US3559722A - Method and apparatus for two-phase heat exchange fluid distribution in plate-type heat exchangers - Google Patents

Method and apparatus for two-phase heat exchange fluid distribution in plate-type heat exchangers Download PDF

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US3559722A
US3559722A US858373A US3559722DA US3559722A US 3559722 A US3559722 A US 3559722A US 858373 A US858373 A US 858373A US 3559722D A US3559722D A US 3559722DA US 3559722 A US3559722 A US 3559722A
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passage
liquid
fluid
heat exchanger
heat exchange
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James J Schauls
Franklin D Duncan
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ALBRAZE INTERNATIONAL Inc
ALBRAZE INTERNATIONAL Inc A CORP OF WISCONSIN
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Trane Co
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Assigned to AMERICAN STANDARD INC., A CORP OF DE reassignment AMERICAN STANDARD INC., A CORP OF DE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/28/84 DELAWARE Assignors: A-S SALEM INC., A CORP. OF DE (MERGED INTO), TRANE COMPANY, THE
Assigned to TRANE COMPANY THE reassignment TRANE COMPANY THE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/1/83 WISCONSIN Assignors: A-S CAPITAL INC., A CORP OF DE (CHANGED TO), TRANE COMPANY THE, A CORP OF WI (INTO)
Assigned to A-S CAPITAL INC., A CORP OF DE reassignment A-S CAPITAL INC., A CORP OF DE MERGER (SEE DOCUMENT FOR DETAILS). Assignors: TRANE COMPANY THE A WI CORP
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Assigned to ALBRAZE INTERNATIONAL, INC., reassignment ALBRAZE INTERNATIONAL, INC., CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). EFFECTIVE NOV. 20, 1986 Assignors: ALTEC INTERNATIONAL, INC.
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    • 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
    • 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
    • F28D9/0062—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 the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0068—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 the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • 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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/104—Particular pattern of flow of the heat exchange media with parallel flow

Definitions

  • the liquid and the gas should be uniformly distributed to obtain maximum heat exchange with the third or other heat exchange fluids.
  • These problems have been partially solved by first separating the two-phase fluid into its constituent phases.
  • Various heat exchanger designs such as those shown in U.S. Pat. Nos. 3,282,334 and 3,310,105 both assigned to the assignee of this invention, have been directed to the problem of distributing the liquid phase uniformly among the vapor-liquid passages and distributing the gaseous phase uniformly among the vapor-liquid passages whereby each of the passages intended to conduct a vapor and liquid mixture receive the proper proportion of vapor and liquid.
  • the vapor and the liquid are mixed at the inlet to the vapor-liquid passage.
  • This invention solves the aforementioned problems by providing an entirely different method and apparatus for distributing gas and liquid in the passages of a plate-type heat exchanger intended to conduct a mixture of both fluid phases. More particularly this invention provides a means of uniformly distributing both the vapor and the liquid phases among the several passages of a heat exchanger and additionally provides a means of uniformly distributing the vapor and liquid phases across the width of each of the several passages. Because of superior distribution of the liquid and gaseous phases, it is possible to orient the heat exchanger for either upflow or downflow of liquid and to vary the mass flow rate of either the gas or the liquid fluid over a wide range without substantial reduction in heat exchanger etficiency.
  • this invention relates to a method of heat exchanging a first heat exchange fluid with a gaseous phase heat exchange fluid and a liquid phase heat exchange fluid including the steps of: providing a first supply of liquid phase heat exchange fluid; providing a second supply of gaseous phase heat exchange fluid; providing a third supply of a third heat exchange fluid; introducing the fluid of one of said phases into a first layer of a multilayer heat exchanger; distributing said introduced fluid of said one phase within said first layer substantially uniformly across the width of said heat exchanger; introducing the fluid of the other of said phases into a second layer adjacent said first layer; distributing said introduced fluid of said other phase within said second layer substantially uniformly substantially across the width of said heat exchanger; transferring the substantially uniformly distributed fluid of one of said phases from one of the first and second layers and diffusing it into the substantially uniformly distributed fluid of the other phase from the other of the first and second layers while substantially maintaining its uniform distribution substantially across the width of said heat exchanger whereby the gaseous and liquid phases are substantially uniformly combined substantially across the width of said
  • this invention further relates to a plate-type brazed heat exchanger comprising: first and second elongated metallic plates of generally similar peripheral configuration contraposed in face-to-face spaced relationship; first sealing means sealingly connecting said elongated metallic plates along the peripheral margins thereof thereby enclosing with said first and second elongated metallic plates a generally flat elongated plenum; a platelike partition interleaved with said first and second elongated metallic plates adjacent at least one end of said plenum and being coincidental with a plane spaced from said first and second elongated plates bisecting said plenum into first and second spacial layers; said partition extending transversely of the longitudinal axis of said elongated plenum to and in sealing connection with said first sealing means thereby defining within said first spacial layer a first passage intermediate said partition and said first elongated plate and within said second spacial layer a second passage intermediate said partition and said second elongated plate; said first sealing means defining a first in
  • FIG. 1 is a schematic of a gas separation system utilizing the heat exchange means of the instant invention.
  • FIG. 2 is a front elevation of a plate-type heat exchanger incorporating a first form of the invention.
  • FIG. 3 is a side elevation of the heat exchanger shown in FIG. 2.
  • FIG. 4 is a section taken at line 4-4 of FIG. 2.
  • FIG. 5 is a section taken at line 5-5 of FIG. 3.
  • FIG. 7 is a front elevation of a plate-type heat exchanger incorporating a second embodiment of the invention.
  • FIG. 8 is a side elevation of the heat exchanger shown in FIG. 7.
  • FIG. 10 is a section taken at line 10-10 of FIG. 8.
  • FIG. 1 1 is a section taken at line 1 1-1 1 of FIG. 8.
  • FIG. 12 is-a front elevation of a heat exchanger incorporating a third embodiment of the invention.
  • FIG. 13 is a side elevation of the heat exchanger shown in FIG. 12.
  • FIG. 14 is a section taken at line 14-14 of FIG. 12.
  • FIG. 15 is a section taken at line 15-15 of FIG. 14.
  • FIG. 16 is a section taken at line 16-16 of FIG. 14.
  • FIG. 17 is a partial section of the heat exchanger taken at line 17-17 ofFIG. 14.
  • FIG. 18 is a front elevation of a heat exchanger incorporating a fourth embodiment of the invention.
  • FIG. 19 is a side elevation of the heat exchanger shown in FIG. 18.
