WO2010000255A1 - Échangeur thermique compact à lamelles - Google Patents

Échangeur thermique compact à lamelles Download PDF

Info

Publication number
WO2010000255A1
WO2010000255A1 PCT/DE2009/000949 DE2009000949W WO2010000255A1 WO 2010000255 A1 WO2010000255 A1 WO 2010000255A1 DE 2009000949 W DE2009000949 W DE 2009000949W WO 2010000255 A1 WO2010000255 A1 WO 2010000255A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
tubes
exchanger according
finned heat
slats
Prior art date
Application number
PCT/DE2009/000949
Other languages
German (de)
English (en)
Other versions
WO2010000255A4 (fr
Inventor
Niels Braunschweig
Sören PAULUSSEN
Original Assignee
Invensor Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Invensor Gmbh filed Critical Invensor Gmbh
Priority to EP09772025A priority Critical patent/EP2313729A1/fr
Priority to DE112009002184T priority patent/DE112009002184A5/de
Publication of WO2010000255A1 publication Critical patent/WO2010000255A1/fr
Publication of WO2010000255A4 publication Critical patent/WO2010000255A4/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag

Definitions

  • Sorption machines or sorption heat pumps or sorption refrigerators are described in various embodiments in the prior art and are generally used for heating and / or cooling of buildings, as well as the water and air temperature control in general. They are characterized by a particularly good primary energy efficiency, since they raise with the aid of a thermodynamic cycle, for example, ambient heat to a usable for a heating and hot water temperature level. A distinction is made between machines based on adsorption or absorption.
  • adsorption gaseous refrigerant
  • the desorption accordingly as dissolution of a solid.
  • the refrigerant which absorbs heat at a low temperature and low pressure and gives off heat at a higher temperature and pressure, is selected so that the adsorption or desorption is accompanied by an aggregate state change.
  • adsorbent materials are described in the prior art, which are finely porous and therefore have a very large inner surface.
  • Advantageous materials include activated carbon, zeolites, alumina or silica gel, aluminum phosphates, silica-aluminum phosphates, metal-silica-aluminum phosphates, mesostructure silicates, metal-organic frameworks and / or microporous material comprising microporous polymers.
  • the Adsorptionskarltemaschine consists of at least one ad / desorber unit, at least one evaporator, at least one condenser and / or a combined evaporator / condenser unit, which housed in a common container or in separate containers, which then o.a. for the
  • Refrigerant flow are interconnected.
  • the advantage of the sorption machines compared to conventional heat pump technology is that the process is carried out solely by the temperature of the sorbent.
  • the container can be hermetically sealed and gas-tight.
  • the adsorption chiller preferably operates in the vacuum range. Due to the very low density of the refrigerant in the vacuum range, this sometimes leads to very high flow velocities (For example, 25 m / s - 100 m / s, or g Banker) of the vapor refrigerant. Accordingly, the vapor flows within an adsorption machine must be carefully designed to avoid unnecessary pressure losses of the vapor flow.
  • tubular heat exchangers which consist of a plurality of parallel tubes through which the heat transfer fluid flows, wherein the tubes are surrounded by the refrigerant or adsorbent.
  • the tubes can be equipped with additional attached perpendicular to the tubes slats, that is, for example, the slats are pushed onto the tubes and the tubes then expanded.
  • finned heat exchangers are in
  • Substantially rectangular slats are used, which are in metallic contact with the core tubes, wherein the slats are designed substantially so that they have the same width and / or height of the heat exchanger.
  • Laminated heat exchangers are often used in adsorption machines as adsorber / desorber, as a condenser, as an evaporator and / or as an evaporator / condenser unit.
  • adsorber / desorber When used as adsorber / desorber, the adsorbent is between or on the lamellae.
  • the refrigerant When used as an evaporator, the refrigerant is usually evaporated between the slats, which is between the slats.
  • a disadvantage of the prior art is that the respective steam flow must flow in the use of a fin heat exchanger within the channels between the slats, resulting from the geometry of the heat exchanger. With larger or more intensive evaporation and sorption processes, pressure losses of the steam flow occur so regularly.
  • these heat exchangers arranged in this way must then be hydraulically piped together so that they correspond in function to a component according to this further production step.
  • the finned heat exchanger is designed as an evaporator in an adsorption machine, effective operating phases such as falling film evaporation are difficult to realize because the refrigerant must be introduced from above into the evaporator and pumped.
  • moving parts are built into the adsorption machine, which are prone to failure and possibly require regular maintenance.
  • the heat transfer results in a vertical orientation of the slats the suboptimal effect that the refrigerant to be evaporated is indeed between the slats, the full slat surface, however, does not work for the evaporation process, but essentially the simple water surface for the heat transfer is relevant.
  • the object of the invention was therefore to provide a fin heat exchanger, which does not have the disadvantages and shortcomings of the described in the prior art fin heat exchanger.
  • this task is characterized by the characteristics of the independent
