EP1329680A1 - Echangeur de chaleur à plaques - Google Patents

Echangeur de chaleur à plaques Download PDF

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Publication number
EP1329680A1
EP1329680A1 EP02009896A EP02009896A EP1329680A1 EP 1329680 A1 EP1329680 A1 EP 1329680A1 EP 02009896 A EP02009896 A EP 02009896A EP 02009896 A EP02009896 A EP 02009896A EP 1329680 A1 EP1329680 A1 EP 1329680A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger block
heat
heat exchange
exchange passages
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.)
Granted
Application number
EP02009896A
Other languages
German (de)
English (en)
Other versions
EP1329680B1 (fr
Inventor
Horst Corduan
Dietrich Rottmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Linde GmbH
Original Assignee
Linde GmbH
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Filing date
Publication date
Application filed by Linde GmbH filed Critical Linde GmbH
Publication of EP1329680A1 publication Critical patent/EP1329680A1/fr
Application granted granted Critical
Publication of EP1329680B1 publication Critical patent/EP1329680B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04284—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using internal refrigeration by open-loop gas work expansion, e.g. of intermediate or oxygen enriched (waste-)streams
    • F25J3/0429—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using internal refrigeration by open-loop gas work expansion, e.g. of intermediate or oxygen enriched (waste-)streams of feed air, e.g. used as waste or product air or expanded into an auxiliary column
    • F25J3/04296—Claude expansion, i.e. expanded into the main or high pressure column
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04333—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using quasi-closed loop internal vapor compression refrigeration cycles, e.g. of intermediate or oxygen enriched (waste-)streams
    • F25J3/04339—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using quasi-closed loop internal vapor compression refrigeration cycles, e.g. of intermediate or oxygen enriched (waste-)streams of air
    • F25J3/04345—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion using quasi-closed loop internal vapor compression refrigeration cycles, e.g. of intermediate or oxygen enriched (waste-)streams of air and comprising a gas work expansion loop
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04248—Generation of cold for compensating heat leaks or liquid production, e.g. by Joule-Thompson expansion
    • F25J3/04375—Details relating to the work expansion, e.g. process parameter etc.
    • F25J3/04393—Details relating to the work expansion, e.g. process parameter etc. using multiple or multistage gas work expansion
    • 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
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04406—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system
    • F25J3/04412—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system in a classical double column flowsheet, i.e. with thermal coupling by a main reboiler-condenser in the bottom of low pressure respectively top of high pressure 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F25J2205/00—Processes or apparatus using other separation and/or other processing means
    • F25J2205/02—Processes or apparatus using other separation and/or other processing means using simple phase separation in a vessel or drum
    • F25J2205/04—Processes or apparatus using other separation and/or other processing means using simple phase separation in a vessel or drum in the feed line, i.e. upstream of the fractionation step
    • 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
    • F25J2245/00—Processes or apparatus involving steps for recycling of process streams
    • F25J2245/50—Processes or apparatus involving steps for recycling of process streams the recycled stream being oxygen
    • 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
    • F25J2290/32—Details on header or distribution passages of heat exchangers, e.g. of reboiler-condenser or plate 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
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/42—Modularity, pre-fabrication of modules, assembling and erection, horizontal layout, i.e. plot plan, and vertical arrangement of parts of the cryogenic unit, e.g. of the cold box

