WO2011101112A1 - Système d'échangeurs thermiques - Google Patents

Système d'échangeurs thermiques Download PDF

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Publication number
WO2011101112A1
WO2011101112A1 PCT/EP2011/000669 EP2011000669W WO2011101112A1 WO 2011101112 A1 WO2011101112 A1 WO 2011101112A1 EP 2011000669 W EP2011000669 W EP 2011000669W WO 2011101112 A1 WO2011101112 A1 WO 2011101112A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
volume
housing
support structure
modules
Prior art date
Application number
PCT/EP2011/000669
Other languages
German (de)
English (en)
Inventor
Christian Behrle
Original Assignee
Fischer Eco Solutions 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 Fischer Eco Solutions Gmbh filed Critical Fischer Eco Solutions Gmbh
Priority to EP11708695A priority Critical patent/EP2536990A1/fr
Publication of WO2011101112A1 publication Critical patent/WO2011101112A1/fr

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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0075—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the same heat exchange medium flowing through sections having different heat exchange capacities or for heating or cooling the same heat exchange medium at different temperatures
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0083—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1653—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies

Definitions

  • the invention relates to a heat exchanger system comprising at least a first heat exchanger and at least one second heat exchanger, wherein each heat exchanger comprises at least one housing with two connection sides and a plurality of pipes extending between the connection sides as the heat exchanger surface, wherein the inner pipe volume of the pipes via the connection sides of the heat exchanger is accessible and the housing defines the tube outer volume of the heat exchanger.
  • Such heat exchanger systems are used, for example, for seawater desalination.
  • the zugebowte seawater is heated, for example, with the waste heat of a power plant on the surface of pipes of a heat exchanger.
  • the brine heated in the so-called brine heater evaporates in downstream expansion stages under reduced pressure, whereby the water vapor precipitates as condensate within the pipes of the stages and can be withdrawn as salt-free water.
  • the salt-enriched water produced by the evaporation process is also called brine.
  • CONFIRMATION COPY Stem which is optimized both fluidically and thermally.
  • the aforementioned object is achieved in a heat transfer system according to the invention characterized in that the tube outer volume of the first heat exchanger with the Roiirinnenvolumen the second heat exchanger is connected by the second heat exchanger is sealingly attached to a connection side to the housing of the first heat exchanger.
  • the first heat exchanger has, for example, in its housing an opening which is provided in addition to the openings on the connection sides of the first heat exchanger.
  • the second heat exchanger is thereby sealingly attached to the housing of the first heat exchanger with a first connection side - encompassing the opening in the housing of the first heat exchanger, so that, for example, steam present in the pipe outer volume of the first heat exchanger can enter the interior volume of the second heat exchanger.
  • outside pipe volume the volume surrounding all the pipes of the respective heat exchanger is always meant, which is limited by the housing of the corresponding heat exchanger.
  • the internal pipe volume of a heat exchanger describes the sum of the volumes of the individual pipes of a heat exchanger, wherein the individual volumes of the pipe and consequently also the internal pipe volume are accessible via the connection sides of a heat exchanger.
  • seawater desalination is always used for the description, in which, for example, salty seawater is evaporated on the surface of pipelines, the resulting vapor is then condensed in other pipelines and discharged as desalted or salt-free water.
  • this application example is by no means intended to be restrictive, since a multiplicity of other possible applications for a heat exchanger system according to the invention is also conceivable.
  • a hot medium such as hot water from a power plant, through the pipes - passed through the pipe internal volume - the first heat exchanger.
  • the hot medium heats the pipes of the first heat exchanger, so that salty water, which is trickled or sprayed in the first heat exchanger or in the pipe outer volume of the first heat exchanger, evaporated on the hot surfaces of the pipes of the first heat exchanger.
  • the water vapor thus produced in the tube outer volume of the first heat exchanger now passes through the opening in the housing of the first heat exchanger in the pipes of the second heat exchanger connected directly to the housing of the first heat exchanger with a first connection side, so that the steam in the pipe inner volume of the pipes of the second Heat exchanger occurs.
  • the increasingly saline water, which does not evaporate on the surfaces of the pipes, collects in the lower part of the housing of the first heat exchanger and is discharged from there.
  • the steam now present in the internal volume of the pipe of the second heat exchanger is produced by trickling a cold medium, e.g.
  • a cold medium e.g.
  • salt water is again condensed in the tube outer volume of the second heat exchanger so that salt-free water emerges from the tube internal volume of the second heat exchanger at the second connection side of the second heat exchanger facing away from the first heat exchanger and can be removed therefrom.
  • the heat energy of the condensed within the second heat exchanger water vapor is transferred to the trickled in the outer tube volume of the second heat exchanger medium, so for example to the salted water there, so that in the outer tube volume of the second heat exchanger again water vapor is formed, which is preferably fed to a further use.
