EP3143352B1 - Heat exchanger with channels for damping movements of liquids - Google Patents

Heat exchanger with channels for damping movements of liquids Download PDF

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Publication number
EP3143352B1
EP3143352B1 EP15720913.1A EP15720913A EP3143352B1 EP 3143352 B1 EP3143352 B1 EP 3143352B1 EP 15720913 A EP15720913 A EP 15720913A EP 3143352 B1 EP3143352 B1 EP 3143352B1
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EP
European Patent Office
Prior art keywords
heat exchanger
channels
medium
shell
exchanger according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15720913.1A
Other languages
German (de)
French (fr)
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EP3143352A1 (en
Inventor
Manfred Steinbauer
Christiane Kerber
Axel Lehmacher
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Linde GmbH
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Linde GmbH
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    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0017—Flooded core heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0262—Details of the cold heat exchange system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0275—Construction and layout of liquefaction equipments, e.g. valves, machines adapted for special use of the liquefaction unit, e.g. portable or transportable devices
    • F25J1/0277—Offshore use, e.g. during shipping
    • F25J1/0278—Unit being stationary, e.g. on floating barge or fixed platform
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/20—Boiler-condenser with multiple exchanger cores in parallel or with multiple re-boiling or condensing streams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/72—Processing device is used off-shore, e.g. on a platform or floating on a ship or barge
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction

Definitions

  • the invention relates to a heat exchanger for indirect heat transfer between a first medium and a second medium according to the horr1.
  • a heat exchanger usually has a jacket (also called “shell”), which defines a jacket space for receiving a liquid phase of the first medium, and at least one heat exchanger block (also referred to as “core” or “block”), the first Heat transfer passages for receiving the first medium and second heat transfer passages for receiving the second medium, so that between the two media indirectly heat transferable, wherein the heat transfer block is arranged in the jacket space, that it is umvorbar with a located in the shell space liquid phase of the first medium ,
  • ALPEMA brazed aluminum plate-fin heat exchanger manufacturer's association
  • Such a design of a heat exchanger is also called “core-in-shell” or “block-in-shell” heat exchanger.
  • US-A-2013153179 discloses a heat exchanger according to the preamble of claim 1.
  • the driving force for the flow through the at least one heat exchanger block with the first medium is preferably generated by the thermosiphon effect due to the evaporation itself.
  • the jacket space of the heat exchanger not only fulfills the purpose of an original container, but also serves as a separating apparatus for separating the generated vapor of the first medium from the refrigerant liquid and the liquid phase of the first medium, respectively.
  • a free surface of the liquid phase of the first medium forms in the shell space.
  • the jacket of the heat exchanger which is preferably cylindrical in shape, can be oriented both horizontally and vertically as far as the orientation of the longitudinal or cylindrical axis is concerned.
  • the heat exchanger block is flowed through mainly by the refrigerant liquid mainly upwards.
  • the flow direction of the stream to be cooled (second medium) is not restricted in particular.
  • the heat exchanger on a mobile surface e.g. Therefore, the well-known problems associated with partially liquid-filled containers may arise, in particular, the liquid may reciprocate in the container space so that e.g. At several locations in the mantle space, time-varying levels result. As a result, e.g. the immersion depth of the heat exchanger blocks into the liquid phase of the first medium, which is e.g. may affect the effectiveness of heat transfer. If possible, therefore, the liquid movement of the bath is to be damped so far that a safe and reliable operation can be guaranteed.
  • the present invention seeks to provide a heat exchanger of the type mentioned, which reduces the above problem.
  • a plurality of parallel cylindrical channels for guiding the first medium is provided in the lateral space laterally to the at least one heat exchanger block, which in particular are in flow connection only with the bath or the liquid phase.
  • Cylindrical here means in the general sense that the base of the cylinder, which in the present case is the cross-sectional area of the channel can be any flat surface, which may be circular (circular cylinder), rectangular, square, triangular or hexagonal in particular.
  • the respective cylinder is formed by displacement of that flat surface along a straight line or longitudinal axis, which does not lie in the plane of the flat surface and preferably runs normal to that flat surface or cross-sectional surface.
  • the individual channels are furthermore preferred over their circumference by walls, and preferably in the form of circumferential walls, in particular completely closed walls, separated from each other. In such completely closed walls, the medium flowing in the respective channel along the longitudinal axis of the channel can not enter an adjacent channel (transverse to the longitudinal axis).
  • a channel, some channels or all channels have a separate, own circumferential wall.
  • a wall of a channel also forms part of a wall of an adjacent channel. This can also apply to several or all channels.
  • the liquid phase of the first medium in the jacket space of the heat exchanger can advantageously be calmed in fluctuating movements of the heat exchanger.
  • a fluctuating movement is understood in particular to mean a movement in which the longitudinal or cylindrical axis of the jacket alters its spatial position or inclination, in particular periodically (for example due to the sea in an arrangement of the heat exchanger on a float on a body of water).
  • the channels - are the channels - based on a designated heat exchanger, which is assumed in the following - e.g. Aligned along the vertical, the liquid phase during operation of the heat exchanger at the upper end of the heat exchanger block exit and flow through the channels laterally back to the heat exchanger block.
  • the channels thereby represent a flow resistance in the horizontal direction, which suppresses a movement of the liquid phase of the first medium along the horizontal.
  • the liquid phase may flow back and forth in the channels during fluctuating movements of the heat exchanger, the channels also acting as flow resistors in the horizontal direction due to the limited flow cross section and therefore damping a corresponding movement of the liquid phase of the first medium , If the longitudinal axes of the parallel channels are aligned horizontally, in particular a liquid movement is damped, which results from a fluctuating movement in which the inclination of the longitudinal axes changes.
  • the at least one heat exchanger block can be any possible heat exchanger, which in particular can transfer heat indirectly from the second medium to the first medium.
  • the heat exchanger block is a plate heat exchanger.
  • Such plate heat exchangers generally have a plurality of mutually parallel plates or plates, which form a plurality of heat transfer passages for participating in the heat transfer media.
  • a preferred embodiment of a plate heat exchanger has a plurality of heat conducting structures, e.g. in the form of average meandering, in particular corrugated or folded sheets (so-called fins), which are each arranged between two parallel partition plates or sheets of Platten Vietnamese pyramidtragers, wherein the two outermost layers of the Platten Vietnamese Bulgariaschreibers are formed by cover plates.
  • a plurality of parallel channels or a heat transfer passage are formed between each two partition plates or between a partition plate and a cover plate due to the respective interposed fin, through which a medium can flow.
  • Heat transfer may therefore take place between the media flowing in adjacent heat transfer passages, the heat transfer passages associated with the first medium being referred to as first heat transfer passages and the heat transfer passages associated with the second medium correspondingly being referred to as second heat transfer passages.
  • first heat transfer passages are open along the vertical upwards and downwards and in particular not closed by end strips, so that the liquid phase of the first medium from below can get into the first heat transfer passages and top of the plate heat exchanger from the first heat transfer passages as liquid and / or gaseous Phase can escape.
  • cover plates, separator plates, fins and side bars are preferably made of aluminum and are used e.g. soldered together in an oven. Via corresponding headers with nozzles media such as e.g. the second medium are introduced into or removed from the associated heat transfer passages.
  • the jacket of the heat exchanger can in particular have a circumferential, (circular) cylindrical wall, which is preferably aligned with a heat exchanger arranged as intended, so that the longitudinal axis or cylinder axis of the wall or the jacket extends along the horizontal or along the vertical.
  • the jacket preferably has mutually opposite walls connected to that wall, which extend transversely to the longitudinal axis or cylinder axis.
  • the at least one plate heat exchanger is designed to cool the second medium guided in the second heat transfer passages against the first medium guided in the adjacent first heat transfer passages and / or at least partially to liquefy, so that forms a gaseous phase of the first medium, wherein the jacket space is formed for collecting the gaseous phase.
  • the at least one plate heat exchanger is formed so that the first medium rises during operation of the heat exchanger in the at least one plate heat exchanger, namely in designated first heat transfer passages of at least one plate heat exchanger, in particular the at least one plate heat exchanger is designed to the second medium in the second heat transfer passages in countercurrent or cross-flow to the first medium to lead.
  • the liquid phase of the first medium emerging at the upper end of the plate heat exchanger together with the gaseous phase flows down again on the sides of the plate heat exchanger, possibly in the vertically oriented channels.
  • the channels or their walls are fixed to each other so that they form a coherent unit, which is also referred to as a register.
  • These Unit is preferably formed separately from the heat exchanger block and / or jacket.
  • the channels or at least some of the channels along their respective longitudinal axis are formed longitudinally, ie, the extent along the respective longitudinal axis is greater than the largest inner diameter of the respective channel perpendicular to the respective longitudinal axis.
  • the channels are thus flowed through along their respective longitudinal or cylindrical axis of the liquid phase of the first medium, wherein they each have an opening at the two end faces, via which the liquid phase in the respective channel can enter or exit.
  • the two openings of a channel lie opposite each other along the longitudinal or cylindrical axis of the respective channel, that is, they are aligned with one another.
  • all channels - with respect to the longitudinal axes - have the same length.
  • some or all channels for adapting the unit to a curved portion of an inner side of the shell of the heat exchanger - with respect to the longitudinal axes - have different lengths. This makes it possible to achieve a gradation of an outer side of the assembled unit following the course of the inner side region (e.g., a hollow cylindrical shell).
  • the unit arranged in the jacket space on the jacket so that it does not contact the at least one heat exchanger block in particular.
  • the unit may also be fixed to the at least one heat exchanger block or to a separate carrier.
  • the respective channel is formed by a hollow profile.
  • the hollow profile which is preferably made of a metal (such as aluminum or steel), thereby forms a wall surrounding the respective channel and limits or thereby forms the respective channel.
  • the hollow profiles are connected to each other so that that coherent unit is formed.
  • the hollow sections can be welded together or be suitably fixed to each other by other fastening means, so that that unit or the hollow profile register is formed.
  • the channels are formed by a plurality of interconnected plate-shaped elements (e.g., sheets). These elements may be flat (e.g., planar sheets) or may have a structure (e.g., those elements may be formed as cross-section corrugated or folded or serrated elements / sheets).
  • the individual elements may e.g. be fixed by nesting each other and may optionally be additionally fixed to each other.
  • fixing or fixing e.g. Soldering and / or welded joints, rivet joints or other non-positive, positive and / or cohesive connections conceivable.
  • the longitudinal axes of the channels extend again parallel to the vertical, again in relation to a heat exchanger arranged as intended.
  • the longitudinal axes of the channels can extend in a lying jacket perpendicular to the longitudinal or cylindrical axis of the shell.
  • the longitudinal axes of the vertical channels preferably run parallel to the longitudinal or cylindrical axis of the jacket.
  • the longitudinal axes of the channels - again in relation to a heat exchanger arranged as intended - run parallel to the horizontal.
  • the longitudinal axes of the channels can extend parallel to the longitudinal or cylindrical axis of the jacket in a lying jacket.
  • the longitudinal axes of the horizontal channels preferably extend perpendicular to the longitudinal or cylindrical axis of the jacket.
  • At horizontally extending channels at least some of the channels have a flow brake or are closed in order to make targeted the action on the liquid phase.
  • the unit or possibly the channels along the vertical has or have a length which is at least greater than half the height of the at least one plate heat exchanger or heat exchanger block along the vertical greater than or equal to the height of the at least one plate heat exchanger or heat exchanger block along the vertical.
  • the unit composed of a plurality of channels or hollow profiles is arranged between the at least one heat exchanger block and the jacket or a section or inner side region of the jacket lying horizontally opposite the block.
  • the unit may also be arranged between two such blocks.
  • a plurality of units each having a plurality of channels can be provided both in a heat exchanger block and in a plurality of heat exchanger blocks, wherein the respective unit is then preferably arranged between one of the heat exchanger blocks and the jacket (see above) or between two adjacent heat exchanger blocks.
  • the respective unit can be designed as described above.
  • the further heat exchanger blocks are in turn preferably designed as a plate heat exchanger, in particular in the form described above.
  • FIG. 1 shows in connection with FIG. 2 a heat exchanger 1, which has a standing, preferably (circular) cylindrical jacket 2, which delimits a jacket space 3 of the heat exchanger 1.
  • the jacket 2 in this case has a circumferential, cylindrical wall 14, which is delimited by two opposing walls 15 frontally.
  • the longitudinal or cylindrical axis of the shell 2 coincides with the vertical z.
  • two heat exchanger blocks 4, 5 are arranged horizontally next to one another, which are plate heat exchangers 4, 5 which have a plurality of parallel heat transfer passages P, P '(cf. FIG. 7 ).
  • the respective plate heat exchanger 4, 5 in this case has a plurality of réelleleit Weg 41, which may be sheets that are formed in a meandering cross section, so for example wavy, jagged or rectangular course. These structures 41 are also referred to as fins 41 and are each arranged between two flat separating plates or plates 40 of the plate heat exchanger 4, 5. In this way, between each two partition plates 40 (or a partition plate and a cover plate, see below) a plurality of parallel channels or a heat transfer passage P, P 'is formed, through which the respective medium M1, M2 can flow.
  • the two outermost layers 40 are formed by cover plates of the plate heat exchanger 4, 5; towards the sides 40 end strips 42 are provided between each two adjacent partition plates or separation and cover plates.
  • FIG. 7 1 shows, by way of example, a first heat transfer passage P for the first medium M1, which is formed by a fin 41 and two adjacent separating plates 40 and an adjacent second heat transfer passage P 'for the second medium M2, which is likewise formed by a fin 41 and two adjacent separating plates 40 becomes.
  • Such an arrangement of passages is preferably repeated in the respective plate heat exchanger 4, 5, so that a plurality of first and second heat transfer passages P, P 'are arranged alternately side by side.
  • the jacket space 3 is filled with a first medium M1 during operation of the heat exchanger 1.
  • This inlet flow into the heat exchanger 1 is usually two-phase, but may also be liquid.
  • the liquid phase F1 of the first medium M1 then forms a bath surrounding the plate heat exchangers 4, 5, the gaseous phase G1 of the first medium M1 accumulating above the liquid phase F1 in an upper region of the jacket space 3 and being removable therefrom.
  • the liquid phase F1 of the first medium M1 rises in the first heat transfer passages P of the plate heat exchangers 4, 5 and thereby becomes through the second medium M2 to be cooled, which is guided eg in crossflow to the first medium M1 in the second heat transfer passages P 'of the plate heat exchangers 4, 5, partially evaporated by indirect heat transfer.
  • the resulting gaseous phase G1 of the first medium M1 can escape at an upper end of the plate heat exchangers 4, 5 and is withdrawn from the jacket space 3 above the blocks 4, 5.
  • a part of the liquid phase F1 circulates in the shell space 3, wherein that part in the plate heat exchangers 4, 5 in the first heat transfer passages P is conveyed from bottom to top and then flows outside the plate heat exchanger 4,5 in the shell space 3 back down.
  • the second medium M2 is passed into the plate heat exchanger 4, 5 and after passing through the associated second heat transfer passages P 'cooled or liquefied withdrawn from the plate heat exchanger 4, 5.
  • FIG. 1 In order to calm the liquid phase F1 in the mantle space 3 in the event of a fluctuating movement of the shell 2, in which the longitudinal or cylinder axis fluctuates about the vertical z, are in accordance with FIG. 1 three units 100 are provided, each with a plurality of parallel channels 10, each extending along a longitudinal axis L which is parallel to the longitudinal axis z of the shell 2. These channels 10 are preferred according to FIG.
  • the channels 10 are preferably arranged next to each other along second orthogonal spatial directions.
  • the vertical channels 10 represent a flow resistance in the horizontal direction and therefore suppress corresponding horizontal movements of the liquid phase F1 of the first medium M1, while those vertical circulation is protected by the channels 10.
  • one of the units 100 is arranged between the two plate heat exchangers 4, 5 laterally to the two blocks 4, 5.
  • the other two units 100 are each arranged between a plate heat exchanger 4, 5 and a horizontally adjacent section or inner side region 2 a of the peripheral wall 14 of the shell 2.
  • FIG. 3 shows a modification of the heat exchanger 1 according to FIG. 1 that in difference to FIG. 1 a lying, longitudinally extending jacket 2, which extends along a longitudinal or cylindrical axis which coincides with the horizontal, that is perpendicular to the vertical z.
  • two plate heat exchangers 4, 5 in contrast to FIG. 1 along the longitudinal axis of the shell 2, the two blocks 4, 5 being laterally flanked on both sides by a unit 100 formed as described above, the units 100 covering the two blocks 4, 5 over the whole, Flank combined length of the two blocks 4, 5 along the longitudinal axis of the shell 2.
  • FIG. 4 shows a further modification of the heat exchanger 1 according to FIG. 1 , in which now the channels 10 in contrast to FIG. 1 run horizontally, ie perpendicular to the longitudinal axis of the stationary shell 2, which coincides with the vertical z.
  • the openings 10a, 10b of the channels 10 now each have a horizontal direction.
  • the units 100 are according to FIG. 1 with respect to the plate heat exchangers 4, 5, wherein the unit 100 between the two blocks 4, 5 channels 10 having a larger flow cross-sectional area than the units 100 on the outsides of the blocks 4, 5.
  • All units 100 are along the vertical z on the upper and lower ends of the plate heat exchangers 4, 5, so as to calm as possible the entire level of the liquid phase F1 of the first medium M1 in a fluctuating movement of the heat exchanger 1, wherein the longitudinal axis z of the shell 2 according to FIG. 4 their inclination changed, in particular from the leaf level out.
  • the reassurance is generated by the flow resistance, the liquid phase F1 in the horizontal channels, for example when flowing back and forth between the openings 10a, 10b of the channels 10 experiences.
  • the channels 10 or units 100 according to FIG. 4 can be formed with a plurality of rectangular cross-section or square hollow profiles or by nested or attached to each other flat, plate-shaped elements, in particular sheets (see above). According to FIG.
  • the vertical channels 10 may not only be rectangular in cross-section, as exemplified in FIG Fig. 4 shown, but also circular. Other shapes are also conceivable.
  • individual horizontal channels 10 may be equipped with an additional flow brake (eg a cross-sectional constriction) 12 or be completely closed 12.
  • FIG. 6 finally shows a heat exchanger 1 by type FIG. 4 with horizontal channels 10, wherein now the jacket 2 of the heat transfer according to FIG. 3 is formed and arranged horizontally.
  • another unit 100 between the two blocks 4, 5 is arranged.
  • the reassurance of the liquid phase F1 of the first medium works as based on the FIG. 4 described.
  • the interconnected (or individual) hollow sections 11 and channels 10 in different cross-sectional shapes (eg circular, rectangular, honeycomb) and length at any position of not occupied by the respective plate heat exchanger 4, 5 shell space 3, but mainly in the liquid-filled area (So next to the block 4 or 5, the blocks 4, 5 and / or between the blocks 4, 5) be attached.
  • Register 100 is customizable. These units 100 are flowed through only in the vertical direction or in the horizontal direction of the liquid phase F1.
  • the composite itself represents a flow resistance in the horizontal direction. This dampens horizontal flows.
  • the units 100 or channels 10 can be adapted to the respective requirements both in vertical and in the horizontal dimensions and can also be subdivided if necessary.
  • the size of the individual channels 10 in cross section is flexible and can also be adapted to the respective requirements.
  • the individual channels 10 of the units 100 may have different lengths. Especially with horizontal channels 10 or hollow sections 11, individual profiles 11 may be closed in order to adapt the flow resistance. This dampens horizontal currents.
  • the units or hollow profile register 100 allow a great influence on the flow direction of the circulating liquid F1 in the container 2, without requiring a high number of individual parts.
  • the volume of liquid outside the plate heat exchangers 4, 5 can be very highly segmented, although the manufacturing and assembly costs for it remains relatively low.
  • the segmentation further allows low wall thicknesses of the units 100 or channels 10 / hollow sections 11, since the composite 100 represents a robust body 100 and only allows small-scale fluid movements.
  • the natural frequencies of oscillating liquid F1 in the container 2 or jacket space 3 can be influenced and movements dampened. Thus, a stimulation in natural frequency and high vibration amplitudes can be prevented.
  • the heat exchanger 1 according to the invention is used on a float on a body of water, for example as a component of a floating plant for the production of liquid natural gas (LNG).
  • LNG liquid natural gas

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Description

Die Erfindung betrifft einen Wärmeübertrager zur indirekten Wärmeübertragung zwischen einem ersten Medium und einem zweiten Medium gemäß dem Anspruch1. Ein solcher Wärmeübertrager weist in der Regel einen Mantel (auch "shell" genannt) auf, der einen Mantelraum zur Aufnahme einer flüssigen Phase des ersten Mediums definiert, sowie zumindest einen Wärmeübertragerblock (auch als "core" oder "block" bezeichnet), der erste Wärmeübertragungspassagen zur Aufnahme des ersten Mediums sowie zweite Wärmeübertragungspassagen zur Aufnahme des zweiten Mediums aufweist, so dass zwischen den beiden Medien indirekt Wärme übertragbar ist, wobei der Wärmeübertragerblock so im Mantelraum angeordnet ist, dass er mit einer im Mantelraum befindlichen flüssigen Phase des ersten Mediums umgebbar ist. Ein derartiger Wärmeübertrager ist beispielsweise in "The standards of the brazed aluminium plate-fin heat exchanger manufacturer's association (ALPEMA)", dritte Ausgabe, 2010, Seite 67 in Figur 9-1 gezeigt. Eine solche Ausführung eines Wärmeübertragers nennt man auch "core-in-shell"- oder "block-in-shell"-Wärmeübertrager.The invention relates to a heat exchanger for indirect heat transfer between a first medium and a second medium according to the Anspruch1. Such a heat exchanger usually has a jacket (also called "shell"), which defines a jacket space for receiving a liquid phase of the first medium, and at least one heat exchanger block (also referred to as "core" or "block"), the first Heat transfer passages for receiving the first medium and second heat transfer passages for receiving the second medium, so that between the two media indirectly heat transferable, wherein the heat transfer block is arranged in the jacket space, that it is umvorbar with a located in the shell space liquid phase of the first medium , Such a heat exchanger is described, for example, in "The standards of the brazed aluminum plate-fin heat exchanger manufacturer's association (ALPEMA)", third edition, 2010, page 67 in Figure 9-1 shown. Such a design of a heat exchanger is also called "core-in-shell" or "block-in-shell" heat exchanger.