Definitions

  • the invention relates to a plate heat exchanger for indirect heat exchange of several fluid flows with one heat / coolant in one Heat exchanger block that has a variety of heat exchange passages for the Has heat / coolant, a first fluid stream and a second fluid stream.
  • the invention further relates to a method for indirect heat exchange of multiple fluid flows with one heat / coolant in one Heat exchanger block, the heat / cold carrier, a first fluid flow and a second fluid flow through a variety of heat exchange passages.
  • the feed air to be separated When air is decomposed at low temperatures, the feed air to be separated must be on the Process temperature are cooled. This is usually done in Main heat exchanger through indirect heat exchange of the feed air with the recovered gas flows.
  • the main heat exchanger is usually called Plate heat exchanger designed a variety of Has heat exchange passages for the streams to be treated.
  • an air separation plant will have two different air flows Pressure supplied and as gaseous products oxygen, pure nitrogen and impure Recovered nitrogen, five streams must pass through the heat exchanger block become.
  • the heat exchanger block must therefore have ten connecting pieces for this Currents, five for the gas inlet and five for the gas outlet.
  • the gas flows are then assigned from the respective inlet connection to the Heat exchange passages distributed or those from the Heat exchange passages emerging gas flows into the corresponding Outlet connection merged.
  • DE 10021081 therefore proposes for large air separation plants to use split heat exchanger blocks divided by products so that only one fluid flow is passed through each heat exchanger block.
  • fluid flows can be carried out without the aforementioned distribution zones routed directly from the connecting piece into the respective heat exchange passages become.
  • the object of the present invention is therefore to provide a method and an apparatus for to develop indirect heating or cooling of multiple gas flows which the pressure loss in the heat exchanger is as low as possible.
  • a plate heat exchanger solved type mentioned wherein the heat exchanger block a first Has sub-area in which all heat exchange passages for the first fluid flow are arranged, and has a second portion in which all Heat exchange passages for the second fluid flow are arranged, the first and the second partial area do not overlap and the first and the second Part of each extend over the entire height of the heat exchanger block, the height of the heat exchanger block being extended in the direction of the Main flow through the heat exchange passages is.
  • the inventive method for indirect heat exchange of several Fluid flows with a heat / coolant in a heat exchanger block, wherein the heat / cold carrier, a first fluid stream and a second fluid stream through one A large number of heat exchange passages are guided, that the first fluid flow only through a first portion of the Heat exchanger blocks is passed and the second fluid flow through only one second portion of the heat exchanger block is passed, the first and the second section does not overlap and the first and the second Part of each extend over the entire height of the heat exchanger block, the height of the heat exchanger block being extended in the direction of the Main flow through the heat exchange passages is.
  • the depth, height and width of the heat exchanger block are defined as follows: On Heat exchanger block has a plurality of arranged parallel to each other Partition plates on. The expansion of the heat exchanger block in one direction perpendicular to the partition plates is referred to below as depth. Between Partition plates are usually arranged so-called fins that cover the space between Subdivide two separating plates into several heat exchange passages at least over a large part of the heat exchanger block all in the same direction exhibit. The expansion of the heat exchanger block in the direction of flow through the heat exchange passages characterize its height. This direction is in hereinafter referred to simply as vertical. With width, therefore Expansion of the heat exchanger block in the remaining spatial direction perpendicular to the main flow direction in the heat exchange passages in the plane of the dividing plates.
  • a distribution of the fluid flow over the entire cross-sectional area of the Heat exchanger blocks are no longer necessary.
  • An integrated heat exchanger block is advantageously used, through which at least two fluid flows, preferably all fluid flows in the indirect Heat exchange can be carried out with one or more heating media.
  • At least one Part of the heat exchange passages for the fluid flows is in the direction of Width divided into at least two areas. Preferably all are for the The fluid exchange passages provided are divided accordingly. It is but also possible and sensible, such a division only for a part the fluid flow passages.
  • the subdivision is such that the space between two partition plates in which the individual heat exchange passages for the fluid streams run through or Multiple vertical partitions are divided into two or more areas between where no fluid exchange is possible. There are one within a range A large number of heat exchange passages, which are usually caused by vertical, so-called fins are separated from each other. The fins are mainly used for Guide the fluids, however, in contrast to the different areas partition walls, not essential for the insulation of a Heat exchange passage from an adjacent heat exchange passage.
  • the division into individual areas can also be carried out cheaply so that the Areas occupy only part of the depth of the heat exchanger block. So for example, it is possible to split the heat exchanger block into two or more Divide strips that extend across the entire height of the heat exchanger block extend and each take up part of the depth or width of the block. at It is also advantageous to use several streams to adjust the width and width of the heat exchanger block to subdivide the depth and provide, for example, four areas, one of which is everyone is in a corner of the heat exchanger block.