  • FIG. 20 is a vertical section of a portion of the heat exchanger taken along line 20-20 of FIG. 18.
  • FIG. 22 is a section taken along line 22-22 of FIG. 20.
  • FIG. 23 is a section of a portion of the heat exchanger taken along line 23-23 of FIG. 20.
  • a first 1 shows an exemplary system utilizing a heat exchanger employing the instant invention.
  • a gas feed such as air or natural gas under pressure is supplied to header 11.
  • the gas feed (See distributed by header 11 to certain passages within the heat exchanger 10.
  • the gas is cooled as it passes through these passages and a portion thereof is condensed.
  • the liquid and gaseous portions are discharged from these passages to a header 12.
  • the gas and liquid mixture is then conducted to a separator 13.
  • the liquid portion from separator 13 may be throttled to a lower pressure by throttling means 14 with the resulting vapor liquid mixture being passed to separator 15.
  • the gas from separator may be withdrawn from the system by way of a valve 16, or may be returned to the heat exchanger 10 via valve 17 and gas header 18 to recover its cold content.
  • the liquid fluid from separator 15 may be withdrawn from the system by way of valve 19 or alternatively returned to heat exchanger 10 via valve and liquid header 21.
  • the gas from header l8 and the liquid from header 21 are separately distributed uniformly within the passages across the width of head exchanger 10. After being so distributed within the core of heat exchanger 10, the gas and liquid phase fluids are combined to form a twophase fluid which is passed in heat exchange relation with the feed gas, and is discharged from the heat exchanger core via discharge header 22.
  • heavy dashed vectors represent gas flow
  • heavy solid vectors represent liquid flow
  • heavy dash-dot vectors represent the flow of a third heat exchange fluid which may be a liquid, gas, or liquid gas mixture.
  • heat exchanger 10 has a core 23 comprised of a plurality of rectangular impervious metallic plates 24 of the same peripheral configuration contraposed in face-to-face parallel spaced relationship. Disposed within each of the plenums formed intermediate adjacent plates 24, is a metallic platelike partition 25 interleaved with, parallel to, and spaced from metallic plates 24. Each partition 25 has substantially the same peripheral configuration, although not shown, as plates 24. Each partition 25 separates the plenum between adjacent plates 24 into first and second spacial layers 26 and 27 respectively.
  • FIG. 5 where the full width of one of layers 26 and the details therein can be viewed, it will be seen that a gap is provided at the lower end of layer 26 between the ends of bars 28 to thereby define a gas inlet 29 to a first passage, and that a second gap is provided at the upper portion of layer 26 between the ends of the bars 28 to form a fluid outlet 30 from the first passage.
  • a trapezoidal section 32 of corrugated metallic sheet fin material is disposed laterally of each fin section 31 and has crest extending diagonally as shown to provide a flow pattern between the inlet or outlet and the full width of the heat exchanger.
  • a small rectangular section 33 of corrugated metallic sheet fin material having crests extending horizontally is arranged immediately above the lower trapezoidal section 32. Section 33 must be porous as the gas passes the hard way therethrough and is accordingly tenned a hardway" fin section.
  • a large rectangular section 34 of corrugated metallic sheet fin material having crests extending vertically.
  • the partition 25 is provided with a slit 35 which extends horizontally across the width of the heat exchanger 10.
  • slit 35 defines a transfer passage for the transfer of liquid fluid from a second passage within an adjoining layer 27 into the gas stream passing through the first passage in layer 26.
  • Slit 35 may be formed simply by spacing two separate plates to form the partition 25.
  • slit 35 may be formed by cutting an elongated opening in a single piece partition. In either event, the ends of slit 35 may be formed adjacent the sides of heat exchanger 10 are closed to prevent external leakage.
  • a rectangular section 36 of corrugated metallic heavy guage fin material having crests extending vertically is disposed within layer 26 overlying partition 25 at both sides of slit 35.
  • Fin section 36 is brazed to partition 25"to provide the necessary structural continuity bridging slit 35.
  • this type fin we therefore refer to this type fin as a bridging fin.
  • Gas entering inlet 29 as illustrated by the heavy dashed vectors in FIGS. 4 and 5 is distributed across the width of the heat exchanger via lower fin sections 31, 32 and 33 in the lower portion of the heat exchanger.
  • the gas is mixed with liquid entering the first passage via transfer passage slit 35 as illustrated by the heavy solid vectors in FIGS. 4 and 5.
  • the liquid and gaseous fluids respectively uniformly distributed across the width of the heat exchanger and subsequently combined in intimate contact with each other then flow upwardly through the main fin section 34 of the first passage.
  • the fluid is then collected at the top of the heat exchanger and directed to the outlet 30 via upper fin sections 32 and 31 adjacent outlet 30 from whence it passes to header 22.
  • l-lardway" fin 33 in addition to serving as part of the gas distributing means also serves to reduce liquid flooding of the gas header 18.
  • FIG. 6 showing one of layers 27, it will be seen that the ends of bars 28 in layer 27 are spaced one from the other to thereby define a liquid inlet 37 in the lower portion of the heat exchanger, a fluid inlet 38 in the upper portion of the heat exchanger, and a fluid outlet 39 in the lower portion of the heat exchanger.
  • Inlets 37 and 38 and outlet 39 communicate respectively with headers 21, 11, and 12.
  • the space within layer 27 is sealingly bisected into second and third passages by a second sealing means in the form of a horizontally extending bar 40 which bridges between partition 25 and plate 24 as best seen in FIGS. 4 and 6.
  • Second triangular sections 42 of corrugated metallic sheet fin material having crests extending vertically are disposed intermediate each of fin sections 41 and a large rectangular section 43 of corrugated metallic sheet fin material also having crests extending vertically.
  • Fluid passing from header ll enters the third passage through inlet 38 and is distributed across the width of the heat exchanger via upper fin section 41 from whence it passes downwardly through upper triangular section 42, rectangular a section 43, and lower triangular section 42 where it is collected in lower fin section 41 and delivered from the third passage to header 12 via outlet 39.
  • This flow of fluid in the third passage is illustrated by the heavy dash-dot vectors in FIGS. 4 and 6.
  • the fluid is thus passed in counterfiow heat exchange relation with the fluid passing through the first passage in layer 26, the heat transfer taking place between layers 26 and 27 through metallic partition 25.
  • a rectangular section 46 of bridging fin similar to the bridging fin of section 36 is disposed immediately below bar 40 in layer 27 overlying and brazed to the area of partition 25 immediately adjacent slit 35.
