at different temperature levels than the temperature level of the cooling liquid circuit.
  • available heat for gas bubble formation can alternatively or additionally be supplied at other temperature levels, ie at different temperature levels than the temperature level of the cooling liquid circuit.
  • a significantly higher temperature level and thus higher wall overheating can also be generated than the wall overheating on the heat transfer surface of the evaporator structure provided for the refrigerant evaporation and wetted with a thin film of the working liquid .
  • This supply of heat at a higher temperature level causes only a very small amount of heat input. In this case, a good thermal delimitation of the areas of high wall overheating from the other evaporation areas, ie in particular the evaporation structure, is provided.
  • the energy used to generate the gas bubbles is fed discontinuously to the bubble generation structure by means of a power control module.
  • the energy required to create the bubbles is delivered in phased, pulsating, and/or controlled capacity according to process requirements.
  • FIG 1 an embodiment of an evaporator 1 according to the invention is shown, in which the bubble generation structure 2 has a fluid guide tube 3 .
  • the bubble generation structure 2 arranged in the region of the working medium reservoir 5 is partially in the working medium reservoir 5 collected working fluid 7 flooded.
  • heavily sprayed gas bubbles 8 are generated in the working liquid 7 in a targeted manner.
  • Working liquid 7 entrained in the working liquid 7 rising gas bubbles 8 sprays over the surface 9 of the working liquid 7 in the working medium reservoir 5 into a spray area of the working liquid 7 to introduce the working liquid 7 to generate the gas bubbles 8 by nucleate boiling.
  • An evaporator structure 10 is arranged in the spray area above the working medium reservoir 5 and the partially flooded bubble generation structure 2 arranged therein.
  • the evaporator structure 10 is formed by a pipe forming a cooling liquid passage 11 .
  • the evaporator structure 10 has a heat transfer surface 13 formed from a porous material (porous layer), which is wetted by the working liquid 7 entrained with a working liquid film. The latter is represented symbolically by the gas bubbles 8 impinging on the evaporator structure 10 .
  • the evaporator structure 10 enables areal wetting with thin working fluid films.
  • the working liquid 7 of the working liquid film evaporates, as a result of which the cooling liquid passage 11 and the cooling liquid flowing through it are cooled.
  • the two structures through which fluid flows namely the evaporator structure 10 and the bubble generation structure 2 are spatially arranged one above the other and can cyclically act as evaporator and condenser.
  • the partially flooded bubble generation structure 2 based on tube geometries in this embodiment transfers heat from the cooling liquid flowing through it to the working liquid 7 and can therefore also be referred to as a lower heat exchanger.
  • the hydraulic connection of the two heat exchangers can be serial or parallel. In the figures, only the connections of the cooling liquid lead-through 10 and the fluid guide pipe 3, which also conducts cooling liquid, are indicated.
  • the bubble generation structure 10 can be constructed with different gap distances of the grooves 15 in some embodiments of the invention. Greater overheating can form between narrower gap spacings, as a result of which the generation of the gas bubbles 8 can be localized to specific parts of the longitudinal extent of the fluid-guiding tube 3 .
  • the gap spacings of the grooves 15 are advantageously in a range of less than 1 mm.
  • the grooves 15 thus form surface structures to increase the heat transfer to the working liquid.
  • the increase in the heat transfer to the working fluid can also be achieved by round or flat tubes and deflections arranged close to one another, so that a greater heat input occurs locally.
  • a change in the surface structure e.g.
  • hydrophilic/hydrophobic can support the detachment of gas bubbles.
  • the partial flooding of the bubble generation structure 2 ensures that a sufficiently large working liquid reservoir 5 is available, from which the working liquid 7 squirts out and can thus wet the evaporator structure 10 arranged spatially higher.
  • porous structures have the advantage that they extend the dwell time of the working liquid, but must be thermally well connected to the heat-emitting pipe, ie the cooling liquid duct, and should only have a small thickness of less than 5 mm.
  • Examples of porous structures are metallic fibers, sponges and/or foams. The advantages of these porous structures are high specific surface areas allow good absorption of the splashing working liquid, the good working liquid distribution due to capillary action and the increased thermal conductivity due to the metallic porous structure compared to the thermal conductivity of pure water.
  • the bubble generation structure 2 is incorporated into the working liquid sump, i.e. the working medium reservoir 5, but can also be supplied with working liquid 7 from a working liquid pool, for example, through capillary structures.
  • the working liquid sump can serve as a condensate collection area.
  • the condensate is fed in via a throttle device from the condenser.
  • the pressure difference that is present here which is about 10 to 50 mbar, can also be introduced into the generation of spouting gas bubbles 8 by the targeted introduction of the two-phase flow.
  • the working medium reservoir 5 and the bubble generation structure 2 of the heat exchanger concept according to the invention are preferably arranged on the bottom of a sorption module 17, i.e. below an evaporator structure.