  • a laminated heat exchanger comprising tube packages consisting of a plurality of tubes arranged in a plane and a fluid flowing in the tubes and lamellae, which are spaced apart from one another, are arranged in parallel and are penetrated by the tubes arranged in each case in one plane , wherein between the stacked pipe pacts Passage passages exist and the tube packages are arranged in several superposed planes alternately with the free passages, wherein the stacked raw packets are not thermally conductively connected via fins, can be provided and does not have the disadvantages of the prior art.
  • a core tube according to the invention is an elongated hollow body whose length is usually much larger than its cross-section and has a rigidity. It may also have a rectangular, oval or other cross-section.
  • the core tube is serpentine-shaped and runs as a coil through the heat exchanger in the superimposed planes.
  • the fluid which comprises, for example, water or another heat carrier, is passed through the tubes and the tubes are arranged such that the tube packages are in one plane.
  • the layer can be in a vertical, horizontal, or other position.
  • the tube packages are arranged in particular as a raw coil in a plane, that is, the tubes extend in a plane.
  • Slats are attached to the tubes in a plane, i. the tubes have a lamellar ribbing.
  • the person skilled in the art knows how a ribbed ribbing can be applied to pipes.
  • the tubes can be widened after applying the slats, or the slats are pressed onto the pipes by machine, so that a connection between the slats and the pipes is formed.
  • a lamellar ribbing referred to in the context of the invention an arrangement of fins on the tubes to increase the surface area of the tubes, or the heat exchange surface.
  • the lamellae are arranged at a distance from one another, which the person skilled in the art can determine empirically by means of routine tests.
  • a substantially parallel arrangement of the slats The person skilled in the art understands, under a substantially parallel arrangement of the lamellas, that the lamellae can be arranged parallel to one another, but also with a tolerance of 5 to 10 degrees to one another.
  • the tube packages are arranged one above the other in the lamella heat exchanger, free passages or clearances being created between the tube packs.
  • Free passage referred to in the context of the invention, a cavity in the heat exchanger, which has no functional components.
  • an alternating arrangement of the stacked tube packages with the free passages that is, between two stacked tube packages creates a free passage.
  • a distance, ie a free passage, between two tube packages of 0.5 cm is preferred.
  • the pipe pacts can be arranged one above the other at different angles.
  • a substantially parallel arrangement of the tube packages is advantageous.
  • a substantially parallel arrangement also includes an arrangement of the tube packages that deviates from idealized parallelism by 5-10 degrees.
  • the plate heat exchanger according to the invention By the plate heat exchanger according to the invention and the attachment of the fins on the tubes and the arrangement of the tube packages alternately with the free passages a simple and effective enlargement of the heat exchange surface is realized.
  • the refrigerant can flow through the fin heat exchanger without the steam flow suffers a pressure loss.
  • the fin heat exchanger consists of a component, whereas the heat exchangers disclosed in the prior art many times consist of several components.
  • an installation of the finned heat exchanger in a system and a maintenance of the finned heat exchanger is much easier, since the heat exchanger is easy to handle by a fitter and the fitter receives, due to the free passages, also access to the interior of the heat exchanger.
  • the tube packages have at least one frictionally attached end plate.
  • the end plate is non-positively connected to at least one arranged in a plane tube package.
  • non-positive connections include screws, presses, rivets, clamping rings, molded parts, bent pipe sections and / or screws.
  • the end plates are soldered or welded to the tube packages.
  • the end plates perpendicular to the tube pacts, are arranged on both opposite sides of the plate heat exchanger.
  • the end plates stabilize the pipe packs arranged in a plurality of superimposed planes and also permit easy attachment of the plate heat exchanger via the end plates to, for example, a surface and the supply and discharge of the fluid flowing through the tubes by means of line systems attached to the end plates.
  • the tube packages are from the
  • End plates fitted that is, the end plates limit the tube packages in the vertical and serve to stabilize the tube packages.
  • the embodiment thus allows a compact design of the fin heat exchanger.
  • the end plates consist of metal and / or ceramic materials.
  • the end plates are made of metal, whereby an optimum strength of the end plates and optimum stability of the attached to the Endblechchen tube packages is achieved.
  • preferred variants include steel, stainless steel, cast iron, copper, brass, nickel alloys, titanium alloys, aluminum alloys, combinations of plastic and metal (composite pipe), combinations of glass and metal (enamel) or ceramic. Ceramic materials, including building ceramic materials, have a high stability and long durability. In addition, weight can be saved by this advantage variant.
  • the end sheets may also be advantageous for the end sheets to have holes. In this case, holes that are suitable for receiving the core tube, are released. The holes in the Endblechen example, the steam can escape better from the heat exchanger.