  • a conceivable further use is the condensation of this vapor from the tube outer volume of the second heat exchanger, so that this steam can be condensed and removed as salt-free water.
  • the hot medium required for the first evaporation which is passed through the tube internal volume of the first heat exchanger, enters the inside volume of the first heat exchanger on the first connection side of the first heat exchanger and subsequently exits the inside volume of the tube on the second connection side of the first heat exchanger and is discharged.
  • the heat energy has given off the hot medium for evaporation to the salt water sprayed in the tube outer volume of the first heat exchanger.
  • the heat energy transferred from the hot medium to the salt water is thus the original output energy which is fed to the process and subsequently transferred for further evaporation or condensation in different stages, with a slight loss of heat energy always occurring at each transfer step.
  • the immediate connection of the second heat exchanger with a connection side to the housing of the first heat exchanger or by connecting the outer tube volume of the first heat exchanger with the inner tube volume of the second heat exchanger by the direct connection has the advantage that dispenses with the use of a fluidically and thermally unfavorable Umlenkhaube can be. Consequently, the heat losses occurring at a deflecting hood are prevented and an optimal utilization of the heat energy is realized, apart from the fact that the omission of the hoods offers constructional and economic advantages.
  • the arrangement of the first and the second heat exchanger relative to each other can take place in various ways, wherein an advantageous arrangement is characterized in that at least one connection side of the housing of at least one of the two heat exchangers two separate openings are provided, namely a first opening for connection the Roiirinnenvolumens and a second opening for connection of the tube outer volume.
  • the first and second heat exchangers are arranged rectified, ie, the longitudinal sides of the heat exchanger are parallel to each other, but the heat exchangers are mutually offset with respect to their width and are thus interconnected only over a portion of the connection side.
  • the offset takes place in such a way that the housings of the heat exchangers overlap at their end faces or at the connection sides approximately with half their width.
  • the width of the overlap of the heat exchanger on the front side can vary.
  • the frontal overlap of the first and the second heat exchanger is less than half the width of a heat exchanger, so that in each case on a longitudinal side of a heat exchanger results in a narrow area, the belongs to the pipe outside and in which no pipes are included.
  • the width of this area corresponds - as in the previous embodiment - about the overlap of the two heat exchangers.
  • This narrow area serves for steam guidance, in particular for the second opening on the second connection side of the first heat exchanger.
  • a collecting space is provided, which is sealed to the pipe outer space of the second heat exchanger.
  • the vapor from the outer pipe space of the first heat exchanger then passes through the second opening on the connection side in the Sammehaum of the second heat exchanger and from there into the inner tube volume of the second heat exchanger can occur uniformly.
  • the second heat exchanger has an area in its outer tube volume, in which there are no pipes, so that the outer tube volume of the second heat exchanger is connected to the inner tube volume of a third heat exchanger.
  • the second heat exchanger is attached to a connection side with a flange on the housing of the first heat exchanger, wherein in particular a Flat gasket between the connection side of the second heat exchanger and the housing of the first heat exchanger is arranged. Due to the flange connection, the second heat exchanger can be screwed with its connection side to the housing of the first heat exchanger, whereby a detachable but reliable connection is realized.
  • connection side surrounding the flange is provided on the second heat exchanger, which can be passed by screws for attachment to the housing of the first heat exchanger, wherein the housing of the first heat exchanger corresponding threads or receptacles are provided for the screws.
  • the first connection side of the second heat exchanger is screwed to the flange with the housing of the first heat exchanger, that the connection side of the second heat exchanger, from which the inner tube volume of the second heat exchanger is accessible, the opening in the housing of the first heat exchanger completely covers, so that from the Pipe outside volume of the first heat exchanger through the opening exiting steam can enter only in the inner tube volume of the second heat exchanger.
  • a flat gasket is arranged, preferably the opening in the housing of completely surrounds the first heat exchanger.
  • connection side of the second heat exchanger is then placed for attachment to the gasket and the second heat exchanger bolted to the first heat exchanger, creating a sealing connection between the heat exchangers.
  • the housing of the heat exchanger are configured cuboid, in particular the connection sides are provided on two opposite end sides. Due to the parallelepiped configuration of the heat exchanger, for example, the second heat exchanger can be fastened with its connection side on a side surface of the housing of the first heat exchanger, wherein it is advantageous that both the connection side of the second heat exchanger and the side surface of the first heat exchanger due to the cuboid configuration is flat.