US-A-2013153179 offenbart einen Wärmeübertrager gemäß dem Oberbegriff des Anspruchs 1. Die treibende Kraft für die Durchströmung des mindestens einen Wärmeübertragerblocks mit dem ersten Medium (z.B. Kältemittel) wird bevorzugt durch den Thermosiphon-Effekt aufgrund der Verdampfung selbst erzeugt. Der Mantelraum des Wärmeübertragers erfüllt jedoch nicht nur den Zweck eines Vorlagebehälters, sondern er dient auch als Trennapparat zur Trennung des erzeugten Dampfes des ersten Mediums von der Kältemittelflüssigkeit bzw. der flüssigen Phase des ersten Mediums. Systembedingt bildet sich also eine freie Oberfläche der flüssigen Phase des ersten Mediums im Mantelraum aus. Der Mantel des Wärmeübertragers, der vorzugsweise zylinderförmig ausgebildet ist, kann dabei, was die Orientierung der Längs- bzw. Zylinderachse anbelangt, sowohl horizontal als auch vertikal ausgerichtet sein. Der Wärmeübertragerblock wird von der Kältemittelflüssigkeit grundsätzlich hauptsächlich aufwärts durchströmt. Die Durchströmungsrichtung des abzukühlenden Stroms (zweites Medium) ist insbesondere nicht eingeschränkt. US-A-2013153179 discloses a heat exchanger according to the preamble of claim 1. The driving force for the flow through the at least one heat exchanger block with the first medium (eg refrigerant) is preferably generated by the thermosiphon effect due to the evaporation itself. However, the jacket space of the heat exchanger not only fulfills the purpose of an original container, but also serves as a separating apparatus for separating the generated vapor of the first medium from the refrigerant liquid and the liquid phase of the first medium, respectively. As a result of the system, a free surface of the liquid phase of the first medium forms in the shell space. The jacket of the heat exchanger, which is preferably cylindrical in shape, can be oriented both horizontally and vertically as far as the orientation of the longitudinal or cylindrical axis is concerned. The heat exchanger block is flowed through mainly by the refrigerant liquid mainly upwards. The flow direction of the stream to be cooled (second medium) is not restricted in particular.

Soll der Wärmeübertrager auf einem beweglichen Untergrund, z.B. einem Schwimmkörper (z.B. Schiff) aufgestellt werden, können sich daher die allgemein bekannten Probleme ergeben, die bei teilweise mit einer Flüssigkeit gefüllten Behältern auftreten, insbesondere kann sich die Flüssigkeit im Behälter bzw. Mantelraum hin-und her bewegen, so dass sich z.B. an mehreren Ort im Mantelraum zeitlich variierende Pegel ergeben. Hierdurch variiert z.B. die Eintauchtiefe der Wärmeübertragerblöcke in die flüssige Phase des ersten Mediums, was z.B. die Effektivität der Wärmeübertragung beinträchtigen kann. Nach Möglichkeit ist daher die Flüssigkeitsbewegung des Bades soweit zu dämpfen, dass ein sicherer und verlässlicher Betrieb gewährleistet werden kann.If the heat exchanger on a mobile surface, e.g. Therefore, the well-known problems associated with partially liquid-filled containers may arise, in particular, the liquid may reciprocate in the container space so that e.g. At several locations in the mantle space, time-varying levels result. As a result, e.g. the immersion depth of the heat exchanger blocks into the liquid phase of the first medium, which is e.g. may affect the effectiveness of heat transfer. If possible, therefore, the liquid movement of the bath is to be damped so far that a safe and reliable operation can be guaranteed.

Hiervon ausgehend liegt daher der vorliegenden Erfindung die Aufgabe zugrunde, einen Wärmeübertrager der eingangs genannten Art bereitzustellen, der die vorgenannte Problematik mindert.Proceeding from this, therefore, the present invention seeks to provide a heat exchanger of the type mentioned, which reduces the above problem.

Dieses Problem wird durch einen Wärmeübertrager mit den Merkmalen des Anspruchs 1 gelöst.This problem is solved by a heat exchanger with the features of claim 1.

Danach ist vorgesehen, dass im Mantelraum lateral zu dem mindestens einen Wärmeübertragerblock eine Mehrzahl an parallel zueinander verlaufenden zylindrischen Kanälen zum Führen des ersten Mediums vorgesehen ist, die insbesondere lediglich mit dem Bad bzw. der flüssigen Phase in Strömungsverbindung stehen bzw. von dieser durchströmbar sind.Thereafter, it is provided that a plurality of parallel cylindrical channels for guiding the first medium is provided in the lateral space laterally to the at least one heat exchanger block, which in particular are in flow connection only with the bath or the liquid phase.

Zylindrisch bedeutet hierbei im allgemeinen Sinne, dass die Grundfläche des Zylinders, die vorliegend die Querschnittsfläche des Kanals ist, eine beliebige ebene Fläche sein kann, die insbesondere kreisförmig (Kreiszylinder), rechteckförmig, quadratisch, dreieckig oder sechseckig ausgebildet sein kann. Der jeweilige Zylinder entsteht dabei durch Verschiebung jener ebenen Fläche entlang einer Geraden bzw. Längsachse, die nicht in der Ebene der ebenen Fläche liegt und vorzugsweise normal zu jener ebenen Fläche bzw. Querschnittsfläche verläuft.Cylindrical here means in the general sense that the base of the cylinder, which in the present case is the cross-sectional area of the channel can be any flat surface, which may be circular (circular cylinder), rectangular, square, triangular or hexagonal in particular. The respective cylinder is formed by displacement of that flat surface along a straight line or longitudinal axis, which does not lie in the plane of the flat surface and preferably runs normal to that flat surface or cross-sectional surface.

Die einzelnen Kanäle sind weiterhin bevorzugt über ihren Umfang durch Wandungen, und zwar vorzugsweise in Form von umlaufenden Wandungen, insbesondere vollständig geschlossenen Wandungen, voneinander getrennt. Bei derartigen vollständig geschlossenen Wandungen kann das Medium, dass in dem jeweiligen Kanal entlang der Längsachse des Kanals strömt, nicht (quer zur Längsachse) in einen benachbarten Kanal eintreten.The individual channels are furthermore preferred over their circumference by walls, and preferably in the form of circumferential walls, in particular completely closed walls, separated from each other. In such completely closed walls, the medium flowing in the respective channel along the longitudinal axis of the channel can not enter an adjacent channel (transverse to the longitudinal axis).

Es ist möglich, dass ein Kanal, einige Kanäle oder alle Kanäle eine separate, eigene umlaufende Wandung aufweisen. Es besteht auch die Möglichkeit, dass eine Wandung eines Kanals auch einen Teil einer Wandung eines benachbarten Kanals bildet. Dies kann auch für mehrere bzw. alle Kanäle gelten.It is possible that a channel, some channels or all channels have a separate, own circumferential wall. There is also the possibility that a wall of a channel also forms part of a wall of an adjacent channel. This can also apply to several or all channels.

Aufgrund der erfindungsgemäßen Lösung kann mit Vorteil die flüssige Phase des ersten Mediums im Mantelraum des Wärmeübertragers bei schwankenden Bewegungen des Wärmeübertragers beruhigt werden. Unter einer schwankenden Bewegung wird dabei insbesondere eine Bewegung verstanden, bei der die Längs- oder Zylinderachse des Mantels ihre Raumlage bzw. Neigung verändert, insbesondere periodisch (z.B. aufgrund des Seegangs bei einer Anordnung des Wärmeübertragers auf einem Schwimmkörper auf einem Gewässer).Because of the solution according to the invention, the liquid phase of the first medium in the jacket space of the heat exchanger can advantageously be calmed in fluctuating movements of the heat exchanger. In this context, a fluctuating movement is understood in particular to mean a movement in which the longitudinal or cylindrical axis of the jacket alters its spatial position or inclination, in particular periodically (for example due to the sea in an arrangement of the heat exchanger on a float on a body of water).

Sind die Kanäle - bezogen auf einen bestimmungsgemäß angeordneten Wärmeübertrager, der im Folgenden vorausgesetzt wird - z.B. entlang der Vertikalen ausgerichtet, kann die flüssige Phase beim Betrieb des Wärmeübertragers am oberen Ende des Wärmeübertragerblocks austreten und durch die Kanäle lateral zum Wärmeübertragerblock wieder nach unten strömen. Die Kanäle stellen dabei einen Strömungswiderstand in horizontaler Richtung dar, der eine Bewegung der flüssigen Phase des ersten Mediums entlang der Horizontalen unterdrückt.Are the channels - based on a designated heat exchanger, which is assumed in the following - e.g. Aligned along the vertical, the liquid phase during operation of the heat exchanger at the upper end of the heat exchanger block exit and flow through the channels laterally back to the heat exchanger block. The channels thereby represent a flow resistance in the horizontal direction, which suppresses a movement of the liquid phase of the first medium along the horizontal.

Bei horizontal orientierten Kanälen kann die flüssige Phase in den Kanälen bei schwankenden Bewegungen des Wärmeübertragers ggf. hin- und her strömen, wobei die Kanäle aufgrund des limitierten Strömungsquerschnitts ebenfalls als Strömungswiderstände in horizontaler Richtung wirken und daher eine entsprechende Bewegung der flüssigen Phase des ersten Mediums dämpfen. Sind die Längsachsen der parallelen Kanäle horizontal ausgerichtet, wird vor allem eine Flüssigkeitsbewegung gedämpft, die durch eine schwankende Bewegung resultiert, bei der sich die Neigung der Längsachsen ändert.In the case of horizontally oriented channels, the liquid phase may flow back and forth in the channels during fluctuating movements of the heat exchanger, the channels also acting as flow resistors in the horizontal direction due to the limited flow cross section and therefore damping a corresponding movement of the liquid phase of the first medium , If the longitudinal axes of the parallel channels are aligned horizontally, in particular a liquid movement is damped, which results from a fluctuating movement in which the inclination of the longitudinal axes changes.

Bei dem mindestens einen Wärmeübertragerblock kann es sich im Prinzip um alle möglichen Wärmeübertrager handeln, die insbesondere indirekt Wärme vom zweiten Medium auf das erste Medium übertragen können.In principle, the at least one heat exchanger block can be any possible heat exchanger, which in particular can transfer heat indirectly from the second medium to the first medium.