  • This has the advantage that all the working liquid 7 dripping off during the condensation collects in the working liquid sump at the bottom and can be evaporated again there. Consequently, working liquid 7 cannot be lost, i. H. reach places where it is difficult to activate/evaporate.
  • the bubble generation structure 2 has, for example, electrical heating means (pins) for supplying heat to the working liquid 7 .
  • These heating means formed by electrical resistances, for example, represent boiling structures 20 and are arranged at the bottom of the working medium reservoir 5, see above that boiling areas are formed there.
  • the figures show two different arrangements of the boiling areas and evaporator structures 10.
  • the evaporator structure 10 is arranged flat over the working medium reservoir 5 .
  • the heating means are arranged in a distributed manner over the floor of the working medium reservoir 5 .
  • the evaporator structure 10 has cooling fins 22 distributed uniformly along the cooling liquid passage 11 thereof.
  • the heating means of the bubble generation structure 2 are only arranged in the areas with free channel cross sections of the evaporator structure 10 at the bottom of the working medium reservoir 5 . They therefore form locally arranged boiling structures.
  • the evaporator structure 10 has a plurality of partial evaporators, each with a cooling liquid passage 11 comprising cooling fins 22 .
  • the areas between the partial evaporators are referred to as free channel cross-sections.
  • the heating means can also be distributed in the working means reservoir or introduced in the form of a heat exchanger. The heating takes place from the underside or the bottom of the working medium reservoir 5.
  • small electrical heating elements and / or heat pipes can be integrated. If the energy required for gas bubble formation is not supplied by a cold water circuit, the bubble generation structures 2 should be thermally insulated.
  • the heat exchanger to be wetted ie the evaporator structure 10
  • the evaporator structure 10 is arranged in an easily accessible manner above or to the side of the bubble generation structure 2.
  • the evaporator structure 10 is characterized by very good wetting behavior. This can be achieved, for example, by mechanical processing in the form of grooves, pins, purposefully produced roughness and/or by a hydrophilic or contact angle-reducing surface coating and/or chemical pretreatment.
  • FIG 3 an embodiment of an evaporator according to the invention is shown, in which the bubble generation structure 2 has means for introducing a two-phase flow 30 of the working liquid 7 into the working medium reservoir 5 .
  • the nucleate boiling and the associated spraying of the working liquid 7 are not initiated by a fully or partially flooded structure 35 for heating the working liquid 7, but for example by supplying the condensate return flow from a condenser.
  • the rising vapor or gas bubbles 8 ensure that the working liquid 7 is sprayed and that the non-flooded, cooling liquid-carrying evaporator structure 10 or its heat transfer surface is wetted with a film 31 of working liquid.
  • the means for introducing a two-phase flow 30 of the working liquid is in the form of a perforated tube.
  • the structure 35 for example a pipe carrying coolant, is arranged flooded in the working medium reservoir 5 in the illustrated embodiment. This tube can be used to preheat the working fluid 7 in the working fluid reservoir 5 .
  • FIG 4 an embodiment of an evaporator according to the invention is shown, in which a distribution structure 40 is provided in the spray area to collect the working liquid 7 entrained by the gas bubbles 8 and to distribute the working liquid to the heat transfer surface of the evaporator structure 10, and a working medium delivery tube 42 is provided.
  • the working liquid 7 entrained by the gas bubbles 8 does not wet directly, as in the embodiments of FIG Figures 1 to 3 , or only partially directly the heat exchanger surface of the evaporator structure 10, but it is channeled via a distribution system 44 of the distributor structure 40, the wetting generated.
  • the evaporator structure 10 has two partial evaporators, each of a cooling liquid passage 11 with parallel to each other running, heat exchanger surfaces forming fins 22 are formed.
  • the heat transfer surface of the evaporator structure 10 can also be formed, for example, only from the surface of the coolant passage 11 .
  • the distributor structure 40 has a distributor cap embodied as a splash guard 45 for the working fluid and the distribution system 44 embodied, for example, as a fabric and/or a wire structure for distributing the working fluid.
  • the funnel-shaped working medium conveying tube 42 (funnel shape) is used to utilize the buoyancy of the gas bubbles 8 in order to spray or sprinkle the evaporator structure 10 with working liquid 7 from above.
  • the wide, open filling end 47 of the funnel shape is immersed in the working liquid 7 in the working medium reservoir above a heating medium forming the bubble generation structure 2 .
  • the heat is introduced into the working liquid 7 for gas bubble generation by the heating medium.
  • the gas bubbles 8 rising above the heating means in the working liquid 7 are caught by the funnel shape and result in working liquid 7 spraying out of the narrow open end 48 of the funnel shape.
  • the working fluid spouting out into the spray area in this way is deflected downwards by the distributor cap. This leads to a corresponding extension of the spray area to the area of the distribution system 44 and the evaporator structure 10.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (12)