  • Side surfaces are the surfaces that extend parallel to the pipes as side surfaces of the cuboid, if the connection sides are provided at the end faces of the pipes. It then follows that - in straight pipes - the connection sides of the heat exchanger are opposite or positioned on opposite end faces.
  • the second heat exchanger is fastened with one of its connection sides on the housing of the first heat exchanger, in particular if the heat exchanger is configured cuboid, then it follows that in this arrangement, the pipes of the first heat exchanger are arranged orthogonal to the pipes of the second heat exchanger.
  • the housings of the heat exchangers have an angular base surface, that is, the base of a heat exchanger has, for example, the shape of an L, resulting in advantageous nested arrangement possibilities of the first heat exchanger relative to the second heat exchanger. While the shape of an L has an angle of 90 °, depending on the field of application, all other angles between 0 ° and 90 ° can be realized.
  • the second heat exchanger be in the end region facing away from a first connection side of the first heat exchanger. of the housing of the first heat exchanger Tragers is attached. It is advantageous if the second heat exchanger is fixed in an end region of the housing of the first heat exchanger, which is remote from the inlet side of a medium in the inner tube volume, so that an optimal evaporation is ensured on the surface of the pipes.
  • the medium entering the internal volume of the pipe of the first heat exchanger is hottest at the inlet side into the inside volume of the pipe and cools down in the course to the second connection side, that is to the outlet side.
  • the second heat exchanger is therefore preferably attached in the end region in the direction of the outlet side, namely where the guided in the inner tube volume of the first heat exchanger medium is already cooled or condensed.
  • an angle module is provided so that the first heat exchanger and the second heat exchanger are not orthogonal to each other can be arranged. It is preferably provided that the second heat exchanger directly, d. H. fastened without fasteners, with one of its terminal sides to the housing of the first heat exchanger. However, if spatial conditions make it necessary for the heat exchangers to be oriented at an angle other than 90 ° to one another, then it is provided that an angle module is arranged between the first heat exchanger and the second heat exchanger, so that the gap formed between them by the angled arrangement bridged and sealed first and second heat exchanger. Preferably, in such an arrangement, the second heat exchanger is already designed at an angle on one of its connection sides, so that a direct connection between the two heat exchangers is ensured.
  • the steam produced in the second heat exchanger by the condensation of the medium guided inside the inner volume of the second heat exchanger in the outer volume of the second heat exchanger can be transferred to a connection side to the housing of the second heat exchanger second heat exchanger connected third heat exchanger, in particular in the inner tube volume, are introduced.
  • this third heat exchanger evaporation of salt water sprayed in the outer volume of the third heat exchanger takes place again by releasing the heat energy of the steam present in the inner volume of the third heat exchanger to the salt water, so that steam is again generated in the outer volume of the third heat exchanger.
  • This vapor is subsequently passed into the inner tube volume of a fourth heat exchanger, which is connected to the housing of the third heat exchanger.
  • This chain of evaporation of salt water by the condensation of water vapor already generated can be continued in an arbitrarily long chain of sequentially inventively arranged heat exchangers.
  • the number of so connected in series heat exchanger is limited only by the originally introduced heat energy and by the resulting pressure losses.
  • a condenser is attached, which completely condenses the steam generated in the pipe outer volume of the last heat exchanger, which is caused by the condensation in a preceding heat exchanger, by the use of a cooling medium, such as seawater, so that the Cascade of heat exchangers arranged one behind the other ends.
  • the condenser is designed substantially like a heat exchanger, but is preferably somewhat smaller in its outer dimensions.
  • the condenser is connected with its outer pipe volume to the pipe outer volume of the last heat exchanger, so that the steam which arises in the pipe outer volume of the last heat exchanger passes directly into the pipe outer volume of the condenser. Subsequently, the cooling medium carried in the Roiirinnenvolumen the condenser completely condense the remaining vapor.
  • an arrangement has been found in which eight heat exchangers are arranged one behind the other, in particular, the respective subsequent heat exchanger is arranged at an angle of about 90 ° to the preceding heat exchanger.
  • the respective subsequent heat exchanger is arranged at an angle of about 90 ° to the preceding heat exchanger.
  • the heat exchanger are mounted to each other movable after releasing the connection, in particular on a rail system are movable.
  • This configuration makes it possible that a heat exchanger, after it is released from its connections with pipelines or other heat exchangers, can be moved out of its position, so that, for example, other heat exchangers, pipes, but also in the assembled state inaccessible sides of the dissolved heat exchanger for Maintenance and repair purposes are accessible.
  • the heat exchanger is for this purpose, for example, mounted on rollers, which are guided by a guide rail, so that the heat exchanger, for example, at an angle of 90 ° to the longitudinal extent of its pipes moving. becomes bar. In the assembled state or in the operating state, the rollers are blocked or the heat exchanger, for example, otherwise supported or lowered, so that no vibrations or displacements of the heat exchanger can arise.