Bevorzugt handelt es sich bei dem Wärmeübertragerblock jedoch um einen Plattenwärmeübertrager. Derartige Plattenwärmeübertrager weisen in der Regel eine Mehrzahl an parallel zueinander angeordneten Platten bzw. Blechen auf, die eine Vielzahl von Wärmeübertragungspassagen für an der Wärmeübertragung beteiligte Medien bilden. Eine bevorzugte Ausführungsform eines Plattenwärmeübertragers weist eine Mehrzahl an Wärmeleitstrukturen, z.B. in Form von im Schnitt mäanderförmigen, insbesondere gewellten bzw. gefalteten Blechen auf (sogenannte Fins), die jeweils zwischen zwei parallelen Trennplatten bzw. -blechen des Plattenwärmeübertragers angeordnet sind, wobei die beiden äußersten Lagen des Plattenwärmeübertragers durch Deckplatten gebildet sind. Auf diese Weise werden zwischen je zwei Trennplatten bzw. zwischen einer Trennplatte und einer Deckplatte aufgrund des jeweils dazwischen angeordneten Fins eine Vielzahl an parallelen Kanälen bzw. eine Wärmeübertragungspassage gebildet, durch die ein Medium strömen kann. Zwischen den in benachbarten Wärmeübertragungspassagen strömenden Medien kann daher eine Wärmeübertragung stattfinden, wobei die dem ersten Medium zugeordneten Wärmeübertragungspassagen als erste Wärmeübertragungspassagen und die dem zweiten Medium zugeordneten Wärmeübertragungspassagen entsprechend als zweite Wärmeübertragungspassagen bezeichnet werden.Preferably, however, the heat exchanger block is a plate heat exchanger. Such plate heat exchangers generally have a plurality of mutually parallel plates or plates, which form a plurality of heat transfer passages for participating in the heat transfer media. A preferred embodiment of a plate heat exchanger has a plurality of heat conducting structures, e.g. in the form of average meandering, in particular corrugated or folded sheets (so-called fins), which are each arranged between two parallel partition plates or sheets of Plattenwärmeübertragers, wherein the two outermost layers of the Plattenwärmeübertragers are formed by cover plates. In this way, a plurality of parallel channels or a heat transfer passage are formed between each two partition plates or between a partition plate and a cover plate due to the respective interposed fin, through which a medium can flow. Heat transfer may therefore take place between the media flowing in adjacent heat transfer passages, the heat transfer passages associated with the first medium being referred to as first heat transfer passages and the heat transfer passages associated with the second medium correspondingly being referred to as second heat transfer passages.

Zu den Seiten hin sind zwischen je zwei benachbarten Trennplatten bzw. zwischen einer Deckplatte und der benachbarten Trennplatte vorzugsweise Abschlussleisten (so genannte Side Bars) zum Verschließen der jeweiligen Wärmeübertragungspassage vorgesehen. Die ersten Wärmeübertragungspassagen sind entlang der Vertikalen nach oben und unten hin offen und insbesondere nicht durch Abschlussleisten verschlossen, so dass die flüssige Phase des ersten Mediums von unten in die ersten Wärmeübertragungspassagen gelangen kann und oben am Plattenwärmeübertrager aus den ersten Wärmeübertragungspassagen als flüssige und/oder gasförmige Phase austreten kann.To the sides are provided between each two adjacent partition plates or between a cover plate and the adjacent partition plate preferably end strips (so-called side bars) for closing the respective heat transfer passage. The first heat transfer passages are open along the vertical upwards and downwards and in particular not closed by end strips, so that the liquid phase of the first medium from below can get into the first heat transfer passages and top of the plate heat exchanger from the first heat transfer passages as liquid and / or gaseous Phase can escape.

Die Deckplatten, Trennplatten, Fins und Side Bars sind vorzugsweise aus Aluminium gefertigt und werden z.B. in einem Ofen miteinander verlötet. Über entsprechende Header mit Stutzen können Medien, wie z.B. das zweite Medium, in die zugeordneten Wärmeübertragungspassagen eingeleitet bzw. aus diesen abgezogen werden.The cover plates, separator plates, fins and side bars are preferably made of aluminum and are used e.g. soldered together in an oven. Via corresponding headers with nozzles media such as e.g. the second medium are introduced into or removed from the associated heat transfer passages.

Der Mantel des Wärmeübertragers kann insbesondere eine umlaufende, (kreis)zylindrische Wandung aufweisen, die bei einem bestimmungsgemäß angeordneten Wärmeübertrager vorzugsweise so ausgerichtet ist, dass sich die Längsachse oder Zylinderachse der Wandung bzw. des Mantels entlang der Horizontalen oder entlang der Vertikalen erstreckt. Stirnseitig weist der Mantel bevorzugt einander gegenüberliegende, mit jener Wandung verbundene Wände auf, die sich quer zur Längsachse bzw. Zylinderachse erstrecken.The jacket of the heat exchanger can in particular have a circumferential, (circular) cylindrical wall, which is preferably aligned with a heat exchanger arranged as intended, so that the longitudinal axis or cylinder axis of the wall or the jacket extends along the horizontal or along the vertical. At the front, the jacket preferably has mutually opposite walls connected to that wall, which extend transversely to the longitudinal axis or cylinder axis.

Im Hinblick auf die Betriebsweise des Wärmeübertragers ist, wie eingangs bereits dargelegt, bevorzugt vorgesehen, dass der mindestens eine Plattenwärmeübertrager dazu ausgebildet ist, das in den zweiten Wärmeübertragungspassagen geführte zweite Medium gegen das in den benachbarten ersten Wärmeübertragungspassagen geführte erste Mediums abzukühlen und/oder zumindest teilweise zu verflüssigen, so dass sich eine gasförmige Phase des ersten Mediums bildet, wobei der Mantelraum zum Sammeln der gasförmigen Phase ausgebildet ist.With regard to the mode of operation of the heat exchanger, as already explained, it is preferably provided that the at least one plate heat exchanger is designed to cool the second medium guided in the second heat transfer passages against the first medium guided in the adjacent first heat transfer passages and / or at least partially to liquefy, so that forms a gaseous phase of the first medium, wherein the jacket space is formed for collecting the gaseous phase.

Bevorzugt ist weiterhin vorgesehen, dass der mindestens eine Plattenwärmeübertrager so ausgebildet ist, dass das erste Medium beim Betrieb des Wärmeübertragers in dem mindestens einen Plattenwärmeübertrager aufsteigt, nämlich in dafür vorgesehenen ersten Wärmeübertragungspassagen des mindestens einen Plattenwärmeübertragers, wobei insbesondere der mindestens eine Plattenwärmeübertrager dazu ausgebildet ist, das zweite Medium in den zweiten Wärmeübertragungspassagen im Gegenstrom oder im Kreuzstrom zum ersten Medium zu führen. Die am oberen Ende des Plattenwärmeübertragers zusammen mit der gasförmigen Phase austretende flüssige Phase des ersten Mediums strömt an den Seiten des Plattenwärmeübertragers wieder nach unten, ggf. in den vertikal orientierten Kanälen.Preferably, it is further provided that the at least one plate heat exchanger is formed so that the first medium rises during operation of the heat exchanger in the at least one plate heat exchanger, namely in designated first heat transfer passages of at least one plate heat exchanger, in particular the at least one plate heat exchanger is designed to the second medium in the second heat transfer passages in countercurrent or cross-flow to the first medium to lead. The liquid phase of the first medium emerging at the upper end of the plate heat exchanger together with the gaseous phase flows down again on the sides of the plate heat exchanger, possibly in the vertically oriented channels.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, dass die Kanäle bzw. deren Wandungen so aneinander festgelegt sind, dass sie eine zusammenhängende Einheit bilden, die auch als Register bezeichnet wird. Diese Einheit ist vorzugsweise separat zum Wärmeübertragerblock und/oder Mantel ausgebildet.According to a preferred embodiment of the invention it is provided that the channels or their walls are fixed to each other so that they form a coherent unit, which is also referred to as a register. These Unit is preferably formed separately from the heat exchanger block and / or jacket.

Weiterhin ist gemäß einer bevorzugten Ausführungsform der Erfindung vorgesehen, dass die Kanäle oder zumindest einige der Kanäle entlang ihrer jeweiligen Längsachse (bzw. Zylinderachse) längs erstreckt ausgebildet sind, d.h., die Ausdehnung entlang der jeweiligen Längsachse ist größer als der größte Innendurchmesser des jeweiligen Kanals senkrecht zur jeweiligen Längsachse.Furthermore, it is provided according to a preferred embodiment of the invention that the channels or at least some of the channels along their respective longitudinal axis (or cylinder axis) are formed longitudinally, ie, the extent along the respective longitudinal axis is greater than the largest inner diameter of the respective channel perpendicular to the respective longitudinal axis.

Die Kanäle sind somit entlang ihrer jeweiligen Längs- bzw. Zylinderachse von der flüssigen Phase des ersten Mediums durchströmbar, wobei sie jeweils an den beiden Stirnseiten je eine Öffnung aufweisen, über die die flüssige Phase in den jeweiligen Kanal ein- oder austreten kann. Die beiden Öffnungen eines Kanals liegen dabei einander entlang der Längs- bzw. Zylinderachse des jeweiligen Kanals gegenüber, fluchten also miteinander.The channels are thus flowed through along their respective longitudinal or cylindrical axis of the liquid phase of the first medium, wherein they each have an opening at the two end faces, via which the liquid phase in the respective channel can enter or exit. The two openings of a channel lie opposite each other along the longitudinal or cylindrical axis of the respective channel, that is, they are aligned with one another.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, dass alle Kanäle - bezogen auf die Längsachsen - die gleiche Länge aufweisen. Alternativ hierzu ist gemäß einer bevorzugten Ausgestaltung der Erfindung vorgesehen, dass einige oder alle Kanäle zur Anpassung der Einheit an einen gekrümmten Bereich einer Innenseite des Mantels des Wärmeübertragers - bezogen auf die Längsachsen - unterschiedliche Längen aufweisen. Hierdurch lässt sich eine Abstufung einer Außenseite der zusammengesetzten Einheit erzielen, die dem Verlauf des Innenseitenbereichs folgt (z.B. bei einem hohlzylindrischen Mantel).According to a preferred embodiment of the invention, it is provided that all channels - with respect to the longitudinal axes - have the same length. Alternatively, it is provided according to a preferred embodiment of the invention that some or all channels for adapting the unit to a curved portion of an inner side of the shell of the heat exchanger - with respect to the longitudinal axes - have different lengths. This makes it possible to achieve a gradation of an outer side of the assembled unit following the course of the inner side region (e.g., a hollow cylindrical shell).