  • the free passages have a height of more than 0.5 cm. Between the stacked tube packages arise free passages, in which, according to the invention, preferably no functional components are arranged. It is advantageous if the free passage has a height of more than 0.5 cm, that is, if the distance between the stacked tube packages is more than or equal to 0.5 cm. It may also be advantageous if between two arranged in a plane tube packages a distance of 0.5 - 20 cm. Particularly advantageous may be a distance of 0, 5 - 3 cm.
  • the free passage allows easy handling of the heat exchanger and good accessibility for the assembly of other components and simplifies the maintenance of the heat exchanger by a fitter.
  • the advantageously stacked tube packages have a Lamellenverrippung, that is, lamellae are spaced from the pipes.
  • the tube packages are arranged alternately with free passages and the slats do not protrude into the free passages hienein.
  • the heat conduction from the tubes to the lamellae is limited to the lamellar ribbing, so that no or only a germinger heat loss occurs.
  • the heat exchangers disclosed in the prior art have fins which connect a plurality of tube packages together. However, the heat conduction is not lossless due to the relatively long fins and effective heat exchange is not possible.
  • the preferred embodiment, short slats are installed, which guarantee a uniform heat distribution and thus improve the heat exchange.
  • the tube packages are arranged in several horizontal planes.
  • the tube packs are arranged one above the other alternately with free passages, wherein the tube packs are structured in a plurality of horizontal planes, that is, the planes are arranged substantially parallel or plane-parallel. It is known to the person skilled in the art that a substantially parallel arrangement, a parallel arrangement of the planes to each other with a tolerance of 5 - 10 degrees.
  • the horizontal arrangement of the tube packages allows a compact design of the fin heat exchanger and optimal flow and homogeneous distribution of the fluid flowing through the heat exchanger.
  • the incoming fluid for example a refrigerant
  • the tube bundles are wetted with the tube ribbing by a thin fluid film, whereby the heat exchange surface is increased and thus the efficiency of the heat exchanger is improved.
  • the tubes are made of metal, plastic and / or ceramic materials.
  • Preferred variants include steel, stainless steel, cast iron, copper, brass, nickel alloys, titanium alloys, aluminum alloys, plastic, combinations of plastic and metal (composite pipe), combinations of glass and metal (enamel) or ceramic.
  • Frictional connections include clamping rings, molded parts, bent pipe sections, screws or rivets. Bonded joints include gluing, welding or vulcanizing. Due to the good thermal conductivity copper or aluminum is advantageously used as the material for the pipes, whereby the use of stainless steel can be advantageous because it has high static and dynamic strength values and a high thermal conductivity.
  • Tubes made of plastic, comprising polyvinyl chloride are particularly light and flexible and can thus reduce the weight of the heat exchanger, without, however, leading to losses in the heat conduction.
  • the tubes and the lamellae are thermally conductively connected.
  • the tubes have a Lamellenverrippung, wherein the lamellae spaced from each other, are arranged in parallel on the tubes and are penetrated by the arranged in each case a plane tubes.
  • the connection between the tubes and the fins is a heat-conducting connection.
  • the slats made of metal, plastic and / or ceramic materials and have a rectangular shape.
  • the preferred materials provide optimum bonding and thus heat transfer between the tubes and the fins.
  • the materials guarantee a stability of the lamellae even under high load due to, for example, high temperatures or varying pressures.
  • a rectangular shape of the slats whereby other shapes such as round or oval may be possible. Due to the preferred shape of the lamella surface enlargement is achieved and the heat exchange surface is increased.
  • rectangular shapes are advantageous for the production of lamellar ribbing and are particularly inexpensive to produce.
  • a shell is arranged in the free passage.
  • the tube packages are arranged one above the other in the heat exchanger in several levels. Between two superposed levels creates a free passage, the
  • Pipe packages are arranged alternately with the free passages.
  • a shell may be introduced, which advantageously has the same base as the tube packages, but can also occupy only a portion of the base.
  • the base area of the tube packs refers to the area of the tube pacts, that is to say the area dependent on the side lengths.
  • These trays or swamps or trays may be secured to the fins and / or pipes via seals such as a rubber or adhesive seal.
  • the shells are advantageously made of metal or plastic. For example, from above into the heat exchanger entering liquid fluid enters the horizontally arranged under the tube bundles shells and is held and stored there, creating a water plane. The preferred embodiment thus enables stacking of water levels.
  • the lamellae of the tube packages partially protrude into the fluid in the shells. It may also be advantageous if the tubes protrude into the liquid fluid. Due to the direct contact of the fluid with the fins and / or the tubes, an effective heat exchange between the fluid and the fins or tubes takes place.
  • overflow devices are mounted in the trays.
  • the shells fill with, for example, a liquid fluid and the Overflow devices serve to adjust the level of liquid in the shell so as to prevent an uncontrolled overflow of the shell.
  • overflow conduits or tubes may be used that are vertically attached to the bottom of each tray and carry excess liquid fluid to a next underlying tray.