  • the heat exchanger each having a plurality of pipes as a heat transfer surface, wherein at least one connection side of the heat exchanger at least one sealing connection can be produced
  • the heat exchanger at least two heat exchanger modules and at least one support structure are included
  • the Heat exchanger modules each comprise pipes and at least one tube plate, wherein the pipes are connected in their end regions via the tube plate, wherein the heat exchanger modules are fastened to the tube plates in the support structure such that the inner tube volume of the second heat exchanger with the tube outer volume of the first heat exchanger connectable and the outside pipe volume of the second heat exchanger is sealed against the pipe outside volume of the first heat exchanger, and wherein the support structure absorbs the heat surrounds transformer modules such that a part of the forces is removed from the support structure.
  • the heat exchanger described above is based on the idea of separating the heat-transferring components or the heat-transferring system from the force-transmitting components or relieving the heat-transferring components significantly from the structural tasks.
  • the heat-transferring components could be designed almost exclusively to transfer heat optimally, while the force-transmitting components can be designed to optimally remove the forces generated in the system.
  • the pipelines of the heat exchanger modules are relieved of the transmission of force, so that a transfer of the forces to be transmitted from the pipelines to the support structure takes place.
  • the heat exchanger modules can not be completely freed from any transmission of power, however, with a construction according to the invention a significant relief of perennialachid- take place modules, so that the heat exchanger modules in general, but in particular the pipes must be made less massive.
  • the heat exchanger modules, as heat-transmitting components, in this case consist of a specific plurality of pipelines, which are connected to each other with at least one tube plate in their end regions and combined to form a tube bundle.
  • the heat exchanger modules are surrounded in the assembled state of the heat exchanger of the support structure, so that the outlet or inlet cross sections of the pipes can be connected to the tube outer volume of a heat exchanger, wherein the guided in the inner tube volume medium is sealed against the medium flowing around the pipes.
  • the resulting in the heat exchanger from pressure or from the flowing medium forces are removed from the surrounding the heat exchanger modules support structure, so that the pipelines are substantially relieved of the power transmission.- This relief of the piping and tube plates of the power transmission causes the Overall, pipelines and the tube plates can be constructed of much thinner material, which leads to a significant material savings and optimized heat transfer.
  • the piping, the tube plates and the support structure are preferably made of a stainless steel or a stainless steel.
  • the pipelines are additionally relieved by arranging the support structure between the heat exchanger modules in such a way that forces occurring on the connection side of the heat exchanger formed from a plurality of tube plates and the supporting structure are removed uniformly distributed over the connection side, in particular of the Support structure to be removed.
  • the support structure forms a uniform grid or grid structure, which divides the connection surface for the connection to the heat exchanger in uniform fields with a small area, wherein at least at the intersection points of the support structure, the forces in the axial longitudinal direction of the heat transfer. be removed.
  • the size of a field corresponds essentially to the size of a tube plate. The same applies to the stability of the first heat exchanger in the region of the opening for the connection of the second heat exchanger.
  • the lattice-like structure of the support structure ensures a simple connection of the tube outer volumes of the individual heat exchanger modules to a global outer tube volume.
  • the heat exchanger modules are used for this purpose in the three-dimensional support structure, so that the heat transfer module and in particular the tube plate are uniformly surrounded by the support structure.
  • the second heat exchanger is preferably fastened to the support structure.
  • the heat exchanger modules in each case have at least two tube plates which connect the pipelines in their end regions with one another, wherein preferably the pipelines are straight.
  • the heat exchanger module has in its longitudinal extension at both ends in each case a tube plate, which connect the pipes together, so that from the unit of tube plates and pipes, a symmetrical heat exchanger module is formed.
  • the pipes are straight, so that at both ends of the heat exchanger in its axial longitudinal extent - at the end faces - each formed by the tube plate, a segment of a connection side, wherein at one end of the medium inlet and at the other end of the Medium outlet is located.
  • the pipelines preferably terminate flush with the tube plate, so that the tube plate represents the interface of the heat exchanger modules to the support structure.
  • the tubesheets preferably terminate flush with the support structure at both ends and are sealingly connected thereto.
  • the heat exchanger modules are preferably arranged horizontally and parallel to each other in the support structure and are of this - in the vertical Direction - supported. In addition to this support function of the support structure, forces occurring and removed by the support structure in addition in the longitudinal direction of the pipes in the axial longitudinal direction of the heat exchanger are absorbed and removed, so that the pipelines are relieved of forces.
