EP2015006A2 - Pompe à chaleur - Google Patents

Pompe à chaleur Download PDF

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Publication number
EP2015006A2
EP2015006A2 EP20080009044 EP08009044A EP2015006A2 EP 2015006 A2 EP2015006 A2 EP 2015006A2 EP 20080009044 EP20080009044 EP 20080009044 EP 08009044 A EP08009044 A EP 08009044A EP 2015006 A2 EP2015006 A2 EP 2015006A2
Authority
EP
European Patent Office
Prior art keywords
heat pump
fluid
zone
heat
pump according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP20080009044
Other languages
German (de)
English (en)
Inventor
Roland Burk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2015006A2 publication Critical patent/EP2015006A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure

Definitions

  • the invention relates to a heat pump with hollow bodies, each comprising at least a first zone and at least a second zone between which a working fluid is reversibly displaceable, wherein a balance of the interaction of the working fluid with each of the zones of thermodynamic state variables depends.
  • a heat exchanger in particular a sorption reaction and / or heat pipe with a plurality of fibers known, wherein a plurality of fibers are attached with one end to or in the wall. The other end of the fibers is spaced from the wall surface.
  • the heat exchanger comprises an evaporation zone, which is arranged offset to an adsorption zone.
  • the object of the invention is to improve the efficiency of a heat pump according to the preamble of claim 1.
  • the object is in a heat pump with hollow bodies, each comprising at least a first zone and at least one second zone between where a working fluid is reversibly displaceable, wherein a balance of the interaction of the working fluid with each of the zones of thermodynamic state variables depends, achieved in that the hollow bodies each have a first active surface with the first zone, which faces a second active surface with the second zone.
  • the directly opposite active surfaces are only separated by a narrow gap.
  • a preferred embodiment of the heat pump is characterized in that the active surfaces are flat and substantially rectangular.
  • the active surfaces are preferably arranged parallel to one another and spaced from one another congruently.
  • a further preferred embodiment of the heat pump is characterized in that a substantially cuboidal cavity is arranged between the two active surfaces.
  • the cuboid cavity is completely closed at its periphery.
  • the hollow bodies are designed as closed tubes or plates with a substantially cuboidal cavity.
  • the working fluid is displaceable between the opposing active surfaces.
  • Another preferred embodiment of the heat pump is characterized in that the hollow bodies are made the same. As a result, the production of the hollow body is simplified.
  • a further preferred exemplary embodiment of the heat pump is characterized in that in each case two hollow bodies are arranged mirror-symmetrically on opposite heat transfer surfaces of fluid passage regions.
  • the fluid passage areas are each arranged between two mirror-symmetrically rotated hollow bodies.
  • a further preferred embodiment of the heat pump is characterized in that alternating passage regions of the first type for flow through with a first fluid for heat exchange with the first zones and passage regions of the second type for flow through with a second fluid for heat exchange with the second zones are arranged between two hollow bodies.
  • the first fluid is, for example, a water-glycol mixture.
  • the second fluid is, for example, air.
  • the passage areas are formed, for example, by flat tubes.
  • the walls of the hollow bodies at the same time form the boundary surfaces of the first and second-type passage areas, which are spaced apart by webs, corrugated ribs, turbulence sheets and or laterally closed. This has the advantage that the heat transfer between the hollow bodies and the fluids flowing through the passage areas is improved.
  • a further preferred embodiment of the heat pump is characterized in that the opposite zones of a hollow body are thermally decoupled from each other. This will heat flows between minimizes different hot opposite zones of a hollow body.
  • a further preferred embodiment of the heat pump is characterized in that the hollow bodies are equipped with a support structure.
  • the support structure serves to support pressure differences from the environment.
  • each hollow body comprises at least one adsorption / desorption zone and at least one evaporation / condensation zone.
  • the heat pump is in particular an adsorption heat pump or an adsorption refrigeration system.
  • a further preferred embodiment of the heat pump is characterized in that the first active surface is provided with an adsorber structure which forms the first zone.
  • the adsorbent structure or adsorber layer comprises, for example, activated carbon.
  • a further preferred embodiment of the heat pump is characterized in that the second active surface is provided with a capillary structure, which forms the second zone.
  • the capillary structure serves to trap condensed fluid and to keep it distributed over the entire surface in good thermal wall contact.
