EP3143352B1 - Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides - Google Patents

Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides 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
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German (de)
English (en)
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EP3143352A1 (fr
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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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Ocean & Marine Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (14)

  1. Échangeur de chaleur pour le transfert de chaleur indirect entre un premier milieu (M1) et un deuxième milieu (M2), comprenant :
    - une enveloppe (2) qui présente un espace d'enveloppe (3) pour recevoir une phase liquide (F1) du premier milieu (M1) et
    - au moins un bloc échangeur de chaleur (4) qui présente des premiers passages de transfert de chaleur (P) pour recevoir le premier milieu (M1) ainsi que des deuxièmes passages de transfert de chaleur (P') pour recevoir le deuxième milieu (M2), de telle sorte que de la chaleur puisse être transmise indirectement entre les deux milieux (M1, M2), l'au moins un bloc échangeur de chaleur (4) étant disposé dans l'espace d'enveloppe (3) de telle sorte qu'il puisse être entouré par une phase liquide (F1) du premier milieu (M1) se trouvant dans l'espace d'enveloppe (3),
    caractérisé en ce que
    dans l'espace d'enveloppe (3), latéralement à l'au moins un bloc échangeur de chaleur (4, 5), est prévue une pluralité de canaux cylindriques s'étendant parallèlement les uns aux autres (10) pour conduire la phase liquide du premier milieu (M1) .
  2. Échangeur de chaleur selon la revendication 1, caractérisé en ce que les canaux (10) sont fixés les uns aux autres de telle sorte qu'ils forment une unité cohérente (100) qui est notamment réalisée séparément de l'au moins un bloc échangeur de chaleur (4) et/ou de l'enveloppe (2).
  3. Échangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que l'étendue des canaux (10) le long de l'axe longitudinal (L) du canal respectif (10) est plus importante que le plus grand diamètre intérieur du canal respectif (10) perpendiculairement à son axe longitudinal.
  4. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les canaux (10) - par rapport aux axes longitudinaux (L) - présentent la même longueur ou en ce qu'au moins certains canaux (10), en particulier pour adapter l'unité (100) à une région courbe d'un côté intérieur (2a) de l'enveloppe (2) - par rapport aux axes longitudinaux (L) - présentent des longueurs différentes.
  5. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que chaque canal (10) est formé par un profilé creux (11), les profilés creux (11) étant en particulier connectés les uns aux autres de telle sorte que l'unité cohésive (100) soit formée.
  6. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les canaux (10) sont formés par une pluralité d'éléments en forme de plaque connectés les uns aux autres, qui sont connectés les uns aux autres.
  7. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que les axes longitudinaux (L) des canaux (10) s'étendent parallèlement à la verticale (z).
  8. Échangeur de chaleur selon l'une quelconque des revendications 1 à 6, caractérisé en ce que les axes longitudinaux (L) des canaux (10) s'étendent parallèlement à l'horizontale.
  9. Échangeur de chaleur selon la revendication 8, caractérisé en ce qu'au moins certains des canaux (10) présentent une restriction d'écoulement (12) ou sont fermés (12).
  10. Échangeur de chaleur selon la revendication 2 ou selon l'une quelconque des revendications 3 à 9 dans la mesure où elle se rapporte à la revendication 2, caractérisé en ce que l'unité (100) le long de la verticale (z) présente une longueur qui est au moins supérieure à la moitié de la hauteur de l'au moins un bloc échangeur de chaleur (4) le long de la verticale (z), de préférence qui est supérieure ou égale à la hauteur de l'au moins un bloc échangeur de chaleur (4) le long de la verticale (z).
  11. Échangeur de chaleur selon la revendication 2 ou selon l'une quelconque des revendications 3 à 10 dans la mesure où elle se rapporte à la revendication 2, caractérisé en ce que l'unité (100) est disposée entre l'au moins un bloc échangeur de chaleur (4) et une portion adjacente (2a) de l'enveloppe (2).
  12. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'échangeur de chaleur (1) présente un bloc échangeur de chaleur supplémentaire (5) disposé dans l'espace d'enveloppe (3), qui est disposé le long de l'horizontale à côté de l'un des blocs échangeurs de chaleur (4).
  13. Échangeur de chaleur selon les revendications 2 et 12, caractérisé en ce que l'unité (100) est disposée entre les deux blocs échangeurs de chaleur (4, 5).
  14. Échangeur de chaleur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'échangeur de chaleur (1) présente une pluralité d'unités (100) qui présentent chacune une pluralité de canaux cylindriques (10) s'étendant parallèlement les uns aux autres pour le guidage de la phase liquide (F1) du premier milieu (M1), l'unité respective (100) étant à chaque fois disposée entre l'un des blocs échangeurs de chaleur (4, 5) et une portion adjacente (2a) de l'enveloppe (2) ou entre deux blocs échangeurs de chaleur (4, 5).
EP15720913.1A 2014-05-13 2015-05-07 Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides Active EP3143352B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14001684.1A EP2944909A1 (fr) 2014-05-13 2014-05-13 Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides
PCT/EP2015/000931 WO2015172870A1 (fr) 2014-05-13 2015-05-07 Échangeur de chaleur muni de conduits pour amortir les mouvements du liquide