  • the connection between the support structure and the tube plate is in each case designed to be sealing, so that the connection sides are altogether tight.
  • planar components in particular plates or sheets - fixed so that the sheet-like elements extend in a membrane over the support structure and limit the pipe outside volume.
  • the housing would be compressed if not sufficiently supported if the thickness of the material is insufficient. Due to the support structure, the outer housing is supported for both internal and external overpressure.
  • the support structure of the heat exchanger can be configured in different ways. According to a preferred embodiment, it is provided that the support structure consists of a frame, wherein the frame forms a plurality of spatially arranged cuboids, in particular the frame formed transversely and longitudinally to the heat exchanger modules profiles, wherein the profiles are connected to each other at their ends, preferably positive, non-positive or cohesive.
  • the support structure consists of a frame which is formed essentially of blocks. The cuboids are created by arranging and connecting the profiles longitudinally and transversely to the heat exchanger modules or the pipelines.
  • the profiles can be the same or different and can be modular to any number of side by side, one behind the other and superimposed cubes composed.
  • the profiles are arranged transversely and longitudinally to the heat exchanger modules, so that the profiles during insertion of the heat exchanger module in the frame does not hinder the insertion.
  • the support structure can also be formed from longitudinal profiles whose length substantially corresponds to the length of the heat exchanger modules. Between the parallel to the heat exchanger modules arranged longitudinal profiles horizontally and vertically extending transverse profiles are arranged, which fasten the longitudinal profiles spaced from each other and absorb forces transverse to the longitudinal extent of the heat exchanger modules.
  • the axial forces in the direction of the longitudinal extent of the heat exchanger modules are supported by the longitudinal profiles. Due to the construction of profiles, the size of the frame - the supporting structure - can be expanded and adjusted as required depending on the application. For the profiles, any profile shapes can be used, in particular open, closed, semi-open, flat profiles or angle profiles.
  • the support structure comprises planar housing modules and cross connectors, wherein the jeweihgen housing modules with the cross connectors are interconnected, in particular, the cross connector support the housing modules as an inner frame.
  • the housing modules are preferably configured as plates, which are interconnected with the cross connectors.
  • the transverse connectors in particular have a length which corresponds to the width of a heat exchanger module, so that a plurality of heat exchangers can be introduced one above the other in the assembled state between two housing modules.
  • the heat exchanger modules are preferably also on the connecting the housing modules cross connectors.
  • the outer housing modules form the outer housing of the heat exchanger. Overall, formed between the housing modules, an inner framework of cross connectors, which are preferably positive, cohesive or materially connected to the housing modules, so that both outer and inner overpressures can be supported by this support structure.
  • the support structure surrounds the heat exchanger modules in such a way that with the exception of the hydrodynamic and hydrostatic forces on the tube plate, the forces are removed from the support structure.
  • the heat exchanger modules are sealingly connected to the support structure, however, no appreciable forces may be transmitted through the seal, so that the forces are essentially removed from the support structure. Only the forces acting on the tube plate present between the end faces of the pipelines are transmitted via the heat exchanger module, i. H. in the axial direction over the pipes, removed; the seal between support structure and heat transfer module transmits substantially no forces.
  • the heat exchanger modules are preferably mounted in a floating manner within the support structure, with the attachment to a second heat exchanger taking place exclusively via the support structure.
  • the sealing of the floating bearing can be done, for example, via a sealing lip surrounding the tube plate, which follows the movement of the heat exchanger module within the support structure.
  • the heat exchanger modules are not arranged in the entire support structure in a heat exchanger, but there are only heat exchangers in selected fields arranged the support structure.
  • the support structure thus fills the entire housing of the heat exchanger, but for example, only in one half of the support structure heat transfer modules are introduced and fixed.
  • the common area of the faces of the heat exchanger module, namely the sum of the tube plates then forms the area of the connection side of the heat exchanger, which allows the connection of the inner tube volume.
  • the fields of the support structure, in which no heat transfer module is arranged serve in addition to the volume between the pipes as pipe outer volume.
  • the end face of the region of the pipe outer volume, in which no pipes run, is used in such an arrangement of the heat exchanger to each other the connection of the inner tube volume of a subsequent - for example, second - heat exchanger.