  • a fluid according to the invention is basically understood any flowable substance, in particular a gas, a liquid, a mixture of gaseous and liquid phase or a mixture of liquid and solid phase (for example, flow-ice).
  • any type of thermodynamically relevant exothermic or endothermic reaction of the working fluid understood with or in the zone in which in particular takes place a heat exchange between the respective zone and the fluid flowing around the zone.
  • the first zone may contain an adsorbent-desorber material, for.
  • zeotite wherein the working fluid may be water, which is condensable or vaporizable especially in the second zone in capillary structures.
  • different metals may be present in the zones, for example, wherein the working medium z. B. is hydrogen, so that under heat absorption and / or heat release takes place formation or dissolution of metal hydrides in the zones.
  • the interaction of the working agent with the zones may include both physisorption and chemisorption or other type of interaction.
  • Under a hollow body or hollow element in the context of the invention is to be understood every element within which a transport of the working fluid is possible.
  • a heat pump is the building services.
  • the heating power generated by a burner can be used to additionally raise environmental heat to a usable for heating temperature level.
  • the heat pump can be used, for example, in conjunction with a combined heat and power plant to increase the overall efficiency.
  • the heat pump can be used for more effective use of the heat flow contained in the coolant and / or exhaust gas for heating purposes by pumping additional heat from the outdoor temperature level to a usable level for the heating.
  • the same, possibly slightly modified or even differently set system can be used to cool the building by also.
  • the waste heat flow of the generator is used to drive the cooling. It may also be a use of thermal solar energy for cooling by means of the heat pump.
  • the heat pump according to the invention can in principle also as in the DE 198 18 807 A1 described be used for air conditioning of particular commercial vehicles.
  • Other conceivable applications are the use of district heating in the summer for cooling or air conditioning or the waste heat utilization of industrial combustion systems for generating air conditioning or process cooling.
  • a heat pump according to the invention is characterized by high maintenance freedom and reliability. There is a high degree of flexibility in selecting the first and second fluids, which need not be the same and may differ, for example, for summer use and winter use.
  • this is an adsorption heat pump, wherein the working fluid in the first zone is adsorbable - and desorbable and is vaporizable and condensable in the second zone.
  • the working medium is reversibly chemisorbable at least in the first zone.
  • the heat pump may also be a mixed principle, for example in the sense that some hollow elements or hollow bodies work according to the adsorber principle (physisorption) and other hollow elements or hollow bodies have chemisorption.
  • the flow paths have a first group of at least two adjacent flow paths and a second group of at least two adjacent flow paths, wherein the flow paths of the first group all in a first direction and the flow paths of the second group all in this opposite direction be flowed through.
  • a plate element comprises a number of parallel closed end flat tubes, wherein each of the flat tubes forms a hollow element with first and second zone.
  • each of the flat tubes forms a hollow element with first and second zone.
  • the flat tubes are hermetically separated from each other. This makes it possible to a particular extent that different hollow elements or flat tubes of the same plate element have different temperatures and pressures, which leads to a further improved heat exchange for a given space size with suitable gradation of temperatures in conjunction with suitable flow direction of the fluid along the plate elements.
  • a hollow plate is arranged between two of the plate elements, the cavity of which is assigned to one of the passage regions, wherein the hollow plate is in planar thermal connection, in particular soldering, with the adjacent plate elements.
  • a hollow plate of the first type is arranged between two plate elements, which forms a passage region of the first type and a hollow plate of the first type substantially thermally separated hollow plate of the second type, which forms a passage region of the second type.
  • the hollow plates of the first and second type need not necessarily have the same thickness, which can be compensated by appropriate shaping of the plate elements or hollow elements;
  • the hollow plate of the first type can be dimensioned adapted for a liquid fluid and the hollow plate of the second type can be adapted for a gaseous fluid.
  • the distribution insert of the distribution devices for the second fluid particularly preferably has partition walls which separate at least three separate helical chambers in at least one of the cylinders, wherein a flow path comprising at least one passage region of the second type is defined by each of the chambers.