  • those for the respective extend Fluid flow provided heat exchange passages from one face of the block to the opposite end face and run essentially parallel to each other.
  • a collector / distributor attached to the outside of the heat exchanger block, which covers the corresponding area of the end face and a connecting piece for the Has supply or discharge.
  • the heat exchange passages are therefore without Cross-sectional tapering in the inlet and outlet via and the flow deflection in the collector / distributor takes place slowly. The pressure loss in the Heat exchanger block and the associated collectors / distributors minimized.
  • At least one fluid flow is as low as possible Pressure loss should experience through such a partial area of the invention Head of heat exchanger blocks.
  • the invention is advantageous.
  • flow through one of the Subregions of the heat exchanger block according to the invention one or more Heating media with which the fluid flow exchanges its heat.
  • the invention allows pressure drops in the heat exchanger blocks, measured from the inlet to the outlet, achieve about 70 mbar.
  • the conventional heat exchangers in which the Distribution and consolidation of the gas flows between the entry and Outlet connection and the heat exchange passages through a in the Heat exchanger block integrated distribution zone with slanted fins Pressure drop of about 100 mbar when the gas flows with a pressure between 1.2 and 1.8 bar were removed from the low pressure column.
  • the invention achieves a reduction in pressure drop of approximately 30 mbar. This means that the low pressure flows are 30 mbar lower Pressure than can otherwise be gained. To maintain the Heat exchange conditions at the main condenser are sufficient if the air after the air compressor is compressed to about 90 mbar lower pressure.
  • the invention is particularly suitable in processes in which gas streams, one Have pressure of less than 3.5 bar, preferably between 1.1 and 1.8 bar, in hereinafter referred to as low pressure flows, in indirect heat exchange with a Heat or cold carriers are to be brought. According to the invention, this is done by a portion of the heat exchanger block only one of these Low pressure gas flows, i.e. for each of the gas streams that have a pressure of have less than 3.5 bar, a separate section of the Heat exchanger blocks provided.
  • the method according to the invention is preferably used in low-temperature decomposition of application air application.
  • Gas streams withdrawn from the double column rectifier have only a small amount Overpressure of about 0.1 to 0.8 bar above atmospheric pressure, so that a reduction the pressure drop is of great importance. This applies analogously to gaseous Argon product, since the crude argon column also operates under relatively low pressure becomes.
  • the gas flows with the feed air in indirect are particularly preferred Heat exchange brought.
  • the feed air can be divided into several flows through the heat exchanger block at different pressure levels be performed.
  • the air supply can be below Pressure column pressure passed through the heat exchanger block and then into the Pressure column can be fed, on the other hand, the feed air can before Heat exchanger block post-compressed and after cooling for cooling be relaxed while working.
  • the fluid stream is preferably passed through the heat exchanger block in such a way that he suffers a pressure drop of 120 to 300 mbar, preferably 120 to 200 mbar.
  • a pressure drop of 120 to 300 mbar, preferably 120 to 200 mbar.
  • FIG. 1 shows a process scheme known from the prior art Cryogenic air separation plant.
  • Compressed and cleaned feed air 10 is partly directly one Main heat exchanger 1 supplied, in part 20 by means of a compressor 4 post-compressed, cooled in an aftercooler 5 and then in the Main heat exchanger 1 passed.
  • This in the following as turbine air flow 20 designated compressed air is the main heat exchanger 1 at an intermediate point removed, relaxed in an air booster turbine 6 and into the low pressure column 3 one comprising a pressure column 2 and a low pressure column 3 Rectification unit initiated.
  • the feed air 10 cooled in the main heat exchanger becomes the pressure column 2 fed to the rectification unit.
  • the low pressure column 3 become more gaseous Oxygen 50, gaseous nitrogen 30 and gaseous impure nitrogen 40 as Regeneration gas removed at a pressure of about 1.3 bar.
  • pressure nitrogen 60 is drawn off. It is also possible in the Rectification unit to obtain oxygen and nitrogen as liquid products 7, 8.
  • the gas streams 30, 40, 50, 60 are fed into the main heat exchanger 1 and against the feed air flow 10 and the turbine air flow 20 by indirect Heat exchange warmed up.
  • Figures 2 to 4 show the usual construction of the heat exchanger block 9.
  • Figure 2 shows the lamella arrangement in the distribution zones 59 for the Oxygen passages 58, FIG. 3 for the pure nitrogen passages 38 and FIG. 4 correspondingly for the impure nitrogen passages 48.
  • the Fluid flows 30, 40, 50 out against the air flow 10 and the turbine air flow 20.
  • the distribution of the respective gaseous product among the corresponding ones Heat exchange passages 38, 48, 58 are conventionally carried out via distribution zones 39, 49, 59, which have slanted slats to the gas 30, 40, 50 from the To distribute supply lines to the passages 38, 48, 58 or in order to the gas passages 38, 48, 58 into the corresponding exhaust line merge.
  • the distribution zones 39, 49, 59 both lead to a change in the direction of flow as well as cross-sectional changes, which in turn changes the Cause flow velocity. Both have a negative impact on the Block flow and creates an undesirable pressure drop across the Heat exchanger block 9. The pressure drop affects in particular the Gas streams that have a relatively low pressure between 1.1 and 1.8 bar, negative.
  • FIG. 5 shows the structure of the main heat exchanger 1 according to the invention