  • the entire housing of the heat exchanger system is likewise filled with a supporting structure, but the tube plates of the heat exchanger modules are only in the second level from the front side the honeycomb-shaped support structure, so that the Sammerraum is formed in the support structure and the collecting space is sealed by the tube plates relative to the tube outer volume of the heat exchanger.
  • the region of the pipe outer volume, in which there are no longitudinally arranged pipes, preferably has the width of a heat exchanger module, namely in that a vertical row of the support structure is not filled with heat exchanger modules.
  • FIG. 1 shows an exemplary embodiment of a heat exchanger system in a perspective side view
  • FIG. 2 shows a further exemplary embodiment of a heat exchanger system in a perspective side view
  • Fig. 3 shows the exemplary embodiment of a heat exchanger system according to FIG. 2 in a plan view
  • FIG. 4 shows an embodiment of a support structure with heat exchanger modules for a heat exchanger of a heat exchanger system.
  • FIGS. 1 to 3 show exemplary embodiments of heat exchanger systems 1 with a first heat exchanger 2 and a second heat exchanger 3, each heat exchanger 2, 3 each having a housing 4 with two connection sides 5.
  • 4 shows an exemplary embodiment of an internal structure of a heat exchanger 2, 3 with pipelines 6 extending between the connection sides 5 as a heat exchanger surface.
  • the course of the process or the course of the flow is always described by the first heat exchanger 2 in the direction of the second heat exchanger 3, etc., whereby a reverse course is also provided.
  • FIG. 1 shows that the second heat exchanger 3 is fastened with a first connection side 5 a in the side region 7 of the first heat exchanger 2.
  • the first heat exchanger 2 has in its housing 4 in the side region 7 an opening through which steam emerging in the tube outer volume of the first heat exchanger 2 can enter the tube interior volume of the second heat exchanger 3.
  • the second heat exchanger 3 is arranged at an angle of approximately 90 ° to the first heat exchanger 2 in the end region of the side surface 7 facing away from the first connection side 5a of the first heat exchanger 2. Due to this direct arrangement of the second heat exchanger 3 on the housing 4 of the first heat exchanger 2, a deflection hood which is otherwise customary in the prior art can be dispensed with.
  • the internal pipe volume of the pipes 6 present in the heat exchangers 2, 3 is accessible in each case via the connection sides 5 of the heat exchangers 2, 3.
  • the outside pipe volume, which surrounds the pipes 6 and is defined by the housing 4 of the heat exchangers 2, 3, is sealed from the environment.
  • a hot medium entering into the tube internal volume of the first heat exchanger 2 on the first connection side 5a heats the pipelines 6 in its course within the first heat exchanger 2 the first heat exchanger 2, so that within the outer tube volume of the first heat exchanger 2 sprayed medium, for.
  • salt water evaporated on the surfaces of the pipes 6, so that within the pipe outer volume of the first heat exchanger 2 water vapor is formed.
  • a spray device provided for this purpose is not shown.
  • the heat energy of the guided in the inner tube volume of the first heat exchanger 2 hot medium in the course of the first connection side 5a to the second connection side 5b of the first heat exchanger 2 is partially transferred to the salt water to be evaporated and cooled the hot medium in the inner tube volume.
  • the second heat exchanger 3 is fixed with a flange on the first heat exchanger 2, wherein between the two heat exchangers 2, 3 is arranged a flat gasket, not shown in detail.
  • This flat gasket can be used advantageously in that both the first heat exchanger 2 and the second heat exchanger 3 comprises a housing 4, which is configured cuboid, so that the heat exchanger 2, 3 can be attached to each other in a simple manner.
  • Fig. 2 shows an embodiment of a heat exchanger system 1 with a total of eight successively arranged heat exchangers.
  • a second heat exchanger 3 is arranged, wherein at the second heat exchanger 3, a third heat exchanger 8, and at the third heat exchanger 8, a fourth heat exchanger 9 is arranged.
  • a fourth heat exchanger 9 is arranged at the fourth heat exchanger 9 is - again - at an angle of 90 °, a fifth heat exchanger 10, to the fifth heat exchanger 10, a sixth heat exchanger 11, to the sixth heat exchanger 11, a seventh heat exchanger 12 and finally to the seventh heat exchanger 12, an eighth heat exchanger 13th arranged.
  • a capacitor 14 is attached.
  • the heat exchangers 2, 3, 8, 9, 10, 11, 12, 13 are arranged such that viewed always in the direction of flow of the inner tube volume, ie here in the ascending direction of the numbering of the heat exchanger 2, 3, 8, 9, 10, 11, 12, 13, in each case bounded by the housing 4 outer tube volume of the respective preceding heat exchanger with the inner tube volume of the subsequently arranged heat exchanger is connected.
  • the heat exchanger 2, 3, 8, 9, 10, 11 » , 12, 13 are - as shown in FIG. 2 - always arranged such that the heat exchanger are arranged at an angle of about 90 ° to each other, so that the subsequent heat exchanger always connected in the side area of a preceding heat exchanger.
  • a deflecting hood for deflecting a media flow between two heat exchangers is dispensable by this arrangement.
  • the steam produced in the last, eighth heat exchanger 13 in the pipe outer space is finally completely condensed in the condenser 14.
  • the tube outer volume of the eighth heat exchanger 13 is connected to the tube outer volume of the condenser 14.
  • a cooling medium is passed, which enters at an inlet side 15a in the inner volume of the tube 14 of the condenser 14 and warmed on an outlet side 15b emerges from the condenser 14, wherein the present in the pipe outer volume of the condenser 14 is completely condensed thereby vapor and can be dissipated in liquid form at the bottom of the capacitor 14.