Grundsätzlich besteht die Möglichkeit, die im Mantelraum angeordnete Einheit am Mantel festzulegen, so dass diese insbesondere den mindestens einen Wärmeübertragerblock nicht kontaktiert. Alternativ hierzu kann die Einheit auch an dem mindestens einen Wärmeübertragerblock festgelegt werden oder an einem separaten Träger.In principle, it is possible to fix the unit arranged in the jacket space on the jacket so that it does not contact the at least one heat exchanger block in particular. Alternatively, the unit may also be fixed to the at least one heat exchanger block or to a separate carrier.

Besonders bevorzugt ist gemäß einer Ausgestaltung der Erfindung vorgesehen, dass der jeweilige Kanal durch ein Hohlprofil gebildet ist. Das Hohlprofil, das vorzugsweise aus einem Metall (wie z.B. Aluminium oder Stahl) gefertigt ist, bildet dabei eine den jeweiligen Kanal umgebende Wandung aus und begrenzt bzw. bildet dadurch den jeweiligen Kanal aus. Bevorzugt sind die Hohlprofile so miteinander verbunden, dass jene zusammenhängende Einheit gebildet wird. Die Hohlprofile können dabei miteinander verschweißt werden oder durch sonstige Befestigungsmittel geeignet aneinander festgelegt werden, so dass jene Einheit bzw. das Hohlprofilregister entsteht.It is particularly preferred according to an embodiment of the invention that the respective channel is formed by a hollow profile. The hollow profile, which is preferably made of a metal (such as aluminum or steel), thereby forms a wall surrounding the respective channel and limits or thereby forms the respective channel. Preferably, the hollow profiles are connected to each other so that that coherent unit is formed. The hollow sections can be welded together or be suitably fixed to each other by other fastening means, so that that unit or the hollow profile register is formed.

Gemäß einer weiteren Ausführungsform der Erfindung sind die Kanäle durch eine Mehrzahl an miteinander verbundenen plattenförmigen Elementen gebildet (z.B. Bleche). Diese Elemente können eben ausgebildet sein (z.B. ebene Bleche) oder aber auch eine Struktur aufweisen (z.B. können jene Elemente als im Querschnitt gewellte oder gefaltete bzw. gestufte oder gezackte Elemente/Bleche ausgebildet sein). Die einzelnen Elemente können z.B. durch Ineinanderstecken aneinander festgelegt sein und können ggf. zusätzlich aneinander fixiert sein. Für das Festlegen bzw. Fixieren sind z.B. Löt- und/oder Schweißverbindungen, Nietverbindungen oder sonstige kraft-, form- und/oder stoffschlüssige Verbindungen denkbar.According to another embodiment of the invention, the channels are formed by a plurality of interconnected plate-shaped elements (e.g., sheets). These elements may be flat (e.g., planar sheets) or may have a structure (e.g., those elements may be formed as cross-section corrugated or folded or serrated elements / sheets). The individual elements may e.g. be fixed by nesting each other and may optionally be additionally fixed to each other. For fixing or fixing, e.g. Soldering and / or welded joints, rivet joints or other non-positive, positive and / or cohesive connections conceivable.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, dass die Längsachsen der Kanäle - wiederum bezogen auf einen bestimmungsgemäß angeordneten Wärmeübertrager - parallel zur Vertikalen verlaufen. Dabei können die Längsachsen der Kanäle bei einem liegenden Mantel senkrecht zur Längs- bzw. Zylinderachse des Mantels verlaufen. Bei einem stehenden Mantel verlaufen die Längsachsen der vertikalen Kanäle bevorzugt parallel zur Längs- bzw. Zylinderachse des Mantels.According to a preferred embodiment of the invention, it is provided that the longitudinal axes of the channels extend again parallel to the vertical, again in relation to a heat exchanger arranged as intended. In this case, the longitudinal axes of the channels can extend in a lying jacket perpendicular to the longitudinal or cylindrical axis of the shell. In a standing jacket, the longitudinal axes of the vertical channels preferably run parallel to the longitudinal or cylindrical axis of the jacket.

Gemäß einer alternativen bevorzugten Ausführungsform der Erfindung ist vorgesehen, dass die Längsachsen der Kanäle - wiederum bezogen auf einen bestimmungsgemäß angeordneten Wärmeübertrager - parallel zur Horizontalen verlaufen. Dabei können die Längsachsen der Kanäle bei einem liegenden Mantel parallel zur Längs- bzw. Zylinderachse des Mantels verlaufen. Bei einem stehenden Mantel verlaufen die Längsachsen der horizontalen Kanäle bevorzugt senkrecht zur Längs- bzw. Zylinderachse des Mantels.According to an alternative preferred embodiment of the invention, it is provided that the longitudinal axes of the channels - again in relation to a heat exchanger arranged as intended - run parallel to the horizontal. In this case, the longitudinal axes of the channels can extend parallel to the longitudinal or cylindrical axis of the jacket in a lying jacket. In a standing jacket, the longitudinal axes of the horizontal channels preferably extend perpendicular to the longitudinal or cylindrical axis of the jacket.

Weiterhin ist gemäß einer bevorzugten Ausführungsform der Erfindung vorgesehen, dass bei horizontal verlaufenden Kanälen zumindest einige der Kanäle eine Strömungsbremse aufweisen oder verschlossen sind, um die Einwirkung auf die flüssige Phase gezielt zu gestalten.Furthermore, it is provided according to a preferred embodiment of the invention that at horizontally extending channels, at least some of the channels have a flow brake or are closed in order to make targeted the action on the liquid phase.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist weiterhin vorgesehen, dass die Einheit bzw. ggf. die Kanäle entlang der Vertikalen eine Länge aufweist bzw. aufweisen, die zumindest größer als die Hälfte der Höhe des mindestens einen Plattenwärmeübertragers bzw. Wärmeübertragerblocks entlang der Vertikalen ist, bevorzugt größer oder gleich der Höhe des mindestens einen Plattenwärmeübertragers bzw. Wärmeübertragerblocks entlang der Vertikalen.According to a preferred embodiment of the invention, it is further provided that the unit or possibly the channels along the vertical has or have a length which is at least greater than half the height of the at least one plate heat exchanger or heat exchanger block along the vertical greater than or equal to the height of the at least one plate heat exchanger or heat exchanger block along the vertical.

Weiterhin kann bei horizontalen Kanälen vorgesehen sein, dass diese entlang ihrer Längsachse kürzer sind als die Länge des ggf. lateral angeordneten Wärmeübertragerblocks entlang der gleichen Richtung.Furthermore, it can be provided with horizontal channels that they are shorter along their longitudinal axis than the length of the optionally laterally arranged heat exchanger block along the same direction.

Bevorzugt wird die aus mehreren Kanälen bzw. Hohlprofilen zusammengesetzte Einheit zwischen dem mindestens einen Wärmeübertragerblock und dem Mantel bzw. einem dem Block horizontal gegenüberliegenden Abschnitt bzw. Innenseitenbereich des Mantels angeordnet.Preferably, the unit composed of a plurality of channels or hollow profiles is arranged between the at least one heat exchanger block and the jacket or a section or inner side region of the jacket lying horizontally opposite the block.

Sind mehrere separate Wärmeübertragerblöcke im Mantelraum angeordnet, so kann die Einheit auch zwischen zwei derartigen Blöcken angeordnet sein.If a plurality of separate heat exchanger blocks arranged in the shell space, the unit may also be arranged between two such blocks.

Schließlich können sowohl bei einem Wärmeübertragerblock als auch bei mehreren Wärmeübertragerblöcken mehrere Einheiten mit je einer Mehrzahl an Kanälen vorgesehen sein, wobei die jeweilige Einheit dann bevorzugt zwischen einem der Wärmeübertragerblöcke und dem Mantel (siehe oben) oder zwischen zwei benachbarten Wärmeübertragerblöcken angeordnet ist.Finally, a plurality of units each having a plurality of channels can be provided both in a heat exchanger block and in a plurality of heat exchanger blocks, wherein the respective unit is then preferably arranged between one of the heat exchanger blocks and the jacket (see above) or between two adjacent heat exchanger blocks.

Die jeweilige Einheit kann dabei wie oben beschrieben ausgebildet sein. Die weiteren Wärmeübertragerblöcke sind wiederum bevorzugt als Plattenwärmeübertrager, insbesondere in der oben beschriebenen Form, ausgebildet.The respective unit can be designed as described above. The further heat exchanger blocks are in turn preferably designed as a plate heat exchanger, in particular in the form described above.

Weitere Einzelheiten und Vorteile der Erfindung sollen durch die nachfolgenden Figurenbeschreibungen von Ausführungsbeispielen anhand der Figuren erläutert werden. Vorteilhafte Ausführungsformen der Erfindung sind außerdem in den Unteransprüchen angegeben.Further details and advantages of the invention will be explained by the following description of exemplary embodiments with reference to the figures. Advantageous embodiments of the invention are also specified in the subclaims.

Es zeigen:

Fig. 1
eine schematische, teilweise geschnittene Ansicht eines erfindungsgemäßen Wärmeübertragers mit stehendem Mantel und vertikalen Kanälen,
Fig. 2
eine ausschnitthafte Draufsicht auf die in der Fig. 1 gezeigten vertikalen Kanäle;
Fig. 3
eine schematische, teilweise geschnittene Ansicht eines weiteren erfindungsgemäßen Wärmeübertragers mit liegendem Mantel und vertikalen Kanälen;
Fig. 4
eine schematische, teilweise geschnittene Ansicht eines erfindungsgemäßen Wärmeübertragers mit stehendem Mantel und horizontalen Kanälen,
Fig. 5
eine ausschnitthafte Draufsicht auf die in der Fig. 4 gezeigten horizontalen Kanäle;
Fig. 6
eine schematische, teilweise geschnittene Ansicht eines weiteren erfindungsgemäßen Wärmeübertragers mit liegendem Mantel und horizontalen Kanälen; und
Fig. 7
eine schematische Schnittansicht zweier Wärmeübertragungspassagen eines Plattenwärmeübertragers wie er bei den Figuren 1, 3, 4 und 6 zum Einsatz kommen kann.
Show it:
Fig. 1
a schematic, partially sectioned view of a heat exchanger according to the invention with a standing jacket and vertical channels,
Fig. 2
a fragmentary plan view of the in the Fig. 1 shown vertical channels;
Fig. 3
a schematic, partially sectioned view of another heat exchanger according to the invention with a lying jacket and vertical channels;
Fig. 4
a schematic, partially sectioned view of a heat exchanger according to the invention with a standing jacket and horizontal channels,
Fig. 5
a fragmentary plan view of the in the Fig. 4 shown horizontal channels;
Fig. 6
a schematic, partially sectioned view of another heat exchanger according to the invention with horizontal jacket and horizontal channels; and
Fig. 7
a schematic sectional view of two heat transfer passages of a plate heat exchanger as in the FIGS. 1 . 3 . 4 and 6 can be used.