  • Section 46 like section 36 is constructed from heavy guage corrugated metallic sheet fin material having crests extending vertically to thereby provide structural continuity in the area of slit 35.
  • hardway section 47 is porous to permit passage of fluid therethrough transversely of the crests thereof.
  • a portion of the fin sections has been removed to expose partition 25 and slit 35.
  • Liquid entering inlet 37 to the second passage from header 21 passes respectively through triangular section 44, triangular section 45, and hardway" section 47 and is thus uniformly distributed across the width of the heat exchanger in the second passage.
  • the liquid fluid passes along the bridging fin and is transferred from layer 27 to layer 26 through the slit 35 as herein before described. This flow of liquid in the second passage is illustrated by the heavy solid vectors.
  • each layer 27 at the lower end thereof provides means for distributing liquid uniformly across the width of the heat exchanger prior to being transferred into the gaseous stream of layer 26. Since the gas is uniformly distributed across the width of the heat exchanger in layer 26, and the liquid is uniformly distributed across the width of the heat exchanger in layer 27 there is no necessity to further distribute these fluids across the width of the heat exchanger after they are combined even if the relative proportions of combined liquid and gas are varied as aforementioned.
  • the flow vectors shown in FIG. 2 are a superimposed composite of the flow vectors of FIGS. 5 and 6 and illustrate the flow pattern for the aforedescribed heat exchange.
  • FIGS. 7 Now referring to the embodiment of the invention shown in FIGS. 7
  • heat exchanger 10a has a core 23 a comprised of a plurality of rectangular impervious metallic plates 24a of the same peripheral configuration contraposed in face-to-face parallel spaced relationship. Disposed within each of the plenums formed intermediate adjacent plates 24a, is a metallic platelike partition 25a interleaved with, parallel to, and spaced from metallic plates 240. Each partition 25a has substantially the same peripheral configuration, although not shown, as plates 24a. Each partition 25a separates the plenum between adjacent plates 24a into first and second spacial layers 26a and 27a respectively.
  • Bars 28a are sealingly bonded to the margins of plates 24a and partitions 250 by brazing. It should be appreciated that the sealing effect of bars 28a may be obtained by elements of other configuration such as channel members, rods, tubes, etc.
  • FIG. 10 where the full width of one of layers 26a and the details therein can be viewed, it will be seen that a gap is provided at the lower end of layer 260 between the ends of bars 28a to thereby define a liquid inlet 29a to a first passage, and that a second gap is provided at the upper portion of layer 26a between the ends of the bars 28a to form a fluid outlet 30a from the first passage.
  • a trapezoidal section 32a of corrugated metallic sheet fin material is disposed laterally of each fin section 31a having crests extending diagonally as shown to provide a flow pattern between the inlet or outlet and the full width of the heat exchanger.
  • a small rectangular section 33a of corrugated metallic sheet fin material having crests extending horizontally is arranged immediately above the lower trapezoidal section 32a. Section 33a must be porous as the liquid passes the hard way therethrough and is accordingly termed a hardway" fin section.
  • a large rectangular section 34a of corrugated metallic sheet fin material having crests extending vertically.
  • the partition 25a is provided with a slit 35a which extends horizontally across the width of the heat exchanger 10a.
  • a portion of the fin sections has been removed to expose partition 25a and slit 35a.
  • slit 35a defines a transfer passage for the transfer of gaseous fluid from a second passage within an adjoining layer 27a into the liquid stream passing through the first passage in layer 26a.
  • Slit 35a may be formed simply by spacing two separate plates to form the partition 25a.
  • slit 35a may be formed by cutting an elongated opening in a single piece partition.
  • a rectangular section 36a of corrugated metallic heavy guage sheet fin material having crests extending vertically is disposed within layer 26a overlying partition 25a at both sides of slit 35a.
  • Fin section 36a is brazed to partition 25a to provide the necessary structural continuity bridging slit 350. We therefore refer to this type fin as a bridging fin.
  • Liquid entering inlet 29a to the first passage from header 21a as illustrated by the heavy solid vectors in FIGS. 9 and 10 is distributed across the width of the heat exchanger via lower fin sections 31a and 32a and 33a in the lower portion of the heat exchanger. After having been uniformly distributed across the width of the heat exchanger, the liquid is mixed with gas entering the first passage via transfer passage slit 35a as illustrated by the heavy clashed vectors in FIGS. 9 and 10.
  • FIG. 11 showing layer 27a
  • the ends of bars 28a in layer 27a are spaced one from the other to thereby define a gas inlet 37a at the lower portion of the heat exchanger, a fluid inlet 38a in the upper portion of the heat exchanger, and a fluid outlet 39a in the lower portion of the heat exchanger.
  • Inlets 37a and 38a and outlet 39a communicate respectively with headers 18a, Ila and 12a.
  • the space within layer 27a is sealingly bisected into second and third passages by a second sealing means in the form of a horizontally extending bar 40a which bridges between partition 25a and plate 240 as best seen in FIGS. 9 and 11.
  • the space within layer 27a above bar 400 i.e..
  • a second triangular section 42a of corrugated metallic sheet fin material having crests extending vertically is disposed intermediate each of fin sections 41a and a large rectangular section 43a of corrugated metallic sheet fin material also having crests extending vertically.
  • Fluid passing from header 11a enters the third passage through inlet 38a and is distributed across the width of the heat exchanger via upper fin section 41a, from whence it passes downwardly through upper triangular section 424, rectangular section 43a, and lower triangular section 42a where it is collected in lower fin section 41:: and delivered from the third passage to header 120 via outlet 390.
  • This flow of fluid in the third passage is illustrated by the heavy dash-dot vectors in FIGS. 9 and 11. The fluid is thus passed in head exchange relation with the fluid passing through the first passage in layer 26a, the heat transfer taking place between layers 26a and 27a through metallic partition 25a.
  • second triangular section 450 of corrugated metallic sheet fin material having crests extending vertically.
  • triangular section 450 is a rectangular hardway fin section 47a of corrugated metallic sheet fin having crests extending horizontally.
  • hardway section 47a is porous to permit passage of gas therethrough transversely of the crests thereof.
  • a rectangular section 460 of bridging fin similar to bridging fin 36a is disposed immediately below hardway" section 47a in layer 27a overlying and brazed to the area of separator 25:: immediately adjacent slit 350.
  • Section 46a like section 36a is constructed from a heavy sheet of corrugated sheet fin material having crests extending vertically to thereby provide structural continuity in the area of slit 35a.
  • a portion of the fin sections has been removed to expose partition 25a and slit 350.