  • the particular, but not necessarily spirally shaped partitions flags or other closure means, by means of which a temporary closure of at least one flow path is effected.
  • a temporary closure of a flow path with regard to the fluid exchange, depending on the design of the heat pump, the effectiveness of a heat exchange at a given size can be further improved by preventing bypass flows.
  • the distribution insert in order to avoid bypass flows, can be moved stepwise so that the time period in which two groups of passage areas are opened simultaneously is swept over relatively quickly and the distribution insert then remains in a position for a certain time only one connection to a group of passage areas exists.
  • the distributor insert has a connection region with radial apertures, wherein a fluid exchange of the chamber takes place via the apertures aligned in each case with a chamber.
  • a simple connection of the helical chamber with an outer fluid guide is made possible even if there are a large number of separate chambers.
  • the fluid exchange of a plurality of helical chambers takes place via a corresponding number of openings with a multipart connection space which at least partially surrounds the cylinder.
  • a connection space of the first cylinder is connected to a connection space of the second cylinder via a number of mutually separated channels.
  • each of the distributor inserts is rotatably driven in rotation synchronized with the other distributor inserts. In-phase synchronization of rotary movement of the distributor inserts is generally required for efficient operation of the heat pump.
  • the two Verteiferein accounts of the first and the two vertical inserts of the second fluid are each positioned in their phase position so that coincide with the communicating with the chambers flow areas.
  • a distribution device of the second fluid with respect to a distribution device of the first fluid with respect to a phase position of a distribution cycle adjustable be changed. This can be done in particular via a phase position of the distributor inserts.
  • the adjustability of the phase position allows further optimization of the heat pump performance. In general, optimization of the phase position as a function of the average temperatures of the fluids, the mode of operation of the hollow elements and the type of working fluid, the type of fluids and other parameters of the heat pump can improve the mode of action.
  • the coiled or at least partially straight chamber sectors are unevenly distributed over the entire circumference. This ensures that over a cycle or a revolution of the Verteil contactses a variable number of passage areas is connected to the respective chamber or defined by the chamber flow path has a variable width, which can lead to an optimization of the heat pump performance in a given space in an individual case.
  • a plurality of hermetically separate hollow elements or hollow bodies may be provided, wherein at least two of the hollow elements have different working means and / or sorbents.
  • a heat pump according to the invention is not limited to uniform material systems in each of the hollow elements.
  • the flow paths of the first fluid are flowed through in the opposite direction in comparison to the flow paths of the second fluid assigned via identical hollow elements.
  • the partitions of the distributor insert are spirally formed, and that the separated chambers are helical.
  • the partitions of the distributor insert run substantially straight over the length of the distributor insert.
  • the distributor inserts are simple and inexpensive to produce, especially as at least partially substantially prismatic body. These can be produced, for example, as optionally reworked extruded profiles or injection-molded parts.
  • the hollow cylinder in this case has a plurality of computations, wherein in the axial direction successive openings are each offset by an angle to each other. As a result, a cyclical sequence of flow paths is realized in a structurally simple manner, which migrate by rotating the straight distributor insert in the stacking direction of the hollow elements.
  • circumferential hollow cylinder has an inner and an outer wall, wherein between the two walls a plurality of axially successively arranged annular chambers are formed.
  • annular chambers are particularly preferably designed as annular chamber modules stackable in the axial direction. This can be achieved by using common parts cost-adapted production of hollow cylinders or distribution devices of different lengths or heat pumps of different sizes.
  • a displacement device for the second fluid is provided for optimizing the performance with a given installation space, wherein the second fluid is conducted by means of the distributor via a plurality of flow paths through the passages regions of the second type.
  • One of the flow paths particularly preferably forms a closed loop separated from the remaining flow paths of the second fluid.
  • the closed flow path advantageously has a smaller width in the stacking direction than an adjacent flow path, wherein the closed flow path is guided in particular for intermediate temperature evaporation and / or intermediate temperature condensation.