Figur 1 zeigt im Zusammenhang mit Figur 2 einen Wärmeübertrager 1, der einen stehenden, vorzugsweise (kreis)zylindrischen Mantel 2 aufweist, der einen Mantelraum 3 des Wärmeübertragers 1 begrenzt. Der Mantel 2 weist dabei eine umlaufende, zylindrische Wandung 14 auf, die stirnseitig durch zwei einander gegenüberliegende Wände 15 begrenzt wird. Die Längs- bzw. Zylinderachse des Mantels 2 fällt mit der Vertikalen z zusammen. FIG. 1 shows in connection with FIG. 2 a heat exchanger 1, which has a standing, preferably (circular) cylindrical jacket 2, which delimits a jacket space 3 of the heat exchanger 1. The jacket 2 in this case has a circumferential, cylindrical wall 14, which is delimited by two opposing walls 15 frontally. The longitudinal or cylindrical axis of the shell 2 coincides with the vertical z.

In dem vom Mantel 2 umschlossenen Mantelraum 3 sind vorliegend zwei Wärmeübertragerblöcke 4, 5 horizontal nebeneinander angeordnet, bei denen es sich um Plattenwärmeübertrager 4, 5 handelt, die mehrere parallele Wärmeübertragungspassagen P, P' aufweisen (vgl. Figur 7).In the jacket space 3 enclosed by the jacket 2, in the present case two heat exchanger blocks 4, 5 are arranged horizontally next to one another, which are plate heat exchangers 4, 5 which have a plurality of parallel heat transfer passages P, P '(cf. FIG. 7 ).

Der jeweilige Plattenwärmeübertrager 4, 5 weist dabei eine Mehrzahl an Wärmeleitstrukturen 41 auf, bei denen es sich um Bleche handeln kann, die im Querschnitt mäanderförmig ausgebildet sind, also z.B. gewellt, gezackt oder mit rechteckförmigem Verlauf. Diese Strukturen 41 werden auch als Fins 41 bezeichnet und sind jeweils zwischen zwei ebenen Trennplatten bzw. -blechen 40 des Plattenwärmeübertragers 4, 5 angeordnet. Auf diese Weise werden zwischen je zwei Trennplatten 40 (bzw. eine Trennplatte und einer Deckplatte, siehe unten) eine Vielzahl an parallelen Kanälen bzw. eine Wärmeübertragungspassage P, P' gebildet, durch die das jeweilige Medium M1, M2 strömen kann. Die beiden äußersten Lagen 40 werden durch Deckplatten des Plattenwärmeübertragers 4, 5 gebildet; zu den Seiten hin sind zwischen je zwei benachbarten Trennplatten bzw. Trenn- und Deckplatten 40 Abschlussleisten 42 vorgesehen. Die Figur 7 zeigt ausschnitthaft exemplarisch eine erste Wärmeübertragungspassage P für das erste Medium M1, die durch einen Fin 41 sowie zwei angrenzende Trennplatten 40 gebildet wird sowie eine benachbarte zweite Wärmeübertragungspassage P' für das zweite Medium M2, die ebenfalls durch einen Fin 41 sowie zwei angrenzende Trennplatten 40 gebildet wird. Eine solche Anordnung von Passagen wiederholt sich vorzugsweise in dem jeweiligen Plattenwärmeübertrager 4, 5, so dass mehrere ersten und zweite Wärmeübertragungspassagen P, P' alternierend nebeneinander angeordnet sind.The respective plate heat exchanger 4, 5 in this case has a plurality of Wärmeleitstrukturen 41, which may be sheets that are formed in a meandering cross section, so for example wavy, jagged or rectangular course. These structures 41 are also referred to as fins 41 and are each arranged between two flat separating plates or plates 40 of the plate heat exchanger 4, 5. In this way, between each two partition plates 40 (or a partition plate and a cover plate, see below) a plurality of parallel channels or a heat transfer passage P, P 'is formed, through which the respective medium M1, M2 can flow. The two outermost layers 40 are formed by cover plates of the plate heat exchanger 4, 5; towards the sides 40 end strips 42 are provided between each two adjacent partition plates or separation and cover plates. The FIG. 7 1 shows, by way of example, a first heat transfer passage P for the first medium M1, which is formed by a fin 41 and two adjacent separating plates 40 and an adjacent second heat transfer passage P 'for the second medium M2, which is likewise formed by a fin 41 and two adjacent separating plates 40 becomes. Such an arrangement of passages is preferably repeated in the respective plate heat exchanger 4, 5, so that a plurality of first and second heat transfer passages P, P 'are arranged alternately side by side.

Der Mantelraum 3 wird während eines Betriebes des Wärmeübertragers 1 mit einem ersten Medium M1 befüllt. Dieser Eintrittsstrom in den Wärmeübertrager 1 ist üblicherweise zweiphasig, kann aber auch nur flüssig sein. Die flüssige Phase F1 des ersten Mediums M1 bildet dann ein die Plattenwärmeübertrager 4, 5 umgebendes Bad aus, wobei sich die gasförmige Phase G1 des ersten Mediums M1 oberhalb der flüssigen Phase F1 in einem oberen Bereich des Mantelraumes 3 ansammelt und von dort abziehbar ist.The jacket space 3 is filled with a first medium M1 during operation of the heat exchanger 1. This inlet flow into the heat exchanger 1 is usually two-phase, but may also be liquid. The liquid phase F1 of the first medium M1 then forms a bath surrounding the plate heat exchangers 4, 5, the gaseous phase G1 of the first medium M1 accumulating above the liquid phase F1 in an upper region of the jacket space 3 and being removable therefrom.

Die flüssige Phase F1 des ersten Mediums M1 steigt in den ersten Wärmeübertragungspassagen P der Plattenwärmeübertrager 4, 5 auf und wird dabei durch das zu kühlende zweite Medium M2, das z.B. im Kreuzstrom zum ersten Medium M1 in den zweiten Wärmeübertragungspassagen P' der Plattenwärmeübertrager 4, 5 geführt wird, durch indirekte Wärmeübertragung teilweise verdampft. Die hierbei entstehende gasförmige Phase G1 des ersten Mediums M1 kann an einem oberen Ende der Plattenwärmeübertrager 4, 5 austreten und wird oberhalb der Blöcke 4, 5 aus dem Mantelraum 3 abgezogen. Weiterhin zirkuliert ein Teil der flüssigen Phase F1 im Mantelraum 3, wobei jener Teil in den Plattenwärmeübertragern 4, 5 in den ersten Wärmeübertragungspassagen P von unten nach oben gefördert wird und dann außerhalb der Plattenwärmeübertrager 4,5 im Mantelraum 3 wieder nach unten strömt.The liquid phase F1 of the first medium M1 rises in the first heat transfer passages P of the plate heat exchangers 4, 5 and thereby becomes through the second medium M2 to be cooled, which is guided eg in crossflow to the first medium M1 in the second heat transfer passages P 'of the plate heat exchangers 4, 5, partially evaporated by indirect heat transfer. The resulting gaseous phase G1 of the first medium M1 can escape at an upper end of the plate heat exchangers 4, 5 and is withdrawn from the jacket space 3 above the blocks 4, 5. Furthermore, a part of the liquid phase F1 circulates in the shell space 3, wherein that part in the plate heat exchangers 4, 5 in the first heat transfer passages P is conveyed from bottom to top and then flows outside the plate heat exchanger 4,5 in the shell space 3 back down.

Das zweite Medium M2 wird in die Plattenwärmeübertrager 4, 5 geleitet und nach einem Durchlaufen der zugeordneten zweiten Wärmeübertragungspassagen P' gekühlt bzw. verflüssigt aus den Plattenwärmeübertrager 4, 5 abgezogen.The second medium M2 is passed into the plate heat exchanger 4, 5 and after passing through the associated second heat transfer passages P 'cooled or liquefied withdrawn from the plate heat exchanger 4, 5.

Um nun bei einer schwankenden Bewegung des Mantels 2, bei der die Längs- bzw. Zylinderachse um die Vertikale z schwankt, die flüssige Phase F1 im Mantelraum 3 zu beruhigen, sind gemäß Figur 1 drei Einheiten 100 mit jeweils mehreren, parallelen Kanälen 10 vorgesehen, die sich jeweils entlang einer Längsachse L erstrecken, die parallel zur Längsachse z des Mantels 2 verläuft. Diese Kanäle 10 werden bevorzugt gemäß Figur 2 durch eine Mehrzahl an geeignet miteinander verbundenen Hohlprofilen 11 gebildet, die z.B. kreiszylindrische Kanäle 10 begrenzen und dabei stirnseitig auf beiden Seiten je eine Öffnung 10a, 10b aufweisen, wobei die eine Öffnung 10a nach oben gewandt ist und sich - entlang der Vertikalen z - in etwa auf Höhe eines oberen Endes des jeweiligen Plattenwärmeübertragers 4, 5 befindet und die andere, gegenüberliegende Öffnung 10b jeweils nach unten gewandt ist und - entlang der Vertikalen z - unterhalb der Blöcke 4, 5 endet. Die Kanäle 10 sind bevorzugt entlang zweiter orthogonaler Raumrichtungen nebeneinander angeordnet.In order to calm the liquid phase F1 in the mantle space 3 in the event of a fluctuating movement of the shell 2, in which the longitudinal or cylinder axis fluctuates about the vertical z, are in accordance with FIG. 1 three units 100 are provided, each with a plurality of parallel channels 10, each extending along a longitudinal axis L which is parallel to the longitudinal axis z of the shell 2. These channels 10 are preferred according to FIG. 2 formed by a plurality of suitably interconnected hollow sections 11, for example, limit the circular cylindrical channels 10 and thereby each have an opening 10a, 10b on both sides, wherein the opening 10a is turned upwards and - along the vertical z - approximately is at the level of an upper end of the respective plate heat exchanger 4, 5 and the other, opposite opening 10b respectively facing down and - along the vertical z - below the blocks 4, 5 ends. The channels 10 are preferably arranged next to each other along second orthogonal spatial directions.

Durch die vertikalen Kanäle 10 kann nun die aus dem jeweiligen Plattenwärmeübertrager 4, 5 am oberen Ende aus den ersten Passagen P austretende flüssige Phase F1 wieder nach unten zirkulieren, wo die flüssige Phase F1 dann am unteren Ende der Plattenwärmeübertrager 4, 5 in die ersten Wärmeübertragungspassagen P eintritt und aufgrund des Thermosiphon-Effektes wieder nach oben gezogen wird, dabei teilweise verdampft und das zweite Medium M2 abkühlt.Through the vertical channels 10 can now from the respective plate heat exchanger 4, 5 at the upper end of the first passages P emerging liquid phase F1 circulate down again, where the liquid phase F1 then at the lower end of the plate heat exchanger 4, 5 in the first heat transfer passages P occurs and is pulled back upwards due to the thermosiphon effect, thereby partly evaporating and cooling the second medium M2.