  • Gas entering inlet 37a to the second passage from header 18a passes respectively through triangular section 440, downwardly through triangular section 45a, and hardway section 47a and is thus uniformly distributed across the width of the heat exchanger in the second passage. After having been thus distributed across the width of the heat exchanger, the gas passes along the bridging fin 460' and is transferred from layer 27a to layer 26a through the slit 35a as herein before described. This flow of gas in the second passage is illustrated by the heavy dashed vectors.
  • each layer 270 at the lower end thereof provides means for distributing gas across the width of the heat exchanger prior to being transferred into the liquid stream of layer 26a.
  • the flow Vectors shown in FIG. 7 are a superimposed composite of the flow vectors of FIGS. 10 and 11 and illustrate the flow pattern for the aforedescribed heat exchange. It should be noted that in the embodiment of FIGS. 7 through 11, it is the gas stream that passes through the transfer passage slit 35a in the partition 25a.
  • the gas inlet 37a is disposed vertically intermediate bar 40a and slit 35a, the gas is first caused to pass downwardly in layer 27a before passing upwardly in layer 26a.
  • the downward course of the gas flow in layer 27a provides an effective means of preventing liquid under low flow conditions from backing up into the gas supply.
  • heat exchanger 10b has a core 23b comprised of a plurality of rectangular impervious metallic plates 24b of the same peripheral configuration contraposed in face-to-face parallel spaced relationship. Disposed within the lower portion-of each of the plenums formed intermediate certain pairs of adjacent plates 24b, is a rectangular metallic platelike partition 25b interleaved with, parallel to, and spaced from metallic plates 24b. Partitions 24b have a vertical extent as shown in FIG. 14 and a horizontal extent equal to plates 24b. A portion of the fin material has been removed in FIG. 16 to directly expose a portion of the face of one of partitions 25b. Each partition 25b separates the lower portion of its respective plenum into first and second spacial layers 26b and 27b respectively.
  • a series of closing bars 28b sealingly bridging between each partition 25b and the adjacent plates 24b along the margins thereof at the lower portion of plates 24b in each of the layers 26b and 27b and between adjacent plates 24b along the margins thereof at the upper portion of plates 24b bound the plenums between said certain pairs of adjacent plates 24b.
  • Bars 281; are sealingly bonded to the margins of plates 24b and partitions 25b by brazing. It should be appreciated that the sealing effect of bars 28b may be obtained by elements of other configurations such as channel members, rods, tubes, and etc.
  • FIG. 16 where the full width of one of layers 26b and the details herein can be viewed, it will be seen that a gap is provided at the lower end of layer 26b between the ends of bars 28b to thereby define a gas inlet 29b to a first passage, and that a second gap is provided at the upper portion of said plenum between the ends of bars 28b to form a fluid outlet 30b from the first passage.
  • a substantially triangular section 31b of corrugated metallic sheet fin material having crests extending vertically.
  • Disposed adjacent outlet 30b is a substantially triangular section of corrugated sheet fin 31b having its crests extending vertically.
  • a trapezoidal section 32b of corrugated metallic sheet fin material is disposed laterally of fin section 31b having crests extending diagonally as shown to provide a flow pattern from inlet 29b to the full width of the heat exchanger.
  • a trapezoidal section 32b of corrugated metallic sheet fin material is disposed laterally of fin section 31b having crests extending diagonally as shown to provide a flow pattern from the full width of the heat exchanger to outlet 30b.
  • a small rectangular section 33b of corrugated metallicsheet fin material having its crests extending horizontally is arranged immediately above trapezoidal section 32b.
  • Section 33b must be porous as the fluid passes the hardway therethrough and'is accordingly termed a hardway" fin section.
  • Intermediate hardway fin section 33b and trapezoidal fin section 32b is a large rectangular section 34b of corrugated metallic sheet fin material having its crests extending vertically.
  • fin sections 31b, 32b and 34b are sufficiently thick as to bridge between spaced plates 24b whereas fin sections 33b, 31b and 32b are sufi'iciently thick as to bridge only between a plate 24b and a partition 25b.
  • Gas entering inlet 29b from header 18b as illustrated by the heavy dashed vectors in FIGS. 14 and 16 is distributed across the width of the heat exchanger via lower fin sections 31b, 32b, and 33b. After the gas has been completely distributed across the width of the heat exchanger by passing through fin sections 31b, 32b, and 33b, it passes beyond the upper edge of partition 25b into fin section 34b where it is combined with liquid, as illustrated by the heavy solid vectors in FIGS. 14, 16, and 17, entering the fin section 34b in a manner hereinafter described in connection with layer 26b.
  • the liquid and gaseous fluids respectively uniformly distributed across the width of the heat exchanger and subsequently combined in intimate contact with each other then flow upwardly through the main fin section 34b of the first passage. The fluid is then collected at the top of the heat exchanger and directed to the outlet 30b via upper fin sections 32b and 31b adjacent outlet 30b from whence it passes to header 22b.
  • FIG. 17 showing one of layers 27b
  • the ends of bars 28b in layer 27b are spaced one from the other to thereby define a liquid inlet 37b, to a second passage which communicates with header 21b of heat exchanger b.
  • a first triangular section 44b of corrugated metallic sheet fin material having crests extending horizontally.
  • a second triangular section 45b of corrugated metallic sheet fin material is disposed immediately above section 44b also having crests extending vertically.
  • a rectangular hardway section 47b of corrugated metallic sheet fin material having crests extending horizontally.
  • hardway section 47b is porous to permit passage of fluid therethrough transversely of the crests thereof.
  • Liquid entering inlet 37b from header 21b passes respectively through triangular section 44 b, triangular section 45b, and hardway" section 47b and is thus uniformly. distributed across the width of the heat exchanger in the second passage. After thus being distributed across the width of the heat exchanger, the liquid fluid passes vertically beyond the upper edge of partition 25b where it intimately mixes with the gas within fin section 34b of the first passage.
  • a transfer passage is formed as both layers 26b and 27b become a common layer above the upper edge of partition 25b.
  • the gas flowing within the first passage of layer 26b and the liquid flowing within the second passage of layer 27b are separately substantially uniformly distributed across the width of the heat exchanger prior to their combination, and that there is no necessity for further distribution of these fluids across the width of the heat exchanger after being so combined.
  • the combined fluids flowing in section 34b i.e., the upper portion of the first passage, are heat exchanged with a third heat exchange fluid flowing in a third passage of an ad jacent layer 50b as illustrated by the heavy dot-dash vectors of FIG. 15.