  • Such a guidance of the closed flow path forms an internal thermal coupling of an evaporation zone and a condensation zone of the heat pump, as a result of which, in particular, heat sources with a lower temperature range can still be used.
  • the closed flow path comprises a pump member for conveying the fluid.
  • This embodiment makes use of the possibility of realizing a kind of cascade connection only by means of the fluid control, either in order to reduce the required desorption temperature and / or to increase the temperature interval between minimum adsorption temperature and evaporation temperature (temperature stroke).
  • This is accomplished by providing intermediate chambers in the fluid distribution cylinders for fluid control of the phase change zone between the condensation and evaporative distribution chambers through which an additional small circuit circulates.
  • This causes heat transfer from the final condensation phase to the final evaporation phase by using cold fluid for condenser cooling.
  • This causes a pressure drop at the end of the desorption / condensation phase whereby a lowering of the temperature required for complete desorption is effected.
  • the associated pressure increase at the end of the adsorption Nerdampfungsphase causes an increase in the required adsorption temperature.
  • thermally driven systems such as absorption and adsorption heat pumps or refrigeration systems and steam jet refrigeration systems known.
  • the present application relates concretely to an adsorption heat pump or refrigeration system according to the German patent application DE 10 2006 059 504.1 ,
  • the device proposed and described there is based on so-called sorption tubes or sorption plates which comprise at least one adsorption / desorption zone and one evaporation / condensation zone.
  • the function and possible internal equipment of such sorption tubes or plates is for example in DE 10 2006 028 372 A1 described.
  • the heat pumping process is produced by the fact that the useful and regenerating process taking place in the sorption tubes, with the simultaneously occurring partial processes of adsorption and evaporation or desorption and condensation, do indeed run at the same pressures but different temperatures.
  • a quasi-continuous heat pumping process can be produced.
  • the problem may occur that even small portions of foreign gas deteriorate the kinetics of the useful and regeneration process, because they hinder the formation of a pure vapor flow of working fluid and the driving sorption and / or stofftransportbehindemde layers of inert gas build up immediately before the interfaces to the adsorber structures.
  • the invention teaches the use of sheet-like hollow bodies, in particular sorption tubes or plates, in which the adsorber coating for the adsorption / desorption process and the capillary structure for the evaporation / condensation process are arranged on essentially opposite surfaces.
  • the concurrent processes of adsorption and evaporation during the use process as well as the desorption and condensation which take place simultaneously during the regeneration process thus take place in direct neighborhoods separated only by a gap.
  • FIG. 1 is a hollow body 1 shown in perspective and cut open at one end.
  • the hollow body 1 is formed by a closed flat tube, which is hollow inside and is also referred to as a plate or plate member.
  • a first zone 4 and a second zone 5 is provided in the hollow body 1.
  • the first zone 4 is provided on a first active surface 6 in the interior of the flat tube 2.
  • the second zone 5 is provided on a second active surface 7 in the interior of the flat tube 2.
  • an adsorber 8 is attached at the first active surface 6, an adsorber 8 is attached.
  • the adsorbent structure 8 is, for example, activated carbon.
  • a capillary 9 is attached.
  • the two zones 4, 5 are arranged directly opposite each other and separated from each other only by a cavity 10.
  • the cavity 10 has substantially the shape of a cuboid.
  • the flat tube 2 is preferably formed of two mirror-symmetrically constructed shells, which are connected to each other in a gastight manner by joining joints 11 to 13 and filled with a working fluid.
  • the hollow body may have support means to intercept differential pressures to the ambient pressure. These proppants also preferably have a very low thermal conductivity.
  • the embodiment of the hollow body 1, which are also referred to as sorption or sorption, requires a modified structure of a plate stack of sorption tubes and two fluid guide tubes for inclusion or removal of the heat flows for the sorption, adsorption / desorption, on the one hand and the phase change processes, evaporation / condensation, on the other.
  • FIG. 2 In FIG. 2 are four hollow body 15, 16, 17, 18, which are carried out the same as in FIG. 1 illustrated hollow body 1, shown stacked one above the other.
  • the adsorber coated plate side is in thermal contact with a first category of fluid guide plates or fluid guide tubes 21, 22, 23, respectively.
  • the fluid guide plates 21 to 23 of the first category serve to remove or supply the adsorption or desorption heat.