  • FIG. 3 shows the embodiment according to FIG. 2 in a plan view, wherein FIG. 3 shows the arrangement of the individual heat exchangers 2, 3, 8, 9, 10, 11, 12, 13 at an angle of approximately 90 ° to one another , Consequently, the steam generated in the outer pipe space of a heat exchanger is always introduced directly from the pipe outlet of a heat exchanger into the inner pipe volume of the downstream condenser. Pairing according to the understanding of the present invention thus results between the heat exchangers 2 and 3, 3 and 8, 8 and 9, 9 and 10, 10 and 11, 11 and 12 and finally between 12 and 13.
  • the condenser 14 is parallel arranged to the eighth heat exchanger 13, so that the tube outer volume of the eighth heat exchanger 13 is connected via an opening in the housing 4 of the eighth heat exchanger 13 with the outside pipe volume of the condenser 14.
  • Fig. 4 shows an embodiment of an internal structure of a heat exchanger 2, 3, 8, 9, 10, 11, 12, 13, wherein in each case a plurality of pipes 6 are provided as a heat transfer surface.
  • the pipes 6 are arranged such that their end faces are each arranged on the connection sides 5.
  • a plurality of heat exchanger modules 16 are arranged, which are supported by a support structure 17.
  • Each heat transfer module 16 includes a plurality of conduits 6 bundled over two tube plates 18 located in the end regions are.
  • the heat exchanger modules 16 are thereby removed individually from the support structure 17 and thus also from the heat exchanger.
  • the heat exchanger modules 16 are fastened in the support structure 17 in such a way that the inside volume of the second heat exchanger 3 can be connected to the outside volume of the first heat exchanger 2, whereby the tube plates 18 of the heat exchanger modules 16 form the connection sides 5 of the heat exchanger.
  • the support structure 17 surrounds the heat exchanger modules 16 such that a part of the forces occurring during operation is removed from the support structure 17.
  • the support structure 17 is for this purpose arranged between the heat transfer modules 16, that the forces occurring on the connection sides 5 are removed evenly distributed over the connection sides 5, in particular be removed from the support structure 17.
  • the housing 4 of a heat exchanger 2, 3, 8, 9, 10, 11, 12, 13 can be fastened to the support structure 17 shown in FIG. 4, so that the connection sides 5 are formed on the end faces of the pipeline modules 16.
  • an opening in the housing 4 is provided, which serves for the connection of the outer tube volume with the inner tube volume of the subsequent heat exchanger connected to this opening.
  • the support structure 17 has the advantage that no instability of the heat exchanger is created by the opening in the housing 4, since the housing 4 is supported evenly from the inside by the support structure 17.
  • the support structure 17 is formed from transversely and longitudinally to the heat exchanger modules 16 arranged profiles, in particular transverse profiles 20 and longitudinal profiles 21. Due to the existing of the cross sections 20 and longitudinal sections 21 support structure 17 of the pipes 6 almost no forces must be borne.
  • the heat exchanger modules 16 are in the illustrated state not sealingly connected to the support structure 17, for which in the embodiment shown preferably a - not shown - mask would be necessary, however, the support structure 17 may also be configured such that can be dispensed with such an additional mask ,
  • the illustrated exemplary embodiment of a heat exchanger clearly shows that the connection side 5 is subdivided into a plurality of fields whose size substantially corresponds to the size of the tube plates 18 with the support structure 17 arranged therebetween. By this configuration, the connection side 5 can be arbitrarily increased, without resulting in losses in terms of stability.
  • the forces occurring in the axial direction of the heat exchanger modules 16 are reliably removed from the longitudinal profiles 21 of the support structure 17.
  • the heat exchanger modules 16 are movably mounted in the support structure 17 in the axial direction.
  • FIG. 5 shows an embodiment of a heat exchanger system 1 with heat exchangers 2, 3, 8, which are rectified, but offset with respect to their width to each other, in particular by about half the width of a heat exchanger 2, 3, 8.
  • the heat exchanger 2, 3, 8 are each constructed so that in a housing 4 in each case on one half of the width - in the non-hatched areas - are longitudinally extending pipes whose inner tube volume is accessible via the terminal sides of the non-hatched areas.
  • the pipelines consequently run between the connection sides of a heat exchanger 2, 3, 8.
  • the hatched areas in FIG. 5 belong to the pipe outside volume, but there are no pipelines in the hatched areas.
  • On the front side of the hatched areas - on the connection side - is the first heat exchanger
  • the tube outer space of the first heat exchanger 2 is connected via an opening on the connection side with the inner tube volume of the second heat exchanger 3 in connection. The same applies to the connection between the second heat exchanger
  • Fig. 6 shows as well as Fig. 5 shows an exemplary embodiment of a heat exchanger system 1 with rectified heat exchangers 2, 3, 8, but wherein the outer tube volume has a much narrower area in which there are no pipes - hatched area - and wherein the heat exchanger 2, 3rd or the heat exchangers 3, 8 are connected to one another via the connection sides within this hatched area of the housing 4.
  • the steam From the hatched area of the heat exchanger 2 - Part of the outer tube volume - the steam enters the front side into a plenum of the heat exchanger 3, wherein the plenum is directly connected to the inner tube volume of the heat exchanger 3 and is sealed against the outer tube volume of the heat exchanger 3.