  • the third passage is formed by certain other adjacent metallic plates 24b and closing bars 28b bridging therebetween along the margins thereof. It will be seen that the ends of bars 28b within layer 50b are spaced to define a fluid inlet 38b at the upper portion of the heat exchanger and a fluid outlet 39b at the lower portion of the heat exchanger arranged to communicate respectively with headers 11b and 12b. Disposed within the space of layer 50b adjacent each inlet 38b and outlet 39b is a substantially triangular section 41b of corrugated metallic sheet fin material having crests extending vertically.
  • a trapezoidal section 42b of corrugated metallic sheet fin material is disposed laterally of each of fin sections 41b and has crests extending diagonally as shown to provide a flow pattern between the inlet or outlet and the full width of the heat exchanger.
  • Intermediate trapezoidal sections 42b is a large rectangular section 43b of corrugated metallic sheet fin material which forms the main packing for the third passage within layer 50b.
  • the fluid to be heat exchanged with the aforementioned gaseous and liquid fluids enters the third passage via header 1 lb, inlet38b and is distributed across the width of the heat exchanger by upper triangular section 41b and upper trapezoidal section 42b whereupon it moves downwardly through rectangular section 43b from which it is directed via lower trapezoidal section 42b and lower triangular section 41b to outlet 39b into header 12b.
  • two-phase mixture fluid passing through the first passages is heat exchanged via plates 24b with the third fluid passing through the third passage within layer 50b.
  • means is provided intermediate plates 24b for independent distribution of both the liquid and gaseous phases uniformly across the full width of the heat exchanger prior to their mixture. Since the gas is uniformly distributed across the width of the heat exchanger in layer 26b, and the liquid is uniformly distributed across the width of the heat exchanger in layer 27b there is no necessity to further distribute these fluids across the width of the heat exchanger after they are combined even if the relative proportions of combined liquid and gas varied as aforementioned.
  • the flow vectors shown in FIG. 12 are a superimposed composite of the flow vectors of FIGS. 15, 16, and I7 and illustrate the flow pattern for the aforedescribed heat exchange.
  • heat exchanger 10c has a core 230 comprised of a plurality of rectangular impervious metallic plates 24c of the same peripheral configuration contraposed in face-to-face parallel spaced relationship. Disposed within each of the plenums formed intermediate certain adjacent plates 24c, is a pair of rectangular metallic platelike partitions 25c interleaved with, parallel to, and spaced from the lower portions of metallic plates 240. Intermediate the planes of adjacent partitions 25c immediately above partitions 250 is a third rectangular metallic platelike partition 25c interleaved with, parallel to, and spaced from the upper portions of said certain plates 24c.
  • Partition 250 has a vertical extent as shown in FIG. 20 and a horizontal extent equal to that of plates 24c. Portions of the fin material have been removed in FIGS. 22 and 23 to directly expose portions of the faces of partitions 25c and 250'.
  • Each pair of partitions 25c separates the lower portion of the plenum between said certain adjacent plates 24c into a pair of spaced spacial layers 26c and an intermediate spacial layer 270 shown in FIGS. 22 and 23 respectively.
  • Each partition 25c separates the upper portion of the plenum between said certain adjacent plates 24c into two identical spacial layers 260' shown in FIGS. 20 and 22.
  • Each layer 26c is somewhat narrower than but coextensive and in fluid communication with a layer 26c.
  • Layer 26c may be considered as a thickened extension of layer 260.
  • Layer 27c is coextensive and in communication with two adjacent layers 26c.
  • a series of closing bars 280 sealingly bridging between each partition 25c and the lower portion of adjacent plates 24c along the margins thereof in each of layers 26c, between partitions 250' along the lower and side margins thereof in layer 27c, bound each plenum between said certain adjacent pairs of plates 24c.
  • Bars 270 are sealingly bonded to the margins of plates 24c and partitions 25c and 250 by brazing. It should be appreciated that the sealing effect of bars 280 may be obtained by elements of other configurations such as channel members, rods, tubes, etc.
  • a gap is provided between the ends of bars 280 at the lower end of the layer 26c to thereby define a gaseous fluid inlet 29c to a first passage, and that a second gap is provided between the ends of bars 28c at the upper portion of the first passage in layer 261: to form a fluid outlet 30c from said first passage.
  • Disposed adjacent inlet 29c is a substantially triangular section 31c of corrugated metallic sheet fin material having crests extending vertically.
  • Disposed adjacent outlet 30c is a substantially triangular section 31c of corrugated metallic sheet fin material having crests extending vertically.
  • a trapezoidal section 32c of corrugated metallic sheet fin material is disposed laterally of fin section 3Ic having crests extending diagonally as shown to provide a flow pattern from inlet 29c to the full width of the heat exchanger.
  • a trapezoidal section 32c of corrugated metallic sheet fin material is disposed laterally of fin section 31c having the crests extending diagonally as shown to provide a flow pattern from the full width of the heat exchanger to outlet 30c.
  • a small rectangular section 33c of corrugated metallic sheet fin material having crests extending horizontally is arranged immediately about trapezoidal section 320. Section 33c must be porous as the gas passes the hard way therethrough and is accordingly termed a hardway fin section.
  • Intermediate hardway fin section 33c and the trapezoidal fin section 32c is a large rectangular section 34c of corrugated metallic sheet fin material having crests extending vertically. It should be noted that the fin sections 31c, 32c and 34c are sufficiently thick as to bridge between a partition 25c and the adjacent plate 240 and that fin sections 31c, 32c, and 330 are sufiiciently thick as to bridge between partition 25c and adjacent plate 24c.
  • the fluid is then collected at the top of the heat exchanger and directed to the outlet 300 via upper fin sections 32c and 31c adjacent outlet 300 from whence it passes to header 220.
  • FIG. 23 showing layer 27c, it will be seen that the ends of bars 280 of layer 270 are spaced one from the other to thereby define a liquid inlet 37c to a second passage which communicates with header 21c of heat exchanger c.
  • a first triangular section 440 of corrugated metallic sheet fin material having crests extending horizontally.
  • a second triangular section 45c of corrugated metallic sheet fin material is disposed immediately above section 44c having crests extending vertically.
  • a rectangular hardway" section 47c of corrugated metallic sheet fin material having crests extending horizontally.
  • hardwayi' section 47c is porous to permit passage of liquid therethrough transversely of the crests thereof.