  • dents or holes inserted laterally in the cups can control the fluid level.
  • a liquid level is set in the shells, which guarantees optimum operation of the fin heat exchanger. Effective operations may be performed in the fin heat exchanger in which a liquid fluid is introduced from above into the fin heat exchanger and the fluid is collected in the trays, with overflow devices adjusting the liquid level.
  • the effectiveness of the heat exchangers can be improved by the preferred embodiment.
  • the fin heat exchanger has inlet and outlet lines for hydraulic interconnection and operation.
  • the heat transfer medium is fed via supply and discharge lines, including pipes, pipe sections, pipe fittings or valves in the heat exchanger.
  • the heat transfer medium from the heat exchanger is directed into a heat transfer circuit. Due to the advantageous arrangement of the inlet and outlet lines, an effective interconnection of the heat transfer circuit is possible, whereby a small heat loss.
  • the invention also relates to the use of a fin heat exchanger for sorption machines, in particular adsorption refrigeration machines.
  • Sorption machines or adsorption machines are described in the prior art and comprise either a condenser heat exchanger and an evaporator heat exchanger or an evaporator-condenser unit and at least one adsorber / desorber unit with heat exchanger and sorption material.
  • the attachment to a solid or adsorbent material is referred to as adsorption and the desorption accordingly as dissolution of a solid.
  • adsorbent materials can be used which are finely porous and have a very large internal surface, comprising activated carbon, zeolites, alumina or silica gel, aluminum phosphates, silica-aluminum phosphates, metal-silica-aluminum phosphates, mesostructure silicates, metal-organic frameworks and / or microporous Material comprising microporous polymers. It was surprising that the plate heat exchanger according to the invention for an adsorption machine does not have the deficiencies described in the prior art.
  • the finned heat exchanger can be used as an evaporator in a Adsorptionshimltemaschine, whereby, for example, an effective use of Rieselfilmverdampfung for Adsorptionshimltemaschinen without the additional pumps must be installed to circulate the refrigerant and from above to guide the heat exchanger is possible.
  • the refrigerant accumulates in the trays when inserted from the top in the fin heat exchanger. As the refrigerant boils, the refrigerant splashes on the vertical fins, creating a thin film on the vertical fins.
  • menisci form on the lamellas, which increase the surface area. Due to the increase in surface area, there is a rapid change in the state of matter, and the heat carrier flowing through the heat exchanger is cooled. In addition, the refrigerant and the resulting steam can optimally flow through the passed through with free passages heat exchanger. An effective heat exchanger improves the efficiency of the adsorption chiller.
  • the finned heat exchanger can be used as a condenser in a Adsorptionshimltemaschine.
  • the arrangement of the tube packages with the free passages and the fins promote a distribution of a flowing through the heat exchanger gaseous fluid.
  • the heat transfer can thus take place on a large heat exchange surface, wherein the heat transfer medium is heated by the condensation of the refrigerant.
  • the absorbed heat can be used, for example, for the evaporation in the adsorber or supplied to an external source as heat.
  • the cooling of the refrigerant is particularly supported by the large exchange surface, which results from the lamellar ribbing. Thus, an efficient heat exchange between the heat transfer medium and the refrigerant takes place.
  • a fin heat exchanger as a heat exchanger of an adsorber / desorber unit for sorption, in particular adsorption is preferred.
  • the structuring according to the invention of the fin heat exchanger is arranged with the superimposed Pipe packages, the free passages and the slats of advantage, since sorption material can be introduced between the slats and so optimal heat exchange with an enlarged contact or heat exchange surface can take place.
  • sorption material can be introduced between the slats and so optimal heat exchange with an enlarged contact or heat exchange surface can take place.
  • Through the free passages a pressure loss-free inflow and outflow of the vapor refrigerant is possible.
  • FIG. 4a side view of a fin heat exchanger described in the prior art
  • Figure 1a) and b) show a plan view and a side view of a fin heat exchanger, as described in the prior art.
  • Heat transfer medium is conducted via the supply and discharge lines 4 into and out of the tubes 2 of the heat exchanger.
  • the tubes 2 are serpentine-like arranged in planes.
  • vertically slats 1 are mounted, which are arranged parallel to each other.
  • the vertical end plates 3 are connected to the tubes.
  • the fins 1 connect the horizontally arranged tubes 2, i. the planes are thermally conductively connected to each other, so that a lamella 1 occupies the height of the heat exchanger and has the same area as the end plates 3.
  • the heat exchangers described in the prior art are built in a multi-layered manner, whereby, however, the component becomes heavy and voluminous and the vapor pressure in the heat exchanger is not constant. As a result, it is only conditionally suitable for use in light and compact adsorption chillers to be built.
  • the use of the heat exchanger in an adsorber / desorber unit is only partially possible. Thus, a steam entering the heat exchanger is distributed only poorly by the arrangement of the lamellae 1.
  • FIG. 2a) and b) represents a top view and side view of the segmented fin heat exchanger according to the invention.