Abstract

L'invention concerne un système d'échangeurs thermiques (1) comportant au moins un premier échangeur thermique (2) et au moins un deuxième échangeur thermique (3), chaque échangeur thermique (2, 3) comprenant au moins un boîtier (4) pourvu de deux côtés de liaison (5), et une pluralité de conduites tubulaires (6) s'étendant entre les côtés de liaison en tant que surface d'échange thermique. Le volume intérieur de tube des conduites tubulaires (6) est accessible par les côtés de liaison (5) de l'échangeur thermique (2, 3) et le boîtier (4) définit le volume extérieur de tube de l'échangeur thermique (2, 3). Un système d'échangeurs thermiques (1) optimisé en terme d'écoulement et thermique est réalisé du fait que le volume de tube extérieur du premier échangeur thermique (2) est relié au volume de tube intérieur du deuxième échangeur thermique (3) par fixation étanche d'un premier côté de liaison (5a) du deuxième échangeur thermique (3) au boîtier (4) du premier échangeur thermique (2).
PCT/EP2011/000669 2010-02-17 2011-02-14 Système d'échangeurs thermiques WO2011101112A1 (fr)

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Application Number Priority Date Filing Date Title
EP11708695A EP2536990A1 (fr) 2010-02-17 2011-02-14 Système d'échangeurs thermiques

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010008383 DE102010008383A1 (de) 2010-02-17 2010-02-17 Wärmeübertragersystem
DE102010008383.6 2010-02-17

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WO2011101112A1 true WO2011101112A1 (fr) 2011-08-25

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Publication number Priority date Publication date Assignee Title
ITUD20120060A1 (it) * 2012-04-13 2013-10-14 Ohg Ind S R L Con Unico Scambiatore di calore

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1814010A (en) * 1925-02-27 1931-07-14 Diamond Power Speciality Air heater
GB671375A (en) * 1949-03-10 1952-05-07 Parsons C A & Co Ltd Improvements in or relating to contra-flow heat exchangers
US2735660A (en) * 1956-02-21 Craig
FR1285548A (fr) * 1961-03-13 1962-02-23 Escher Wyss Sa Soc Réfrigérant préalable ou intermédiaire pour installation de turbine à gaz
GB2032611A (en) * 1978-10-05 1980-05-08 Fiat Ricerche Heat exchanger
DE10048016C1 (de) * 2000-09-26 2002-05-16 Siegenia Frank Kg Gegenstrom-Wärmetauscher

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Publication number Priority date Publication date Assignee Title
DE3840460A1 (de) * 1988-12-01 1990-06-07 Mtu Muenchen Gmbh Waermetauscher
DE4019991A1 (de) * 1990-06-22 1992-01-02 Dvt Buero Fuer Anwendung Deuts Kolonnenkoerper zur aufnahme von plattenwaermetauschern
ATE188395T1 (de) * 1995-04-24 2000-01-15 Krebs & Co Ag Vorrichtung zur trennung von fluiden
US7758754B2 (en) * 2007-01-09 2010-07-20 Membrane Technology And Research, Inc Pervaporation process and assembly

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2735660A (en) * 1956-02-21 Craig
US1814010A (en) * 1925-02-27 1931-07-14 Diamond Power Speciality Air heater
GB671375A (en) * 1949-03-10 1952-05-07 Parsons C A & Co Ltd Improvements in or relating to contra-flow heat exchangers
FR1285548A (fr) * 1961-03-13 1962-02-23 Escher Wyss Sa Soc Réfrigérant préalable ou intermédiaire pour installation de turbine à gaz
GB2032611A (en) * 1978-10-05 1980-05-08 Fiat Ricerche Heat exchanger
DE10048016C1 (de) * 2000-09-26 2002-05-16 Siegenia Frank Kg Gegenstrom-Wärmetauscher

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EP2536990A1 (fr) 2012-12-26

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