  1. Evaporateur hybride (1) présentant une structure d'évaporation (10), formant une surface de transfert de chaleur (13), et un réservoir de fluide de travail (5) contenant un liquide de travail (7), la structure d'évaporation (10) présentant un conduit de liquide de refroidissement (11),
    dans lequel
    il est prévu une structure de génération de bulles (2),
    la structure de génération de bulles (2) est disposée dans la zone du réservoir de fluide de travail (5) de manière à pouvoir être inondée au moins partiellement par le liquide de travail (7) et/ou à pouvoir être mouillée par le liquide de travail (7), et
    la structure d'évaporation (10) est disposée dans une zone de projection du liquide de travail (7) de telle sorte que la surface de transfert de chaleur (13) peut être mouillée par un film de liquide de travail (31) entraîné par des bulles de gaz (8) susceptibles d'être générées et/ou introduites dans le liquide de travail (7) par la structure de génération de bulles (2) et remontant dans le liquide de travail (7),
    la structure de génération de bulles (2) comprend un tube de guidage de fluide (3) pour la génération des bulles de gaz (8) par ébullition nuclée, et le tube de guidage de fluide (3) et le conduit de liquide de refroidissement (11) sont disposés en série l'un derrière l'autre dans un circuit de liquide de refroidissement,
    caractérisé en ce que
    dans la zone de projection, il est prévu des moyens pour élargir et/ou dévier la zone de projection, comprenant une structure de distribution (40) pour recueillir le liquide de travail (7) entraîné par les bulles de gaz (8) et pour distribuer le liquide de travail (7) sur et/ou par-dessus la structure d'évaporation (10), et
    le liquide de travail (7) contient de l'eau et/ou de l'éthanol et/ou du méthanol ou en est constitué.
  2. Evaporateur hybride (1) selon la revendication 1,
    caractérisé en ce que la structure de génération de bulles (2) comprend en outre au moins un moyen de chauffage électrique et/ou un caloduc et/ou des moyens de génération mécanique des bulles de gaz (8).
  3. Evaporateur hybride (1) selon l'une des revendications 1 à 2,
    caractérisé en ce que la structure de génération de bulles (2) présente une déviation de tube et/ou des structures de surface (15) pour augmenter un transfert de chaleur au liquide de travail (7) et/ou pour améliorer un détachement des bulles de gaz (8), et/ou
    en ce que le tube de guidage de fluide (3) présente un état de surface inhomogène, en particulier des isolations de surface partielles et/ou des zones alternativement hydrophiles et hydrophobes.
  4. Evaporateur hybride selon l'une des revendications 1 à 3,
    caractérisé en ce que la structure de génération de bulles (2) comprend des moyens d'introduction d'un flux diphasique (30) du liquide de travail (7), contenant les bulles de gaz (8), dans le réservoir de fluide de travail (5).
  5. Evaporateur hybride (1) selon l'une des revendications 1 à 4,
    caractérisé en ce que la structure d'évaporation (10) présente des lamelles (22) et/ou des nervures disposées sur le conduit de liquide de refroidissement (11), et/ou
    en ce que le conduit de liquide de refroidissement (11) est réalisé au moins partiellement en forme de plaque, et/ou
    en ce que le conduit de liquide de refroidissement (11) est réalisé au moins partiellement sous forme de tubes s'étendant parallèlement entre eux.
  6. Evaporateur hybride (1) selon l'une des revendications 1 à 5,
    caractérisé en ce qu'une structuration de surface et/ou un revêtement hydrophile et/ou une couche poreuse est appliqué(e) sur la surface de transfert de chaleur (13) de la structure d'évaporation (10).
  7. Evaporateur hybride (1) selon l'une des revendications 1 à 6,
    caractérisé en ce que des particules poreuses sont introduites dans le liquide de travail (7), et/ou
    en ce que des structures tissées et/ou des structures en fil sont disposées dans le réservoir de liquide de travail (5).
  8. Procédé pour faire fonctionner un évaporateur hybride (1) selon l'une des revendications 1 à 7, comprenant les étapes consistant à
    - générer et/ou introduire des bulles de gaz (8) dans le liquide de travail (7) au moyen de la structure de génération de bulles (2) dans le réservoir de liquide de travail (5), laquelle comprend un tube de guidage de fluide (3) pour la génération des bulles de gaz (8) par ébullition nuclée, le tube de guidage de fluide (3) et le conduit de liquide de refroidissement (11) étant disposés en série l'un derrière l'autre dans un circuit de liquide de refroidissement,
    - mouiller la surface de transfert de chaleur (13) de la structure d'évaporation (10) avec du liquide de travail (7) entraîné par des bulles de gaz (8) remontant dans le liquide de travail (7) et projeté dans la zone de projection, et
    - refroidir un liquide de refroidissement traversant le conduit de liquide de refroidissement (11) par évaporation du liquide de travail (7) mouillant la surface de transfert de chaleur (13),
    l'évaporation s'effectuant dans une plage de température de 0°C à 30°C, à des pressions dans la plage de 0,006 bar à 0°C à 0,042 bar à 30°C, ou
    de l'eau en tant que de substance pure étant transférée cycliquement de la phase solide à la phase gazeuse dans une plage de température de -10°C à 0°C, et
    une température de surchauffe de paroi de plus de 20 K étant appliquée sur les surfaces lisses, et d'au moins 7 K sur les surfaces structurées.
  9. Procédé selon la revendication 8,
    caractérisé en ce que, dans une étape suivante du procédé, le liquide de travail désorbé est condensé sur la structure d'évaporation (10).
  10. Procédé selon l'une des revendications 8 ou 9,
    caractérisé en ce que, pour générer les bulles de gaz (8), on utilise moins de 5 % de la quantité d'énergie thermique extraite du liquide de refroidissement lors du refroidissement du liquide de refroidissement traversant le conduit de liquide de refroidissement (11).
  11. Procédé selon l'une des revendications 8 à 10,
    caractérisé en ce que l'énergie utilisée pour générer les bulles de gaz (8) est fournie de manière discontinue à la structure de génération de bulles (2) au moyen d'un module de régulation de puissance et/ou est commandée et/ou régulée en fonction des besoins en puissance de l'adsorbeur.
  12. Procédé selon l'une des revendications 8 à 11,
    caractérisé en ce que le mouillage de la surface de transfert de chaleur (13) de la structure d'évaporation (10) est provoqué en supplément par aspiration du liquide de travail à partir du puisard de fluide de travail au moyen de structures de distribution à activité capillaire.
EP17748788.1A 2016-08-19 2017-08-07 Évaporateur hybride Active EP3500807B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016215591.1A DE102016215591A1 (de) 2016-08-19 2016-08-19 Klimamaschine
PCT/EP2017/069904 WO2018033418A1 (fr) 2016-08-19 2017-08-07 Machine de conditionnement d'air