  • Pipes 2 are arranged in tube packages 2.1, wherein the tubes 2 run serpentine in a horizontal plane. However, the tube packages 2.1 can also be arranged vertically or at any angle. Horizontal pipe packages 2.1 can be arranged one above the other which creates individual segments or layers.
  • the tubes 2 are formed from a core tube.
  • the core tube is an elongated hollow body whose length is generally much larger than its cross-section and has a rigidity. It may also have a rectangular, oval or other cross-section.
  • the tubes 2 may be made of materials comprising metal,
  • Plastic, and / or ceramic materials are manufactured. Particularly suitable metals with a high thermal conductivity, such as copper and aluminum.
  • slats 1 are attached on the tubes 2 in a plane. The person skilled in the art is aware that lamellae 1 can be pressed onto the tubes 2. Also, methods are possible in which the slats 1 are pushed onto the tubes 2 and the tubes 2 are then widened. The tubes 2 in one plane form a heat-conducting connection with the lamellae 1. A metallic connection is advantageous, since it conducts heat particularly well.
  • the slats 1 can also be made of metal, plastic and / or ceramic materials and can have a rectangular shape. There are also other forms of slats 1 or combination possible, such as round or oval slats 1.
  • the slats 1 are mounted substantially parallel to the tubes 2.
  • a substantially parallel arrangement may be an arrangement which deviates from an idealized parallel arrangement without the arrangement being designated as parallel by the average person skilled in the art. That is, within the meaning of the invention, an arrangement would be parallel, which deviates by 5 - 10 degrees from a parallel arrangement.
  • free passages 5 wherein the tube packages 2.1 and the free passages 5 are arranged alternately in the heat exchanger. In the free passages 5 no slats 1 protrude into, that is, the slats 1 do not connect each arranged in a plane pipe packages 2.1 with each other.
  • the heat exchange, or the heat exchange surface is supported by the inventive arrangement of the slats 1, wherein the shape and size of the slats 1, a constant and uniform distribution of heat is achieved on the slats 1. It is particularly advantageous that a refrigerant flowing through the heat exchanger can be well distributed in the heat exchanger, whereby the heat conduction and the heat exchange is improved. If the finned heat exchanger is used as a heat exchanger in an adsorber / desorber unit, a sorption material can be used in the
  • Heat exchangers are filled or possibly the tubes 2 and the fins 1 are coated with this. Especially by the free passages and the arrangement of the lamellae, the contact surface and thus the heat exchange surface between the sorbent material and the heat transfer medium is increased and that at the same time optimal accessibility for the refrigerant vapor.
  • the refrigerant may enter after entering the
  • Figure 3a) and b) show schematically a plan view and a side view of the segmented fin heat exchanger according to the invention with trays.
  • the structure of the finned heat exchanger is as in the figure 2a) and b) described.
  • 5 trays 6 are introduced into the free passages. This is particularly advantageous when the fin heat exchanger is used as an evaporator.
  • the shells 5 may also be advantageous when using the fin heat exchanger as a condenser or when the fin heat exchanger is integrated in an adsorber / desorber unit.
  • the person skilled in the art knows that the technical features of a heat exchanger used as an evaporator are also advantageous for the use of the heat exchanger as a condenser or as a heat exchanger in an adsorber / desorber unit.
  • the trays 5 or sumps or trays may be made of metal, plastic and / or ceramic materials and serve to hold and store refrigerant.
  • the tube packages 2.1 of the finned heat exchanger are in several levels arranged one above the other. Between two superimposed planes creates a free passage 5, wherein the tube packages are arranged 2.1 alternately with the free passages 5.
  • a shell 6 may be introduced, which advantageously has the same area as the tube packages 2.1, but can also occupy only part of the area or can be larger than the surface. Also, the shells 6 can be arranged so that they are not inserted in each free passage 5. This can be advantageous for small and compact fin heat exchangers.
  • the shells 6 can be fastened by way of seals, for example a rubber or adhesive seal, to the lamellae 1, the end plates 3 and / or the tubes 2.
  • the trays 6 may have overflow devices. The trays 6 fill with, for example, a liquid refrigerant and the overflow devices adjust the level of liquid in the tray 6 so as to prevent uncontrolled overflow of the tray 6.
  • Overflow devices may be used as spillways, which are vertically mounted to the bottom of each shell 6 and carry excess liquid fluid to a next underlying shell 6. Also dents or holes, which are inserted laterally in the shells 5, can control the liquid level.
  • the slats 1 of the tube packages 2.1 partially protrude into the fluid contained in the shells 5. It may also be advantageous if the tubes 2 and / or the lamellae 1 protrude into the liquid fluid. Due to the direct contact of the fluid with the
  • Slats 1 or the tubes 2 takes place an effective heat exchange between the fluid and the fins 1 or tubes 2.
  • the refrigerant accumulates in the shells 5. Due to the evaporation process begins a violent boiling on the surfaces of the tubes 2, with which the liquid refrigerant in contact.
  • refrigerant spatters are applied to exposed portions of the tubes 2 and the fins 1 in a thin film. The applied liquid film is vaporized on the surfaces of the tubes 2 and the fins 1 and thereby absorbs latent heat, whereby the flowing through the tubes 2 heat transfer medium is cooled.