  • all streams 10, 20, 30, 40, 50, 60 are shared by one Heat exchanger block 9 out, that is, the main heat exchanger 1 is as integrated heat exchanger.
  • the heat exchanger block 9 is off built up a large number of dividing plates parallel to the drawing plane, between which there are a large number of heat exchange passages.
  • the expansion of the heat exchanger block 9 is perpendicular to Plane as its depth, its extension in the direction of the Heat exchange passages, which are indicated by arrows in FIGS. 2 to 4, as its height and its extent in the plane of the drawing perpendicular to Flow direction through the heat exchange passages referred to as its width.
  • the feed air 10, the high pressure air 20 and that taken from the pressure column 2 gaseous pressurized nitrogen 60 are in the collector / distributor 11, 21, 61 in the Heat exchanger block 9 passed. These are in the heat exchanger block 9 Currents 10, 20, 60 in the usual way, each in one in the drawing shown distribution zone, which has sloping slats, over the entire Distributed width of the heat exchanger block 9, further by vertical Passed heat exchange passages and the respective via a further distribution zone Collectors 12, 22, 62 fed.
  • the streams 10, 20, 60 experience pressure losses caused by the Current direction changes and the cross-sectional changes of the individual passages caused.
  • the pressure losses of about 100 mbar are at Feed air 10
  • the high pressure air 20 and the pressure nitrogen product 60 are not relevant, since these flows have a significantly higher absolute pressure of more than 5 bar exhibit.
  • the low-pressure streams 30, 40, 50 one compared to the Atmospheric pressure have only slightly increased pressure, have such Pressure losses, on the other hand, are of great importance.
  • the low-pressure flows 30, 40, 50 are therefore not via the distributed over the entire width of the heat exchanger block 9.
  • the heat exchanger block 9 is divided in its width by dividing plates 70, so-called side bars, into three areas 33, 43, 53 divided. With each of these areas 33, 43, 53 are at the top and bottom End of the heat exchanger block 9 collector / distributor 31, 41, 51 and 32, 42, 52 connected.
  • the collectors / distributors 31, 41, 51 and 32, 42, 52 are semi-cylindrical executed and have a connecting piece for the respective product supply or dissipation.
  • the low-pressure stream 30, 40 introduced into the heat exchanger block 9 50 experiences no change in cross-section and no significant changes Current direction change.
  • the pressure drop across the heat exchanger block 9 is compared to the pressure drop across a conventional block, such as that shown in FIGS to 4 has been reduced by about 30%. Furthermore, the cost of the Heat exchanger block 9 reduced because of the elaborate lamella cuts for the distribution zones 39, 49, 59 can be dispensed with in FIGS. 2 to 4.
  • the new Heat exchanger blocks preferably only have a narrow distribution zone 73 am Entry and exit area of the heat exchange passages 33, 43, 53 are provided.
  • the lamellae in the narrow distribution zone 73 are parallel to the ones underneath or arranged above the fins of the heat exchange passages 33, 43, 53, but have a smaller distance from each other. That in collector 31, 41, 51 entering gas thus builds up easily in front of the distribution zone 73, causing a uniform distribution of the gas to all passages of the distribution zone 73 and thus on all heat exchange passages 33, 43, 53 is reached.
  • FIG. 6 shows a variant of the heat exchanger according to the invention.
  • the heat exchanger block 9 is identical to the block shown in FIG. 5. in the In contrast to FIG. 5, however, there are no individual collectors / distributors 31, 41, 51 or 32, 42, 52 provided, but a the entire end face of the Heat exchanger blocks 9 spanning common collector / distributor 71. Der Space between the end face of the heat exchanger block 9 and the Collector / distributor 71 is corresponding to areas 33, 43, 53 by separating plates 72 divided and each provided with a connecting piece.
  • FIGS. 7 and 8 show further embodiments of the invention.
  • This Heat exchangers are used for example in air separation processes, where the top section of the low pressure column has been omitted, so that no more low-pressure nitrogen 30 is generated in the low-pressure column. The As a result, low-pressure flows are reduced to impure nitrogen 40 and oxygen 50.
  • the main heat exchanger block 9 can thus be made simpler.
  • the Heat exchange passages for the low pressure streams 40, 50 are as in the FIGS. 7 and 8 shown, designed according to the invention, the pressure flows 10, 20, 60 are distributed over the corresponding zones in the usual way Heat exchange passages distributed.
  • the invention applies to all air separation processes in which at least two Low pressure flows occur, can be used with advantage.
  • Air separation process with air circulation or with nitrogen circulation.
  • FIG. 9 shows an example of a low-temperature air separation process with a single-turbine air circuit shown.
  • the feed air 10 is compressed and as High-pressure air flow 90 led into the skin heat exchanger.
  • Part 91 of the High pressure air is drawn from the heat exchanger at an intermediate point, relaxed and partly introduced into the pressure column, the other part 93 through the Heat exchanger 90 returned and added to the feed air 10 again.
  • the rest of the high-pressure air 90 is passed as a high-pressure stream 92 directly into the pressure column.
  • FIG. 10 shows an air separation process with a two-turbine air circuit and FIG. 12 the corresponding design of the main heat exchanger 9.
  • Die Heat exchange passages for the low pressure streams 30, 40, 50 run analogously to 11, the currents 101, 104 which are under higher pressure, 105, 106, as shown in FIG. 12, are passed through the heat exchanger.
EP02009896A 2002-01-18 2002-05-02 Echangeur de chaleur à plaques Expired - Lifetime EP1329680B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10201832 2002-01-18
DE10201832A DE10201832A1 (de) 2002-01-18 2002-01-18 Plattenwärmetauscher