Die vertikalen Kanäle 10 stellen dabei einen Strömungswiderstand in horizontaler Richtung dar und unterdrücken daher entsprechende horizontale Bewegungen der flüssigen Phase F1 des erstem Mediums M1, während jene vertikale Zirkulation durch die Kanäle 10 geschützt wird.The vertical channels 10 represent a flow resistance in the horizontal direction and therefore suppress corresponding horizontal movements of the liquid phase F1 of the first medium M1, while those vertical circulation is protected by the channels 10.

Gemäß Figur 1 ist eine der Einheiten 100 zwischen den beiden Plattenwärmeübertragern 4, 5 lateral zu den beiden Blöcken 4, 5 angeordnet. Die beiden anderen Einheiten 100 sind jeweils zwischen einem Plattenwärmeübertrager 4, 5 und einem horizontal benachbarten Abschnitt bzw. Innenseitenbereich 2a der umlaufenden Wandung 14 des Mantels 2 angeordnet.According to FIG. 1 one of the units 100 is arranged between the two plate heat exchangers 4, 5 laterally to the two blocks 4, 5. The other two units 100 are each arranged between a plate heat exchanger 4, 5 and a horizontally adjacent section or inner side region 2 a of the peripheral wall 14 of the shell 2.

Figur 3 zeigt eine Abwandlung des Wärmeübertragers 1 gemäß Figur 1, der im Unterschied zur Figur 1 einen liegenden, längs erstreckten Mantel 2 aufweist, der sich entlang einer Längs- bzw. Zylinderachse erstreckt, die mit der Horizontalen zusammenfällt, also senkrecht zur Vertikalen z verläuft. Hierbei sind zwei Plattenwärmeübertrager 4, 5 im Unterschied zur Figur 1 entlang der Längsachse des Mantels 2 hintereinander angeordnet, wobei die beiden Blöcke 4, 5 jeweils lateral auf beiden Seiten von einer Einheit 100 flankiert werden, die wie oben beschrieben ausgebildet ist, wobei die Einheiten 100 die beiden Blöcke 4, 5 jeweils über die gesamte, kombinierte Länge der beiden Blöcke 4, 5 entlang der Längsachse des Mantels 2 flankieren. FIG. 3 shows a modification of the heat exchanger 1 according to FIG. 1 that in difference to FIG. 1 a lying, longitudinally extending jacket 2, which extends along a longitudinal or cylindrical axis which coincides with the horizontal, that is perpendicular to the vertical z. Here, two plate heat exchangers 4, 5 in contrast to FIG. 1 along the longitudinal axis of the shell 2, the two blocks 4, 5 being laterally flanked on both sides by a unit 100 formed as described above, the units 100 covering the two blocks 4, 5 over the whole, Flank combined length of the two blocks 4, 5 along the longitudinal axis of the shell 2.

Figur 4 zeigt eine weitere Abwandlung des Wärmeübertragers 1 gemäß Figur 1, bei dem nun die Kanäle 10 im Unterschied zur Figur 1 horizontal verlaufen, also senkrecht zur Längsachse des stehenden Mantels 2, die mit der Vertikalen z zusammenfällt. Die Öffnungen 10a, 10b der Kanäle 10 weisen nunmehr jeweils in eine horizontale Richtung. Die Einheiten 100 sind gemäß Figur 1 bezüglich der Plattenwärmeübertrager 4, 5 angeordnet, wobei die Einheit 100 zwischen den beiden Blöcken 4, 5 Kanäle 10 mit einer größere Strömungsquerschnittsfläche aufweist, als die Einheiten 100 auf den Außenseiten der Blöcke 4, 5. Alle Einheiten 100 stehen entlang der Vertikalen z über die oberen und unteren Enden der Plattenwärmeübertrager 4, 5 hinaus, um möglichst den gesamten Füllstand der flüssigen Phase F1 des ersten Mediums M1 bei einer schwankenden Bewegung des Wärmeübertragers 1 zu beruhigen, bei der die Längsachse z des Mantels 2 gemäß Figur 4 ihre Neigung verändert, insbesondere aus der Blattebene heraus. Die Beruhigung wird dabei durch den Strömungswiderstand erzeugt, den die flüssige Phase F1 in den horizontalen Kanälen z.B. beim hin- und her strömen zwischen den Öffnungen 10a, 10b der Kanäle 10 erfährt. Die Kanäle 10 bzw. Einheiten 100 gemäß Figur 4 können mit einer Mehrzahl an im Querschnitt rechteckförmigen bzw. quadratischen Hohlprofilen ausgebildet werden oder durch ineinander gesteckte bzw. aneinander befestige ebene, plattenförmige Elemente, insbesondere Bleche (siehe oben). Gemäß Figur 5 können die vertikalen Kanäle 10 im Querschnitt nicht nur rechteckförmig ausgebildet sein, wie exemplarisch in Fig. 4 gezeigt, sondern auch kreisförmig. Andere Formen sind ebenfalls denkbar. Zur Vergrößerung des Strömungswiderstandes in horizontaler Richtung können einzelne horizontale Kanäle 10 mit einer zusätzlichen Strömungsbremse (z.B. einer Querschnittverengung) 12 ausgestattet sein oder vollständig verschlossen sein 12. FIG. 4 shows a further modification of the heat exchanger 1 according to FIG. 1 , in which now the channels 10 in contrast to FIG. 1 run horizontally, ie perpendicular to the longitudinal axis of the stationary shell 2, which coincides with the vertical z. The openings 10a, 10b of the channels 10 now each have a horizontal direction. The units 100 are according to FIG. 1 with respect to the plate heat exchangers 4, 5, wherein the unit 100 between the two blocks 4, 5 channels 10 having a larger flow cross-sectional area than the units 100 on the outsides of the blocks 4, 5. All units 100 are along the vertical z on the upper and lower ends of the plate heat exchangers 4, 5, so as to calm as possible the entire level of the liquid phase F1 of the first medium M1 in a fluctuating movement of the heat exchanger 1, wherein the longitudinal axis z of the shell 2 according to FIG. 4 their inclination changed, in particular from the leaf level out. The reassurance is generated by the flow resistance, the liquid phase F1 in the horizontal channels, for example when flowing back and forth between the openings 10a, 10b of the channels 10 experiences. The channels 10 or units 100 according to FIG. 4 can be formed with a plurality of rectangular cross-section or square hollow profiles or by nested or attached to each other flat, plate-shaped elements, in particular sheets (see above). According to FIG. 5 For example, the vertical channels 10 may not only be rectangular in cross-section, as exemplified in FIG Fig. 4 shown, but also circular. Other shapes are also conceivable. To increase the flow resistance in the horizontal direction, individual horizontal channels 10 may be equipped with an additional flow brake (eg a cross-sectional constriction) 12 or be completely closed 12.

Figur 6 zeigt schließlich einen Wärmeübertrager 1 nach Art der Figur 4 mit horizontalen Kanälen 10, wobei nunmehr der Mantel 2 des Wärmeübertrages gemäß Figur 3 ausgebildet ist und liegend angeordnet ist. Dabei sind auf beiden Seiten der hintereinander angeordneten Plattenwärmeübertrager 4, 5, die gemäß Figur 3 platziert sind, jeweils zwischen dem jeweiligen Block 4, 5 und einem horizontal benachbarten Innenseitenbereich bzw. Abschnitt der umlaufenden Wandung 14 des Mantels 2 eine Einheit 100 mit mehreren übereinander sowie nebeneinander angeordneten horizontalen Kanälen 10 vorgesehen, die jedoch entlang der Längsachse des Mantel 2 eine geringere Ausdehnung aufweisen als die Blöcke 3, 4 entlang dieser Richtung. Hierdurch wird eine möglichst geringfügige Störung der vertikalen Zirkulation der flüssigen Phase F1 (siehe oben) ermöglicht. Weiterhin ist entlang der Längsachse des Mantels 2 gemäß Figur 6 eine weitere Einheit 100 zwischen den beiden Blöcken 4, 5 angeordnet. Auch hier funktioniert die Beruhigung der flüssigen Phase F1 des ersten Mediums wie anhand der Figur 4 beschrieben. FIG. 6 finally shows a heat exchanger 1 by type FIG. 4 with horizontal channels 10, wherein now the jacket 2 of the heat transfer according to FIG. 3 is formed and arranged horizontally. In this case, on both sides of the plate heat exchangers 4, 5, which are arranged one behind the other, according to FIG FIG. 3 are placed, respectively provided between the respective block 4, 5 and a horizontally adjacent inner side region or portion of the circumferential wall 14 of the shell 2, a unit 100 with a plurality of stacked and juxtaposed horizontal channels 10, but along the longitudinal axis of the jacket 2 a smaller Have expansion as the blocks 3, 4 along this direction. This allows the least possible disturbance of the vertical circulation of the liquid phase F1 (see above). Furthermore, along the longitudinal axis of the shell 2 according to FIG. 6 another unit 100 between the two blocks 4, 5 is arranged. Again, the reassurance of the liquid phase F1 of the first medium works as based on the FIG. 4 described.

Grundsätzlich können die miteinander verbundenen (oder auch einzelne) Hohlprofile 11 bzw. Kanäle 10 in unterschiedlichen Querschnittsformen (z.B. kreisförmig, rechteckig, wabenförmig) und Länge an jeder Position des nicht durch den jeweiligen Plattenwärmeübertrager 4, 5 belegten Mantelraumes 3, jedoch hauptsächlich im flüssigkeitsgefüllten Bereich (also neben dem Block 4 bzw. 5, den Blöcken 4, 5 und / oder zwischen den Blöcken 4, 5) angebracht sein. Die Anzahl der Einheiten bzw.Basically, the interconnected (or individual) hollow sections 11 and channels 10 in different cross-sectional shapes (eg circular, rectangular, honeycomb) and length at any position of not occupied by the respective plate heat exchanger 4, 5 shell space 3, but mainly in the liquid-filled area (So next to the block 4 or 5, the blocks 4, 5 and / or between the blocks 4, 5) be attached. The number of units or

Register 100 ist anpassbar. Diese Einheiten 100 werden nur in vertikaler Richtung oder in horizontaler Richtung von der flüssigen Phase F1 durchströmt. Der Verbund selbst stellt einen Strömungswiderstand in horizontaler Richtung dar. Dadurch werden horizontale Strömungen gedämpft. Die Einheiten 100 bzw. Kanäle 10 können sowohl in vertikaler als auch in den horizontalen Dimensionen den jeweiligen Anforderungen angepasst werden und können ggf. auch unterteilt sein. Die Größe der einzelnen Kanäle 10 im Querschnitt ist flexibel und kann ebenfalls an die jeweiligen Anforderungen angepasst werden. Die einzelnen Kanäle 10 der Einheiten 100 können unterschiedliche Längen aufweisen. Insbesondere bei horizontalen Kanälen 10 bzw. Hohlprofilen 11 können einzelne Profile 11 verschlossen sein, um den Strömungswiderstand anzupassen. Dadurch werden horizontale Strömungen gedämpft.Register 100 is customizable. These units 100 are flowed through only in the vertical direction or in the horizontal direction of the liquid phase F1. The composite itself represents a flow resistance in the horizontal direction. This dampens horizontal flows. The units 100 or channels 10 can be adapted to the respective requirements both in vertical and in the horizontal dimensions and can also be subdivided if necessary. The size of the individual channels 10 in cross section is flexible and can also be adapted to the respective requirements. The individual channels 10 of the units 100 may have different lengths. Especially with horizontal channels 10 or hollow sections 11, individual profiles 11 may be closed in order to adapt the flow resistance. This dampens horizontal currents.