  • Liquid entering inlet 37c to the second passage from header 21c passes respectively through triangular section 44c, triangular section 45c, and "hardway section 47c and is thus uniformly distributed across the width of the heat exchanger. After thus being distributed across the width of the heat exchanger in the second passage, the liquid fluid passes vertically beyond the upper edge of partition 250 where the liquid intimately mixes with the gaseous fluid in the first passage at fin sections 34c aforedescribed.
  • no discrete slit or gap is provided within partition 25c.
  • a transfer passage is formed as both layers 26c and 27c become a common layer 26c above the upper edge of partition 25c. It will be seen that the gas flowing within layer 26c and the liquid flowing within layer 27c are separately substantially uniformly distributed across the width of the heat exchanger prior to their combination, and that there is no necessity for further distribution of these fluids across the width of the heat exchanger after being so combined.
  • the combined fluids flowing in section 34c i.e., the upper portion of the first passage, are heat exchanged with a third heat exchange fluid flowing in a third passage of an adjacent layer 500 via plates 24c as illustrated by the heavy dot-dash vectors of FIG. 21.
  • the third passage is formed by certain other adjacent metallic plates 24c and closing bars 28c bridging therebetween along the margins thereof. It will be seen that the ends of bars 28c within layer 50c are spaced to define a fluid inlet 38c at the upper portion of the heat exchanger and a fluid outlet 39c at the lower portion of the heat exchanger arranged to communicate respectively with headers 11c and 12c. Disposed within the space of layer 50c adjacent inlet 38c and outlet 390 is a substantially triangular section 41c of corrugated metallic sheet fin material having crests extending vertically.
  • a trapezoidal section 42c of corrugated metallic sheet fin material is disposed laterally of each of fin sections 41c and has crests extending diagonally as shown to provide a flow pattern between the inlet or outlet and the full width of the heat exchanger.
  • Intermediate trapezoidal sections 42c is a large rectangular section 43c of corrugated metallic sheet fin material which forms the main packing for layer 50c.
  • the third fluid to be heat exchanged with the aforementioned gaseous and liquid fluids enters the third passage in layer 50c via the header 1 1c, inlet 38c and is distributed as illustrated by the dot-dash vectors in FIG.
  • the flow vectors shown in FIG. 18 are a superimposed composite of the flow vectors of FIGS. 21, 22 and 23 and illustrate the flow pattern for the aforedescribed heat exchange.
  • FIGS. 9, 10 and 11 of U.S. Pat. No. 3,282,334 for a more comprehensive illustration of the types of material utilized in the corrugated metallic sheet fin sections for the heat exchanger embodiments disclosed herein.
  • numerals 11, 12, 18, 21, and 22 will become respectively: 110, 12a, 18a, 21a, and 22a; 11b, 12b, 18b, 21b, and 22b, and 110, 12c, 18c, 21c, and 220.
  • Their operation within the system of FIG. 1 is similar to that of the first embodiment.
  • a plate-type heatexchanger apparatus comprising: first and second elongated metallic plates of generally similar peripheral configuration contraposed in face-to-face spaced relationship; first sealing means sealingly connecting said elongated metallic plates along the peripheral margins thereof thereby enclosing with said first and second elongated metallic plates a generally flat elongated plenum; a platelike partition interleaved with said first and second elongated metallic plates adjacent at least one end of said plenum and being generally coincident with a plane spaced from said first and second elongated metallic plates bisecting said plenum at said one end into first and second spacial layers; said partition extending transversely of the longitudinal axis of said elongated plenum substantially to said first sealing means thereby defining within one of said spacial layers a first passage intermediate said partition and said first elongated metallic plate and within the other of said spacial layer a second a passage intermediate said partition and said second elongated plate; said first sealing means defining a first inlet
  • the apparatus as defined by claim 1 including a third elongated metallic plate of generally similar peripheral configuration to said first and second elongated metallic plates contraposed in face-to-face spaced relationship with said second elongated metallic plate externally of said plenum; said first sealing means further sealingly connecting said second and third elongated metallic plates along the peripheral margins thereof whereby said third passage is defined therebetween; said first sealing means defining an inlet and an outlet respectively to and from said third passage.
  • a method of heat exchange including the steps of: providing a supply of gaseous phase heat exchange fluid; providing a supply of liquid phase heat exchange fluid; introducing the fluid of one of said phases into a first layer of a multilayer heat exchanger; distributing said introduced fluid of said one phase within said first layer substantially uniformly substantially across the width of said heat exchanger; passing the substantially uniformly distributed fluid of said one phase through the remainder of said first layer; simultaneously introducing the fluid of the other of said phases into a second layer adjacent said first layer; distributing said introduced fluid of said other phase within said second layer substantially uniformly substantially across the width of said heat exchanger; and transferring the substantially uniformly distributed fluid of said other phase from said second layer to said first layer while substantially maintaining its uniform distribution substantially across the width of said heat exchanger whereby the gaseous and liquid phases are substantially uniformly combined substantially across the width of a heat exchanger independently of their relative mass flows.
  • a method of heat exchanging a first heat exchange fluid with a gaseous phase heat exchange fluid and liquid phase heat exchange fluid including the steps of: providing a first supply of liquid phase heat exchange fluid; providing a second supply of gaseous phase heat exchange fluid; providing a third supply of a third heat exchange fluid; introducing the fluid of one of said phases into a first layer of a multilayer heat exchanger; distributing said introduced fluid of said one phase within said first layer substantially uniformly substantially across the width of said heat exchanger; introducing the fluid of the other of said phases into a second layer adjacent said first layer; distributing said introduced fluid of said other phase within said second layer substantially uniformly substantially across the width of said heat exchanger; transferring the substantially uniformly distributed fluid of one of said phases from one of the first and second layers and diffusing it into the substantially uniformly distributed fluid of the other phase from the other of the first and second layers while substantially maintaining its uniform distribution substantially across the width of said heat exchanger whereby the gaseous and liquid phases a are substantially uniformly combined substantially across the width of a heat exchanger independently
  • a method of operating a plate-type heat exchanger having a plurality of substantially parallel spaced plates defining therebetween a plurality of relatively thin but wide passages including the steps of: passing a gas into a first of said relatively thin but wide passages formed by said plates; spreading said gas out in said first passage over substantially the full width of said plates forming said first passage; passing a liquid into a second of said relatively thin but wide passages formed by said plates; spreading said liquid out in said second passage over substantially the full width of said plates forming said second pasage; passing the thus spread gaseous and liquid fluids in substantially a common direction within their respective passages and passing one of said gaseous and liquid fluids beyond an edge of one of said plates forming one of a said first and second passages into the other of said gaseous and liquid fluids in the other of said passages for uniform intimate mixing of the gaseous and liquid fluids across the full width of said other passage; and passing the resulting mixture of gas and liquid in heat exchange relation via one of said plates with a third heat exchange fluid.