  • the shells 5 may be designed such that they are beveled inwards at the edges, so that coolant splashes that arise on the surfaces of the tubes 2 and fins 1, do not get out of the shells 5.
  • baffles or baffles may be attached to the trays 5 to prevent spattering of the refrigerant.
  • the baffles can be arranged vertically on the underside of the shells 5, or also on the upper side of the shells 5.
  • Figure 4a) shows a side view of a fin heat exchanger described in the prior art. Slats 1 are mounted on the tubes 2, wherein the slats 1 connect the superposed tubes 2 vertically to each other, that is, there is a heat-conducting connection between the superposed tubes 2.
  • the slats 1 are spaced from each other and parallel to each other on the tubes. 2 arranged.
  • Steam 7 enters into the interstices of the fins 1 and flows along the surface of the fins 1.
  • the contact surface of the steam 7 is restricted with the tubes 2 by the limitation of the fins 1, whereby the heat exchange limited to the lying between the fins 1 area is.
  • the disadvantage here is further that the vapor flow of an introduced refrigerant is reduced by an occurring pressure loss.
  • Figure 4b shows a side view of a fin heat exchanger according to the invention with free passages.
  • tubes 2 are arranged one above the other in different planes, with free passages 5 being created between the tubes arranged one above the other.
  • the free passages 5 have a height greater than or equal to 0.5 cm, that is, if the distance between the superposed tubes 2 is greater than or equal to 0.5 cm.
  • Particularly advantageous may be a distance of 0.5 to 3 cm.
  • Slats 1 are mounted on the superposed tubes 2, wherein the slats 1 are advantageously arranged parallel to each other.
  • the slats 1 do not protrude into the free passages 5, that is, there is no heat-conducting connection via the slats 1 between the superposed tubes 2.
  • a flowing through the slats 1 steam 7 flows through the free passages 5, whereby a substantially constant vapor pressure and Consequently, steam flow can be maintained.
  • a substantially constant vapor pressure can preferably deviate from a mean value and is still referred to as constant.
  • the finned heat exchanger can be used as an evaporator, as a condenser and / or be integrated as a heat exchanger in an adsorber / desorber unit.
  • FIG. 5a shows a side view of a fin heat exchanger with a shell described in the prior art.
  • Slats 1 connect the tubes 2 arranged one above the other in a thermally conductive manner.
  • a shell 6 can be placed below the heat exchanger, that is, under the last in-plane tubes 2, whereby a liquid fluid 8 introduced into the heat exchanger is held by the shell 6 and stored.
  • the fluid contained in the shells 6 8 can be evaporated by supplying heat.
  • the fins 1 protrude into the shells 6 and the fluid 8 and supply heat to the fluid 8, whereby the fluid 8 changes its state of aggregation and passes into the vapor phase.
  • the arrangement of the fins 1 and tubes 2 disclosed in the prior art produces a pressure reduction of the vaporous fluid 8, whereby also the steam flow is reduced.
  • the contact area of the hot tubes 2 and the fluid 8 is small and the effectiveness of the evaporator is reduced.
  • the vapor flow of the vaporized fluid 8 may be lowered by the structure of the fins 1 and the arrangement of the tubes 2.
  • FIG. 5b shows a side view of a preferred fin heat exchanger according to the invention with shells inserted into the free passages. Slats 1 are attached to the superposed tubes 2, wherein between the superposed tubes 2 free passages 5 arise, in which the fins 1 preferably not protrude. So there is no heat-conducting connection over the
  • the preferred arrangement according to the invention of the tubes 2 and the fins 1, the use of the resulting free passages 5 is possible.
  • components can be introduced into the free passages 5.
  • a shell 6 can be inserted into the free passages 5.
  • the inserted shell 6 collects and stores a fluid 8 introduced into the fin heat exchanger, for example a refrigerant.
  • the number of shells 6 introduced can be varied and the shells 6 can be introduced into the free passages 5 alternately with the tubes 2 arranged one above the other.
  • the shells 6 made of metal, plastic or ceramic materials.
  • overflow devices can be introduced into the shells 6, which prevent overflow of the collected and stored fluid 8 and transfer from a certain level of fluid, the collected fluid 8 in the next underlying shell 6.
  • Overflow devices include holes, Pipes or dents.
  • the fins 1 are preferably in contact with the liquid collected in the trays 6. It may also be advantageous if the tubes 2 are in contact with the fluid 8 in the shells 6. Heat is transferred to the fluid 8 by the contact of the lamellae 1 and / or the tubes 2 with the fluid 8 collected in the shells 6, whereby the fluid 8 changes its state of aggregation and passes into the vapor phase.
  • a violent boiling may occur, wherein the fluid contained in the shells 6 8, for example, refrigerant, can spray on the slats 1 and possibly generates a liquid film there.
  • substantially the entire surface of the tubes 2 and fins 1 can be used as a heat exchange surface, whereby the effectiveness of the evaporator is improved.
  • the vaporized fluid 8 can flow through the preferred inventive arrangement of the fins 1, the tubes 2 and the free passages 5, the heat exchanger, wherein the arrangement of the free passages 5, a pressure loss is prevented and the steam flow is not affected. As a result, a particularly effective operation of the fin heat exchanger is possible.