Publications (2)

Publication Number Publication Date
EP3500807A1 EP3500807A1 (fr) 2019-06-26
EP3500807B1 true EP3500807B1 (fr) 2023-05-03

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EP17748788.1A Active EP3500807B1 (fr) 2016-08-19 2017-08-07 Évaporateur hybride

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EP (1) EP3500807B1 (fr)
DE (1) DE102016215591A1 (fr)
WO (1) WO2018033418A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011053310A1 (de) * 2011-09-06 2013-03-07 Technische Universität Berlin Verfahren zum Betreiben einer Kälteanlage und Kälteanlage

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT411395B (de) 1999-07-07 2003-12-29 Vaillant Gmbh Wärmetauscher
EP1178269B1 (fr) * 2000-08-04 2003-02-19 Vaillant GmbH Pompe à chaleur à absorption
DE10232726A1 (de) 2001-07-21 2003-02-06 Vaillant Gmbh Wärmepumpen-Modul für eine Adsorptionswärmepumpe
DE102004049411B4 (de) * 2004-10-08 2015-06-03 Viessmann Werke Gmbh & Co Kg Vakuum-Sorptionsvorrichtung
DE102008028854A1 (de) 2008-06-19 2009-10-01 Sortech Ag Verdampfer und Kältemaschine oder Wärmepumpe
DE102011015153A1 (de) 2011-03-25 2012-09-27 Sortech Ag Verfahren und Vorrichtung zum Ausführen eines alternierenden Verdampfungs- und Kondensationsprozesses eines Arbeitsmediums
WO2016059777A1 (fr) * 2014-10-15 2016-04-21 株式会社デンソー Adsorbeur

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011053310A1 (de) * 2011-09-06 2013-03-07 Technische Universität Berlin Verfahren zum Betreiben einer Kälteanlage und Kälteanlage

Also Published As

Publication number Publication date
WO2018033418A1 (fr) 2018-02-22
EP3500807A1 (fr) 2019-06-26
DE102016215591A1 (de) 2018-03-08

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