  • a method of operating a plate-type heat exchanger having a plurality of substantially parallel spaced plates defining therebetween a plurality of relatively thin but wide passages including the steps of: passing a gas into a first of said relatively thin but wide passages formed by said plates; spreading said gas out in said first passage over substantially the full width of said plates forming said first passage; passing a liquid into a second of said relatively thin but wide passages formed by said plates; spreading a said liquid out in said second passage over substantially the full width of said plates forming said second pasage; passing the thus spread gaseous and liquid fluids in substantially opposite directions within their respective passages and passing one of said gaseous and liquid fluids beyond an edge of one of said plates forming one of said first and second passages into the other of said gaseous and liquid fluids in the other of said'passages for uniform intimate mixing of the gaseous and liquid fluids across the full width of said other passage; and passing the resulting mixture of gas and liquid in heat exchange relation via one of said plates with a third heat exchange fluid.
  • a plate-type heat exchanger comprising: a plurality of substantially parallel closely spaced plates defining therebetween a plurality of relatively thin but wide passages;
  • one of said plates being common to a first and second passage adjacent to each other; said one plate having an edge in fluid communication with each of said first and second passages; said first passage having a gas inlet; means within said first passage downstream of said edge for distributing gas entering said gas inlet uniformly across the width of said first passage; said second passage having a liquid inlet; means within, said second passage downstream of said edge for distributing liquid entering said liquid inlet uniformly across the width of said second passage whereby said gaseous and liquid fluids are uniformly mixed as they pass beyond said edge of said one plate; and a third passage for conducting a third heat exchange fluid in heat exchange relation with the mixture of gas and liquid fluids.
  • the apparatus as defined by claim 29 including a second plate having a peripheral edge parallel to and spaced from said first edge, the space between said edges conducting one of said gaseous and liquid fluids into the other of said gaseous and liquid fluids.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US858373A 1969-09-16 1969-09-16 Method and apparatus for two-phase heat exchange fluid distribution in plate-type heat exchangers Expired - Lifetime US3559722A (en)

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Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2248273A1 (de) * 1971-10-01 1973-04-05 Air Liquide Waermeaustauscher und verfahren zu dessen anwendung
US3860065A (en) * 1970-04-08 1975-01-14 Trane Co Distributor for plate type heat exchanger having side headers
DE2521279A1 (de) * 1974-05-24 1975-12-04 Borg Warner Waermetauscherplatte
US3992168A (en) * 1968-05-20 1976-11-16 Kobe Steel Ltd. Heat exchanger with rectification effect
US4249595A (en) * 1979-09-07 1981-02-10 The Trane Company Plate type heat exchanger with bar means for flow control and structural support
EP0074740A3 (en) * 1981-09-11 1983-06-29 Raymond James Pollard Fluid flow apparatus and core elements therefor
US4450903A (en) * 1982-09-20 1984-05-29 The Trane Company Plate type heat exchanger with transverse hollow slotted bar
US4646822A (en) * 1984-04-27 1987-03-03 Linde Aktiengesellschaft Heat exchanger
US4763488A (en) * 1980-05-26 1988-08-16 University Of Sydney Plate heat exchanger for separating vapor and liquid phases
WO1989010172A1 (en) * 1988-04-27 1989-11-02 Rosenblad Axel E Selective condensation apparatus
US5410885A (en) * 1993-08-09 1995-05-02 Smolarek; James Cryogenic rectification system for lower pressure operation
FR2718835A1 (fr) * 1994-04-15 1995-10-20 Nordon Cryogenie Snc Echangeur de chaleur à plaques brasées.
FR2718836A1 (fr) * 1994-04-15 1995-10-20 Grenier Maurice Echangeur de chaleur perfectionné à plaques brasées.
EP0723125A2 (en) 1994-12-09 1996-07-24 Kabushiki Kaisha Kobe Seiko Sho Gas liquefying method and heat exchanger used in gas liquefying method
US6044902A (en) * 1997-08-20 2000-04-04 Praxair Technology, Inc. Heat exchange unit for a cryogenic air separation system
WO2003100338A1 (en) * 2002-05-29 2003-12-04 Alfa Laval Corporate Ab A plate heat exchanger device and a heat exchanger plate
US20050045312A1 (en) * 2003-08-28 2005-03-03 Jibb Richard J. Heat exchanger distributor for multicomponent heat exchange fluid
US6935417B1 (en) * 1998-10-19 2005-08-30 Ebara Corporation Solution heat exchanger for absorption refrigerating machine
US20070007120A1 (en) * 2005-07-11 2007-01-11 Taylor William P Desalinator
US20070289726A1 (en) * 2006-06-19 2007-12-20 Richard John Jibb Plate-fin heat exchanger having application to air separation
US20100064724A1 (en) * 2008-09-18 2010-03-18 Multistack Llc Flooded plate heat exchanger
CN104896978A (zh) * 2015-05-15 2015-09-09 兰州兰石集团有限公司 一种新型三介质复合热交换器
US9279626B2 (en) * 2012-01-23 2016-03-08 Honeywell International Inc. Plate-fin heat exchanger with a porous blocker bar
CN106288927A (zh) * 2016-09-21 2017-01-04 天津商业大学 一种均匀分配板翅式换热器导流片
US20170138588A1 (en) * 2015-11-18 2017-05-18 Bosal Emission Control Systems Nv Combined evalporator and mixer
US20210041164A1 (en) * 2018-03-13 2021-02-11 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Reliquefaction device
US11022377B2 (en) * 2016-07-01 2021-06-01 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger comprising a device for distributing a liquid/gas mixture
US11221178B2 (en) * 2017-03-24 2022-01-11 L'air Liquide, Société Anonyme Pour L'etude Et L'exploitation Des Precédés Georges Claude Heat exchanger with liquid/gas mixer device having openings with an improved shape
US11365942B2 (en) * 2018-03-16 2022-06-21 Hamilton Sundstrand Corporation Integral heat exchanger mounts
CN115420131A (zh) * 2022-09-21 2022-12-02 西安电子科技大学 一种中心差分式换热器及其换热性能检测装置

Families Citing this family (2)

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FR2499226B1 (fr) * 1981-02-05 1985-09-27 Air Liquide Procede et installation de liquefaction d'un gaz
CN114909831B (zh) * 2021-02-08 2024-06-14 广东美的暖通设备有限公司 换热器、电控盒及空调系统

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2008887B1 (enrdf_load_stackoverflow) * 1968-05-20 1973-12-07 Kobe Steel Ltd

Cited By (46)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992168A (en) * 1968-05-20 1976-11-16 Kobe Steel Ltd. Heat exchanger with rectification effect
US3860065A (en) * 1970-04-08 1975-01-14 Trane Co Distributor for plate type heat exchanger having side headers
DE2248273A1 (de) * 1971-10-01 1973-04-05 Air Liquide Waermeaustauscher und verfahren zu dessen anwendung
US3880231A (en) * 1971-10-01 1975-04-29 Air Liquide Heat-exchanger and method for its utilization
DE2521279A1 (de) * 1974-05-24 1975-12-04 Borg Warner Waermetauscherplatte
US4249595A (en) * 1979-09-07 1981-02-10 The Trane Company Plate type heat exchanger with bar means for flow control and structural support
US4763488A (en) * 1980-05-26 1988-08-16 University Of Sydney Plate heat exchanger for separating vapor and liquid phases
EP0074740A3 (en) * 1981-09-11 1983-06-29 Raymond James Pollard Fluid flow apparatus and core elements therefor
US4450903A (en) * 1982-09-20 1984-05-29 The Trane Company Plate type heat exchanger with transverse hollow slotted bar
US4646822A (en) * 1984-04-27 1987-03-03 Linde Aktiengesellschaft Heat exchanger
WO1989010172A1 (en) * 1988-04-27 1989-11-02 Rosenblad Axel E Selective condensation apparatus
US4878535A (en) * 1988-04-27 1989-11-07 Rosenblad Corporation Selective condensation apparatus
US5410885A (en) * 1993-08-09 1995-05-02 Smolarek; James Cryogenic rectification system for lower pressure operation
FR2718835A1 (fr) * 1994-04-15 1995-10-20 Nordon Cryogenie Snc Echangeur de chaleur à plaques brasées.