Publications (2)

Publication Number Publication Date
EP1329680A1 true EP1329680A1 (fr) 2003-07-23
EP1329680B1 EP1329680B1 (fr) 2011-01-26

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EP02009896A Expired - Lifetime EP1329680B1 (fr) 2002-01-18 2002-05-02 Echangeur de chaleur à plaques

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Country Link
EP (1) EP1329680B1 (fr)
AT (1) ATE497138T1 (fr)
DE (2) DE10201832A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2645038A1 (fr) * 2012-03-29 2013-10-02 Linde Aktiengesellschaft Échangeur thermique à plaques avec plusieurs modules liés avec des profilés
EP2645037A1 (fr) * 2012-03-29 2013-10-02 Linde Aktiengesellschaft Échangeur thermique à plaques avec plusieurs modules liés par un ruban de tôle
WO2017074544A1 (fr) * 2015-10-27 2017-05-04 Praxair Technology, Inc. Système et procédé de fourniture de réfrigération à une unité de séparation cryogénique

Citations (5)

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US3282334A (en) * 1963-04-29 1966-11-01 Trane Co Heat exchanger
US3759322A (en) * 1970-10-01 1973-09-18 Linde Ag Heat exchanger
US4128410A (en) * 1974-02-25 1978-12-05 Gulf Oil Corporation Natural gas treatment
US5205351A (en) * 1991-04-03 1993-04-27 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Process for vaporizing a liquid, heat exchanger therefor, and application thereof to an apparatus for air distillation with a double column
US5979182A (en) * 1997-03-13 1999-11-09 Kabushiki Kaisha Kobe Seiko Sho Method of and apparatus for air separation

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3282334A (en) * 1963-04-29 1966-11-01 Trane Co Heat exchanger
US3759322A (en) * 1970-10-01 1973-09-18 Linde Ag Heat exchanger
US4128410A (en) * 1974-02-25 1978-12-05 Gulf Oil Corporation Natural gas treatment
US5205351A (en) * 1991-04-03 1993-04-27 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Process for vaporizing a liquid, heat exchanger therefor, and application thereof to an apparatus for air distillation with a double column
US5979182A (en) * 1997-03-13 1999-11-09 Kabushiki Kaisha Kobe Seiko Sho Method of and apparatus for air separation

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2645038A1 (fr) * 2012-03-29 2013-10-02 Linde Aktiengesellschaft Échangeur thermique à plaques avec plusieurs modules liés avec des profilés
EP2645037A1 (fr) * 2012-03-29 2013-10-02 Linde Aktiengesellschaft Échangeur thermique à plaques avec plusieurs modules liés par un ruban de tôle
CN103363823A (zh) * 2012-03-29 2013-10-23 林德股份公司 具有多个用型材连接的模块的板式热交换器
US9335102B2 (en) 2012-03-29 2016-05-10 Linde Aktiengesellschaft Plate heat exchanger with several modules connected by sheet-metal strips
CN103363823B (zh) * 2012-03-29 2017-03-01 林德股份公司 具有多个用型材连接的模块的板式热交换器
US10605536B2 (en) 2012-03-29 2020-03-31 Linde Aktiengesellschaft Plate heat exchanger with several modules connected by sections
WO2017074544A1 (fr) * 2015-10-27 2017-05-04 Praxair Technology, Inc. Système et procédé de fourniture de réfrigération à une unité de séparation cryogénique
US10295252B2 (en) 2015-10-27 2019-05-21 Praxair Technology, Inc. System and method for providing refrigeration to a cryogenic separation unit

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DE10201832A1 (de) 2003-07-31
EP1329680B1 (fr) 2011-01-26
DE50214880D1 (de) 2011-03-10
ATE497138T1 (de) 2011-02-15

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