Landscapes

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

Abstract

La présente invention concerne un échangeur thermique à lamelles comprenant (a) des paquets de tubes (2.1) qui se composent de plusieurs tubes (2) disposés dans un plan et parcourus par un liquide; et (b) des lamelles (1) espacées et parallèles entre elles et traversées par les tubes (2) disposés dans un plan respectif. Selon l'invention, entre les paquets de tubes (2.1) superposés sont formés des passages (5), les paquets de tubes (2.1) étant disposés dans plusieurs plans superposés en alternance avec les passages (5), et les paquets de tubes (2.1) horizontaux n'étant pas reliés de façon thermoconductrice par des lamelles (1).
PCT/DE2009/000949 2008-07-04 2009-07-03 Échangeur thermique compact à lamelles WO2010000255A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09772025A EP2313729A1 (fr) 2008-07-04 2009-07-03 Échangeur thermique compact à lamelles
DE112009002184T DE112009002184A5 (de) 2008-07-04 2009-07-03 Kompakter Lamellenwärmetauscher

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP08075610.9 2008-07-04
EP08075610 2008-07-04

Publications (2)

Publication Number Publication Date
WO2010000255A1 true WO2010000255A1 (fr) 2010-01-07
WO2010000255A4 WO2010000255A4 (fr) 2010-03-18

Family

ID=41258769

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/000949 WO2010000255A1 (fr) 2008-07-04 2009-07-03 Échangeur thermique compact à lamelles

Country Status (3)

Country Link
EP (1) EP2313729A1 (fr)
DE (1) DE112009002184A5 (fr)
WO (1) WO2010000255A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012062312A2 (fr) 2010-11-10 2012-05-18 Invensor Gmbh Machine frigorifique à adsorption entraînée par les gaz d'échappement
AT515972A1 (de) * 2014-05-20 2016-01-15 Josef Dipl Ing Dr Techn Masswohl Modularer Luft-Sole-Wärmetauscher

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1607171A (en) * 1923-05-02 1926-11-16 Bridgeport Rolling Mills Inc Radiator
JP2002340490A (ja) * 2001-05-18 2002-11-27 Denso Corp 熱交換器
WO2005106372A1 (fr) * 2004-04-28 2005-11-10 Daikin Industries, Ltd. Échangeur de chaleur par adsorption
EP1736725A1 (fr) * 2004-03-31 2006-12-27 Daikin Industries, Ltd. Échangeur thermique
EP1748259A1 (fr) * 2004-04-28 2007-01-31 Daikin Industries, Ltd. Échangeur de chaleur par adsorption