Publications (2)

Publication Number Publication Date
EP3143352A1 EP3143352A1 (fr) 2017-03-22
EP3143352B1 true EP3143352B1 (fr) 2017-11-29

Family

ID=50729335

Family Applications (2)

Application Number Title Priority Date Filing Date
EP14001684.1A Withdrawn EP2944909A1 (fr) 2014-05-13 2014-05-13 Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides
EP15720913.1A Active EP3143352B1 (fr) 2014-05-13 2015-05-07 Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP14001684.1A Withdrawn EP2944909A1 (fr) 2014-05-13 2014-05-13 Dispositif de transmission de la chaleur doté de canaux destinés à l'amortissement de mouvements de fluides

Country Status (12)

Country Link
US (1) US20170051985A1 (fr)
EP (2) EP2944909A1 (fr)
JP (1) JP2017519174A (fr)
KR (1) KR20170005092A (fr)
CN (1) CN106461348A (fr)
AU (1) AU2015258457A1 (fr)
CA (1) CA2947366A1 (fr)
ES (1) ES2657848T3 (fr)
MX (1) MX2016014435A (fr)
RU (1) RU2016148615A (fr)
TR (1) TR201802608T4 (fr)
WO (1) WO2015172870A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP6904190B2 (ja) * 2017-09-19 2021-07-14 株式会社デンソー 車両用熱交換装置
US10823453B2 (en) * 2017-11-20 2020-11-03 Atlantic, Gulf & Pacific Company Of Manila, Inc. Marinized vaporizer units, and methods of making and using same
CN113950595A (zh) 2019-11-15 2022-01-18 林德有限责任公司 具有绝缘的过渡部件

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 (fr) * 1991-12-11 1996-12-13 Air Liquide Echangeur de chaleur indirect du type a plaques.
US5651270A (en) * 1996-07-17 1997-07-29 Phillips Petroleum Company Core-in-shell heat exchangers for multistage compressors
DE19722360A1 (de) * 1997-05-28 1998-12-03 Bayer Ag Verfahren und Vorrichtung zur Verbesserung des Wärmeüberganges
FR2807826B1 (fr) * 2000-04-13 2002-06-14 Air Liquide Echangeur vaporisateur-condenseur du type a bain
KR101313617B1 (ko) * 2010-07-13 2013-10-02 삼성중공업 주식회사 액상 화물 화물창의 슬로싱 임팩트 저감장치 및 저감방법
US9464851B2 (en) * 2010-12-09 2016-10-11 Provides Metalmeccanica S.R.L. Heat exchanger
CN103946658B (zh) * 2011-11-18 2017-02-22 开利公司 管壳式热交换器
AU2012355357B2 (en) * 2011-12-20 2016-12-22 Conocophillips Company Internal baffle for suppressing slosh in a core-in-shell heat exchanger

Also Published As

Publication number Publication date
US20170051985A1 (en) 2017-02-23
CN106461348A (zh) 2017-02-22
JP2017519174A (ja) 2017-07-13
KR20170005092A (ko) 2017-01-11
TR201802608T4 (tr) 2018-03-21
CA2947366A1 (fr) 2015-11-19
EP2944909A1 (fr) 2015-11-18
MX2016014435A (es) 2017-01-23
ES2657848T3 (es) 2018-03-07
AU2015258457A1 (en) 2016-11-10
WO2015172870A1 (fr) 2015-11-19
RU2016148615A (ru) 2018-06-13
EP3143352A1 (fr) 2017-03-22

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