FR2718836A1 (fr) * 1994-04-15 1995-10-20 Grenier Maurice Echangeur de chaleur perfectionné à plaques brasées.
WO1995028610A1 (en) * 1994-04-15 1995-10-26 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Improved heat exchanger with brazed plates
US5787975A (en) * 1994-04-15 1998-08-04 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger with brazed plates
US5857517A (en) * 1994-04-15 1999-01-12 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger with brazed plates
US5904205A (en) * 1994-04-15 1999-05-18 L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger with brazed plates
CN1119618C (zh) * 1994-04-15 2003-08-27 液体空气乔治洛德方法利用和研究的具有监督和管理委员会的有限公司 带钎焊板的热交换器及包括这种热交换器的空气蒸馏装置
EP0723125A2 (en) 1994-12-09 1996-07-24 Kabushiki Kaisha Kobe Seiko Sho Gas liquefying method and heat exchanger used in gas liquefying method
US6044902A (en) * 1997-08-20 2000-04-04 Praxair Technology, Inc. Heat exchange unit for a cryogenic air separation system
US6935417B1 (en) * 1998-10-19 2005-08-30 Ebara Corporation Solution heat exchanger for absorption refrigerating machine
WO2003100338A1 (en) * 2002-05-29 2003-12-04 Alfa Laval Corporate Ab A plate heat exchanger device and a heat exchanger plate
US20050211421A1 (en) * 2002-05-29 2005-09-29 Rolf Ekelund Plate heat exchanger device and a heat exchanger plate
US7669643B2 (en) 2002-05-29 2010-03-02 Alfa Laval Corporate Ab Plate heat exchanger device and a heat exchanger plate
US7163051B2 (en) * 2003-08-28 2007-01-16 Praxair Technology, Inc. Heat exchanger distributor for multicomponent heat exchange fluid
US20050045312A1 (en) * 2003-08-28 2005-03-03 Jibb Richard J. Heat exchanger distributor for multicomponent heat exchange fluid
US20070007120A1 (en) * 2005-07-11 2007-01-11 Taylor William P Desalinator
US20070289726A1 (en) * 2006-06-19 2007-12-20 Richard John Jibb Plate-fin heat exchanger having application to air separation
US7779899B2 (en) * 2006-06-19 2010-08-24 Praxair Technology, Inc. Plate-fin heat exchanger having application to air separation
US20100064724A1 (en) * 2008-09-18 2010-03-18 Multistack Llc Flooded plate heat exchanger
US9279626B2 (en) * 2012-01-23 2016-03-08 Honeywell International Inc. Plate-fin heat exchanger with a porous blocker bar
CN104896978B (zh) * 2015-05-15 2016-10-05 兰州兰石集团有限公司 一种三介质复合热交换器
CN104896978A (zh) * 2015-05-15 2015-09-09 兰州兰石集团有限公司 一种新型三介质复合热交换器
US20170138588A1 (en) * 2015-11-18 2017-05-18 Bosal Emission Control Systems Nv Combined evalporator and mixer
US10465902B2 (en) * 2015-11-18 2019-11-05 Bosal Emission Control Systems Nv Combined evaporator and mixer
US11022377B2 (en) * 2016-07-01 2021-06-01 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Heat exchanger comprising a device for distributing a liquid/gas mixture
CN106288927A (zh) * 2016-09-21 2017-01-04 天津商业大学 一种均匀分配板翅式换热器导流片
US11221178B2 (en) * 2017-03-24 2022-01-11 L'air Liquide, Société Anonyme Pour L'etude Et L'exploitation Des Precédés Georges Claude Heat exchanger with liquid/gas mixer device having openings with an improved shape
US20210041164A1 (en) * 2018-03-13 2021-02-11 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Reliquefaction device
US11754337B2 (en) * 2018-03-13 2023-09-12 Kobe Steel, Ltd. Reliquefaction device
US11365942B2 (en) * 2018-03-16 2022-06-21 Hamilton Sundstrand Corporation Integral heat exchanger mounts
US11740036B2 (en) 2018-03-16 2023-08-29 Hamilton Sundstrand Corporation Integral heat exchanger mounts
CN115420131A (zh) * 2022-09-21 2022-12-02 西安电子科技大学 一种中心差分式换热器及其换热性能检测装置
CN115420131B (zh) * 2022-09-21 2024-04-19 西安电子科技大学 一种中心差分式换热器及其换热性能检测装置

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GB1284667A (en) 1972-08-09
FR2061736B1 (enrdf_load_stackoverflow) 1973-11-23
FR2061736A1 (enrdf_load_stackoverflow) 1971-06-25

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