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1607171A (en) * 1923-05-02 1926-11-16 Bridgeport Rolling Mills Inc Radiator
JP2002340490A (ja) * 2001-05-18 2002-11-27 Denso Corp 熱交換器
EP1736725A1 (fr) * 2004-03-31 2006-12-27 Daikin Industries, Ltd. Échangeur thermique
WO2005106372A1 (fr) * 2004-04-28 2005-11-10 Daikin Industries, Ltd. Échangeur de chaleur par adsorption
EP1748259A1 (fr) * 2004-04-28 2007-01-31 Daikin Industries, Ltd. Échangeur de chaleur par adsorption

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012062312A2 (fr) 2010-11-10 2012-05-18 Invensor Gmbh Machine frigorifique à adsorption entraînée par les gaz d'échappement
AT515972A1 (de) * 2014-05-20 2016-01-15 Josef Dipl Ing Dr Techn Masswohl Modularer Luft-Sole-Wärmetauscher
AT515972B1 (de) * 2014-05-20 2016-04-15 Josef Dipl Ing Dr Techn Masswohl Modularer Luft-Sole-Wärmetauscher

Also Published As

Publication number Publication date
WO2010000255A4 (fr) 2010-03-18
DE112009002184A5 (de) 2011-06-09
EP2313729A1 (fr) 2011-04-27

Similar Documents

Publication Publication Date Title
EP2476975B1 (fr) Dispositif de transfert thermique pour un véhicule
AT12048U1 (de) Vorrichtung zur übertragung von wärme
WO2009007168A1 (fr) Système d'échange de chaleur doté d'un échangeur de chaleur et procédé de fabrication d'un système d'échange de chaleur
EP0131270A1 (fr) Absorbeur utilisant une matière solide pour un cycle d'absorption
EP2225527B1 (fr) Système d'échange de chaleur
WO2007098904A2 (fr) Thermopompe a absorption, refrigérateur a absorption, et leurs éléments adsorbeurs
DE112014004473T5 (de) Kältespeicher-Wärmetauscher
WO2012069048A2 (fr) Cuve à vide permettant d'éliminer les gaz étrangers d'une machine frigorifique à adsorption
EP1920202B1 (fr) Ensemble de plaques d'echange thermique en contact thermique avec un adsorbant
DE102007034710B4 (de) Zweistufiger Absorptionskühler
DE102020007211A1 (de) Adsorptionskältevorrichtung und Verfahren zum Erzeugen von Adsorptionskälte aus Wärme
WO2015014772A1 (fr) Module d'adsorption
EP2558186A1 (fr) Dessiccateur cryogénique, en particulier dessiccateur cryogénique d'air comprimé, et échangeur de chaleur pour un dessiccateur cryogénique, en particulier pour un dessiccateur cryogénique d'air comprimé
EP2313729A1 (fr) Échangeur thermique compact à lamelles
DE112017000646T5 (de) Luftgekühlter Plattenrippe-Phasenänderungs-Radiator mit zusammengesetzen Kapillarrillen
EP2606292A1 (fr) Module de condenseur à réfrigérant
EP2622286A2 (fr) Dispositif de recirculation de condensat d'une machine frigorifique à adsorption
DE19645475B4 (de) Periodisch arbeitende Adsorptionswärmepumpe, Adsorptionskältemaschine oder Adsorptionswärmetransformator
DE19522250A1 (de) Verfahren zum Betrieb von Wärmepumpen und Kältemaschinen
WO2010000311A1 (fr) Bloc échangeur thermique et procédé de fabrication d'un bloc échangeur thermique
EP3333507A1 (fr) Dispositif formant évaporateur
EP3025111A1 (fr) Tube collecteur pour dispositif échangeur de chaleur, dispositif échangeur de chaleur et procédé de purge d'un dispositif échangeur de chaleur
EP3002530B1 (fr) Échangeur thermique, dispositif d'échangeur thermique et procédé d'utilisation d'un échangeur thermique
WO2011073762A2 (fr) Échangeur de chaleur
DE10297119B4 (de) Kondensator, Verdampfer und Kühlvorrichtung

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09772025

Country of ref document: EP

Kind code of ref document: A1

REEP Request for entry into the european phase

Ref document number: 2009772025

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2009772025

Country of ref document: EP

REF Corresponds to

Ref document number: 112009002184

Country of ref document: DE

Date of ref document: 20110609

Kind code of ref document: P

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112009002184

Country of ref document: DE

Effective date: 20110609