  • By arrows 24 to 26 heat transfer streams for adsorption / desorption are indicated.
  • the sides of the hollow bodies 15 to 18 with the capillary structure (7 in FIG. 1 ) are each in thermal contact with a second category of fluid guide plates 27, 28.
  • the fluid guide plates 27, 28 serve to remove or supply the condensation or evaporation heat.
  • the flow through the fluid guide plates 27, 28 takes place in the cross flow, that is perpendicular to the flow through the fluid guide plates 21 to 23, which is indicated by the reference numerals 31 and 32.
  • the fluid management for the supply and removal of the sorption heat and the heat for the phase change is analogous to the German patent application DE 10 2006 059 504.1 the same applicant.
  • the fluid distribution to the individual fluid guide plates is not shown here.
  • FIG. 3 is an adsorption heat pump with the fluid flow limiting walls 41 shown schematically.
  • the adsorption heat pump 40 is equipped with fluid distribution cylinders 42, 43 and 44, 45.
  • the Fluidverteilzylinder 42, 43 control the flow of a liquid heat carrier through fluid guide tubes of the first kind and are equipped for this purpose, each with twelve sub-chambers for guiding the liquid heat carrier at different temperature levels.
  • the course of the flow of the liquid heat carrier for the supply and removal of the adsorption and desorption is indicated by arrows 46 to 48.
  • the arrows 46 and 47 indicate a flow guidance.
  • the arrow 48 indicates a deflection of the fluid flow.
  • the Fluidverteilvoriquesen 44, 45 are each equipped with only two Operakammem and control a liquid or gaseous heat exchanger, such as water or air, for the supply or removal of the evaporation or condensation heat.
  • a liquid or gaseous heat exchanger such as water or air
  • the associated fluid flow is indicated.
  • the fluid streams of first category 46, 47 and second category 49 are cross-countercurrently connected.
  • an adsorption heat pump 50 having opposed active areas is shown in various sectional views.
  • the adsorption heat pump 50 includes a housing or the fluid flow limiting walls 51, in which a plurality of hollow bodies 52 to 55 are stacked on top of each other.
  • the hollow bodies 52 to 55 are arranged such that the sides of the hollow bodies with the adsorber structure are in thermal contact with flutation tubes 61 to 63.
  • the associated fluid flows are in FIG. 5 indicated by arrows. Fluid distribution is accomplished with fluid distribution devices 64, 65, each comprising an annular chamber and a straight distributor roller having a star profile divided into six chambers.
  • fluid distribution devices 64, 65 each comprising an annular chamber and a straight distributor roller having a star profile divided into six chambers.
  • Such Fluidverteilvoriquesen are in the German patent application DE 10 2006 059 504.1 described.
  • the fluid guide tubes 61 to 63 are each equipped at one end with a deflection 68, 67, 66.
  • an adsorption heat pump 80 with opposing active surfaces is shown schematically.
  • the Adsorptions Scripumpe 80 is equipped with two Fluidverteilvoriquesen 81, 82, which serve to distribute a liquid heat carrier for dissipating or supplying the condensation or evaporation heat in associated fluid guide plates.
  • the flow of the fluid is indicated by an arrow 83.
  • the adsorption heat pump 80 further includes two fluid advance devices 84, 85 for distributing a fluid to remove / supply the adsorption or desorption heat in associated fluid guide tubes or fluid guide plates.
  • the fluid flow between the Fluidverteilvortechnischen 84, 85 is indicated by an arrow 86.
  • the Fluid flows 83, 86 are connected in countercurrent.
  • the structure and function of the fluid distribution devices 81, 82 and 84, 85 are in the DE 10 2006 028 372 A1 described.
  • the construction of an adsorption heat pump with opposing active surfaces described with reference to various exemplary embodiments provides, inter alia, the following advantages:
  • the vapor transport paths between adsorbent and capillary structure are very short and low in pressure. They are therefore less sensitive to foreign gas components.
  • the flow direction of the working medium vapor is perpendicular to the active surfaces at a significantly reduced vapor velocity, which significantly reduces the risk of transfer of liquid components from the capillary structure into the adsorber structure.
  • the volume filled with pure working medium vapor is significantly lower, which increases the COP of the plant. Due to the lower influence of foreign gas fractions, material systems are also suitable whose working materials have a very low vapor pressure, for example water.
  • the passage openings of the Fluidverteilzylindern in the fluid guide plates can be made larger and thus less pressure loss. Or conversely, the diameters of the Fluidverteilzylinder be reduced at the same flow passage, resulting in a material and cost savings.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sorption Type Refrigeration Machines (AREA)
EP20080009044 2007-06-14 2008-05-16 Pompe à chaleur Withdrawn EP2015006A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007028032 2007-06-14