Zusammenfassend erlauben die Erfindungsgemäßen Einheiten bzw. Hohlprofilregister 100 eine große Einflussnahme auf die Strömungsrichtung der zirkulierenden Flüssigkeit F1 im Behälter 2, ohne dass dazu eine hohe Anzahl von Einzelteilen erforderlich wäre. Das Flüssigkeitsvolumen außerhalb der Plattenwärmeübertrager 4, 5 kann sehr stark segmentiert werden, obwohl der Fertigungs- und Montageaufwand dafür verhältnismäßig gering bleibt. Die Segmentierung erlaubt weiterhin geringe Wandstärken der Einheiten 100 bzw. Kanäle 10 / Hohlprofile 11, da der Verbund 100 einen robusten Körper 100 darstellt und nur kleinräumige Flüssigkeitsbewegungen zulässt. Durch Anpassen der Abmessungen der einzelnen Elemente 10 sowie des Verbundes 100 insgesamt können die Eigenfrequenzen von schwingender Flüssigkeit F1 im Behälter 2 bzw. Mantelraum 3 beeinflusst und Bewegungen gedämpft werden. Damit kann ein Anregen in Eigenfrequenz und hohe Schwingungsamplituden verhindert werden.In summary, the units or hollow profile register 100 according to the invention allow a great influence on the flow direction of the circulating liquid F1 in the container 2, without requiring a high number of individual parts. The volume of liquid outside the plate heat exchangers 4, 5 can be very highly segmented, although the manufacturing and assembly costs for it remains relatively low. The segmentation further allows low wall thicknesses of the units 100 or channels 10 / hollow sections 11, since the composite 100 represents a robust body 100 and only allows small-scale fluid movements. By adjusting the dimensions of the individual elements 10 and of the composite 100 as a whole, the natural frequencies of oscillating liquid F1 in the container 2 or jacket space 3 can be influenced and movements dampened. Thus, a stimulation in natural frequency and high vibration amplitudes can be prevented.

Besonders bevorzugt wird der erfindungsgemäße Wärmeübertrager 1 auf einem Schwimmkörper auf einem Gewässer eingesetzt, z.B. als Komponente einer schwimmenden Anlage zur Herstellung von flüssigem Erdgas (LNG). Bezugszeichenliste 1 Wärmeübertrager 2 Mantel 2a Innenseite 3 Mantelraum 4,5 Plattenwärmeübertrager 10 Kanal 10a, 10b Öffnung 11 Hohlprofil 14 Wandung 15 Wand 40 Trennplatten 41 Wärmeleitstrukturen bzw. Fins 42 Side Bars 100 Einheit M1 Erstes Medium M2 Zweites Medium G1 Gasförmige Phase erstes Medium F1 Flüssige Phase erstes Medium P Erste Wärmeübertragungspassage P' Zweite Wärmeübertragungspassage Z Vertikale Particularly preferably, the heat exchanger 1 according to the invention is used on a float on a body of water, for example as a component of a floating plant for the production of liquid natural gas (LNG). <B> LIST OF REFERENCES </ b> 1 Heat exchanger 2 coat 2a inside 3 shell space 4.5 Plate heat exchangers 10 channel 10a, 10b opening 11 hollow profile 14 wall 15 wall 40 partition plates 41 Wärmeleitstrukturen or Fins 42 Side bars 100 unit M1 First medium M2 Second medium G1 Gaseous phase first medium F1 Liquid phase first medium P First heat transfer passage P ' Second heat transfer passage Z vertical

Claims (14)

  1. Heat exchanger for indirect heat transfer between a first medium (M1) and a second medium (M2), with:
    - a shell (2), which has a shell space (3) for receiving a liquid phase (F1) of the first medium (M1), and
    - at least one heat exchanger block (4), which has first heat transfer passages (P) for receiving the first medium (M1) and second heat transfer passages (P') for receiving the second medium (M2), so that heat can be transferred indirectly between the two media (M1, M2), wherein the at least one heat exchanger block (4) is arranged in the shell space (3) in such a way that it can be surrounded by a liquid phase (F1) of the first medium (M1) that is located in the shell space (3),
    characterized
    in that a plurality of cylindrical channels (10) for conducting the liquid phase of the first medium (M1) that run parallel to one another are provided in the shell space (3) laterally in relation to the at least one heat exchanger block (4, 5).
  2. Heat exchanger according to Claim 1, characterized in that the channels (10) are fixed to one another in such a way that they form an interlinked unit (100), which is in particular formed separately from the at least one heat exchanger block (4) and/or the shell (2).
  3. Heat exchanger according to Claim 1 or 2, characterized in that the extent of the channels (10) along the longitudinal axis (L) of the respective channel (10) is greater than the greatest inside diameter of the respective channel (10) perpendicularly in relation to the respective longitudinal axis.
  4. Heat exchanger according to one of the preceding claims, characterized in that - with respect to the longitudinal axes (L) - the channels (10) have the same length, or in that - with respect to the longitudinal axes (L) - at least some channels (10) have different lengths, in particular to adapt the unit (100) to a curved region of an inner side (2a) of the shell (2).
  5. Heat exchanger according to one of the preceding claims, characterized in that the respective channel (10) is formed by a hollow profile (11), in particular the hollow profiles (11) being connected to one another in such a way that the interlinked unit (100) referred to is formed.
  6. Heat exchanger according to one of the preceding claims, characterized in that the channels (10) are formed by a plurality of interconnected plate-shaped elements, which are connected to one another.
  7. Heat exchanger according to one of the preceding claims, characterized in that the longitudinal axes (L) of the channels (10) run parallel to the vertical (z).
  8. Heat exchanger according to one of Claims 1 to 6, characterized in that the longitudinal axes (L) of the channels (10) run parallel to the horizontal.
  9. Heat exchanger according to Claim 8, characterized in that at least some of the channels (10) have a flow retarder (12) or are closed (12).
  10. Heat exchanger according to Claim 2 or one of Claims 3 to 9, insofar as said claims refer back to Claim 2, characterized in that the unit (100) has along the vertical (z) a length that is at least greater than half the height of the at least one heat exchanger block (4) along the vertical (z), preferably greater than or equal to the height of the at least one heat exchanger block (4) along the vertical (z).
  11. Heat exchanger according to Claim 2 or one of Claims 3 to 10, insofar as said claims refer back to Claim 2, characterized in that the unit (100) is arranged between the at least one heat exchanger block (4) and a neighboring portion (2a) of the shell (2).
  12. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger (1) has a further heat exchanger block (5), which is arranged in the shell space (3) and along the horizontal is arranged next to the one heat exchanger block (4)
  13. Heat exchanger according to Claims 2 and 12, characterized in that the unit (100) is arranged between the two heat exchanger blocks (4, 5).
  14. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger (1) has a plurality of units (100), which respectively have a plurality of cylindrical channels (10) for conducting the liquid phase (F1) of the first medium (M1) that run parallel to one another, in particular the respective unit (100) being arranged between one of the heat exchanger blocks (4, 5) and a neighboring portion (2a) of the shell (2) or between two heat exchanger blocks (4, 5) .
EP15720913.1A 2014-05-13 2015-05-07 Heat exchanger with channels for damping movements of liquids Active EP3143352B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14001684.1A EP2944909A1 (en) 2014-05-13 2014-05-13 Heat exchanger with channels for damping movements of liquids
PCT/EP2015/000931 WO2015172870A1 (en) 2014-05-13 2015-05-07 Heat exchanger having channels for damping liquid motions

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EP3143352A1 EP3143352A1 (en) 2017-03-22
EP3143352B1 true EP3143352B1 (en) 2017-11-29

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EP (2) EP2944909A1 (en)
JP (1) JP2017519174A (en)
KR (1) KR20170005092A (en)
CN (1) CN106461348A (en)
AU (1) AU2015258457A1 (en)
CA (1) CA2947366A1 (en)
ES (1) ES2657848T3 (en)
MX (1) MX2016014435A (en)
RU (1) RU2016148615A (en)
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WO (1) WO2015172870A1 (en)

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JP6904190B2 (en) * 2017-09-19 2021-07-14 株式会社デンソー Vehicle heat exchanger
US11149981B2 (en) * 2017-11-20 2021-10-19 Atlantic, Gulf & Pacific Company Of Manila, Inc. Systems for vaporizing that include marinized vaporizer units, and methods for making and using such systems
US20220290916A1 (en) * 2019-08-14 2022-09-15 Shell Oil Company Heat exchanger system and method
WO2021093993A1 (en) 2019-11-15 2021-05-20 Linde Gmbh Transition component having insulation
US12025383B2 (en) 2021-03-30 2024-07-02 Mitsubishi Electric Us, Inc. Air-to-air heat recovery core and method of operating the same

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US2922287A (en) * 1954-03-22 1960-01-26 Garrett Corp Liquid storage tank
US4750631A (en) * 1986-07-21 1988-06-14 Sperry Corporation Anti-slosh apparatus for liquid containers
FR2685071B1 (en) * 1991-12-11 1996-12-13 Air Liquide INDIRECT PLATE TYPE HEAT EXCHANGER.
US5651270A (en) * 1996-07-17 1997-07-29 Phillips Petroleum Company Core-in-shell heat exchangers for multistage compressors
DE19722360A1 (en) * 1997-05-28 1998-12-03 Bayer Ag Method and device for improving heat transfer
FR2807826B1 (en) * 2000-04-13 2002-06-14 Air Liquide BATH TYPE CONDENSER VAPORIZER
KR101313617B1 (en) * 2010-07-13 2013-10-02 삼성중공업 주식회사 Sloshing impact reduce device of Cargo Containment and method of reduce the same
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JP6270734B2 (en) * 2011-12-20 2018-01-31 コノコフィリップス カンパニー Internal baffle for sloshing suppression in core heat exchanger in shell

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AU2015258457A1 (en) 2016-11-10
ES2657848T3 (en) 2018-03-07
EP2944909A1 (en) 2015-11-18
US20170051985A1 (en) 2017-02-23
EP3143352A1 (en) 2017-03-22
RU2016148615A (en) 2018-06-13
CA2947366A1 (en) 2015-11-19
CN106461348A (en) 2017-02-22
TR201802608T4 (en) 2018-03-21
KR20170005092A (en) 2017-01-11
MX2016014435A (en) 2017-01-23
JP2017519174A (en) 2017-07-13
WO2015172870A1 (en) 2015-11-19

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