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EP2015006A2 true EP2015006A2 (fr) 2009-01-14

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012000563A1 (fr) 2010-07-02 2012-01-05 Schwoererhaus Kg Système de four destiné à brûler un combustible liquide, en particulier de l'éthanol
EP3012558A3 (fr) * 2009-03-31 2016-09-07 MAHLE Behr GmbH & Co. KG Stockage de ressource de fonctionnement, fluide caloporteur, pompe a chaleur
EP3124895A1 (fr) * 2015-07-29 2017-02-01 Vaillant GmbH Pompe a chaleur a adsorption et echangeur thermique a plaques
EP3339792A1 (fr) * 2016-12-20 2018-06-27 Alfa Laval Corporate AB Collecteur pour un échangeur de chaleur et échangeur de chaleur

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19818807A1 (de) 1998-04-27 1999-10-28 Behr Gmbh & Co Sorptionsvorrichtung, insbesondere zur Klimatisierung von Fahrzeuginnenräumen
DE102006028372A1 (de) 2005-06-17 2007-02-01 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Sorptions-, Reaktions- und/oder Wärmerohr

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006059504A1 (de) 2005-12-14 2007-06-28 Behr Gmbh & Co. Kg Wärmepumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19818807A1 (de) 1998-04-27 1999-10-28 Behr Gmbh & Co Sorptionsvorrichtung, insbesondere zur Klimatisierung von Fahrzeuginnenräumen
DE102006028372A1 (de) 2005-06-17 2007-02-01 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Sorptions-, Reaktions- und/oder Wärmerohr

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3012558A3 (fr) * 2009-03-31 2016-09-07 MAHLE Behr GmbH & Co. KG Stockage de ressource de fonctionnement, fluide caloporteur, pompe a chaleur
WO2012000563A1 (fr) 2010-07-02 2012-01-05 Schwoererhaus Kg Système de four destiné à brûler un combustible liquide, en particulier de l'éthanol
EP3124895A1 (fr) * 2015-07-29 2017-02-01 Vaillant GmbH Pompe a chaleur a adsorption et echangeur thermique a plaques
EP3339792A1 (fr) * 2016-12-20 2018-06-27 Alfa Laval Corporate AB Collecteur pour un échangeur de chaleur et échangeur de chaleur
WO2018114237A1 (fr) * 2016-12-20 2018-06-28 Alfa Laval Corporate Ab Collecteur pour échangeur de chaleur et échangeur de chaleur
US11530883B2 (en) 2016-12-20 2022-12-20 Alfa Laval Corporate Ab Header for a heat exchanger and a heat exchanger

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Publication number Publication date
DE102008023662A1 (de) 2008-12-18

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