US3840070A - Evaporator-condenser - Google Patents

Evaporator-condenser Download PDF

Info

Publication number
US3840070A
US3840070A US00230729A US23072972A US3840070A US 3840070 A US3840070 A US 3840070A US 00230729 A US00230729 A US 00230729A US 23072972 A US23072972 A US 23072972A US 3840070 A US3840070 A US 3840070A
Authority
US
United States
Prior art keywords
plates
passages
heat exchanger
fluid
pairs
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.)
Expired - Lifetime
Application number
US00230729A
Other languages
English (en)
Inventor
R Becker
W Ulbrich
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19712111026 external-priority patent/DE2111026C/de
Application filed by Linde GmbH filed Critical Linde GmbH
Application granted granted Critical
Publication of US3840070A publication Critical patent/US3840070A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • F28D9/0018—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 apparatus having an annular form without any annular circulation of the heat exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/04—Down-flowing type boiler-condenser, i.e. with evaporation of a falling liquid film
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356—Plural plates forming a stack providing flow passages therein
    • Y10S165/357—Plural plates forming a stack providing flow passages therein forming annular heat exchanger
    • Y10S165/358—Radially arranged plates

Definitions

  • Alternating pairs of plates are sealed together at opposite sides of the rectangular array from the sides of each'neighboring pair whereby each pair of plates defines one fluid passage and the next pair of plates defines the other fluid passage.
  • the plates are of corrugated or wrinkled (profiled) configuration so that, at least in the flow path of the condensable fluid, the corrugations or undulations define flanks which are inclined to the outlet of the condensate and form chutes or ramps along which the liquid is guided.
  • An evaporator-condenser of the plate-type is, of course, only a special case of a heat exchanger of the indirect type.v
  • at least one fluid is condensable or contains a condensable component such that, when latent heat of condensation is transferred through the wall of the heat exchanger to the other fluid, the component condenses and isdrawn off as a liquid from the system.
  • a liquid On the evaporator side, a liquid is vaporized with the thermal transfer toit of latent heat of condensation by heat exchange through the wall.
  • Evaporator-condensers are used, for example, in air-rectification installations of the Linde-Frnkl type, as boilers for low-temperature liquids and as gas condensers in similar applications.
  • the inlet and outlet of one pair of plates will permit the general flow of fluid in a direction perpendicular ⁇ to the flow of fluid between the next pair of plates,.the heatexchange wall between the fluids of these-two passages being common to both pairs.
  • the advantages of such plate-type heat exchangers include a high specific heatexchange surface area, low volume per unit of throughput or heat transfer, low 'material cost and simple construction methods.
  • Another object of the invention is to provide an evaporator-condenser which advances the art of platetype heat-exchangers and provides improved direction of the fluids 'traversing the respective flow passages.
  • plumb line or vertical as will be described in greaterdetail hereinafter; at least one of the inclined ramps, ledges or flanks discharging the condensate being inclined sharply to the horizontal but slightly relative to the verticle so as to approximate the fall line.
  • the present invention thus resides in a plate-type heat exchanger, adapted to operate as a condenser, in which the profiles or formations of the plates extend linearly and parallel to one another and preferably are formed with continually contacting crests at least engaging one another in the passage for the condensable fluid, the crests forming flumes or ramps leading downwardly to the condensate outlet, at least one such ramp being at a steep angle approximating the natural fall line.
  • the essential characteristic of this structure is that the profiles or crests of the juxtaposed plates defining the condensable-fluid passage are inclined to different extents to the aforementioned fall or plumb line and form troughs for the condensate which reach at least to the vicinity of the contact point at the steep inclination mentioned.
  • the profiles form the aforementioned troughs or ramps and can be of sawtooth cross-section with the sawtooth pitch of one plate being twice the sawtooth pitch of the opposite plate.
  • Another advantage of the system of the presentinvention is that the profiles or crests which extend at a slight angle to the principal flow direction according to the present invention, do not significantly interfere with throughflow and hence give rise to a minimal pressure drop between the inlet and outlet sides of the stack. It is possible in accordance with the aforementioned principles to have one fluid pass through chambers in which the ribs, profiles or crests form relatively large angles with the main flow direction while the throughflow in the other passages occurs at a minimal angle to the crests as already noted. ln this case, the low-pressure-drop passages may be used for the condensable fluid while a gas traverses the passages in which the crests run at large angles to the main flow direction and hence undergo intensive mixing.
  • each plate may be at both large and small angles to the main flow direction so that the optimum balance between pressure drop and turbulence is attained.
  • a turbulence or intensive mixing corresponds to greater heat transfer.
  • the rectangular plate is subdivided into parallel zones whose crests alternately lie at a small and a large angle to the main flow direction and we may provide crest-free strips between these zones to facilitate the cascading of the condensate toward the outlet.
  • the profiles are of the sawtooth shape mentioned above and consist of a generally horizontal flank defining the ramp and facing upwardly in the condensate compartment and an upwardly and inwardly directed wall rising from the horizontal flank.
  • This construction has been found to offer both the most desirable utilization of surface area and most rapid discharge of condensate. It has been found to be advantageous, moreover, to provide the aforementioned zones as vertically extending strips of profiled plate separated by vertically extending nonprofiled strips of smaller horizontal width.
  • the condensate fluid is preferably introduced in the horizontal direction through passages formed by openings of the plate pair along the vertical edges thereof when the plates are upright. For the pair of plates through which the condensable fluid is passed, we seal 'the horizontal sides of the plate pair together, e.g., by welding.
  • the stack of plates is provided in the form of a ring, with each pair of plates lying generally along a radial plane and extending vertically.
  • the condensable fluid is then passed radially through the heat exchanger while the vaporizable fluid may be passed axially therethrough.
  • the evaporator-condenser so constructed can be provided with a generally cylindrical housing having upper and lower annular dome portions through which the fluids are conducted axially through the array of plates and an annular trough along a periphery of the annular along which the condensate is collected.
  • FIG. l is an elevational view of a portion of a plate stack according to the present invention, partly broken away and corresponding generally to a view taken along the line I I of FIG. 2;
  • FIG. 2 is a cross-sectional view taken along the line II II of FIG. 1;
  • FIG. 3 is a vertical cross-sectional view through a portion of an evaporator-condenser embodying the invention
  • FIG. 4 is a cross-section taken generally along the line IV IV of FIG. 3;
  • FIG. 5 is an elevational view illustrating another set of plates according to the present invention.
  • FIG. 5 of the drawing from which the operating principles of the present invention will become clearer, it can be seen that a stack of sheetmetal plates S1, S2 and S3, all of rectangular configuration, can be joined along opposite edges to form pairs of plates defining respective fluid-flow compartments.
  • plates S1 and S2 may be sealed along their vertical edges E1 to define a flow compartment F1 between these plates which is open along the horizontal edges H1.
  • a fluid e.g., a vaporizable liquid or a heatabstracting gas, may then be introduced into the flow compartment F1 in the direction of arrow Al and will emerge as represented at A2.
  • a condensable fluid may be introduced horizontally (arrow A3) and will emerge as shown at A3.
  • the vertical openings of the entire stack of plates may be provided with a manifold M1, into which the condensable fluid is fed while, on the opposite side of the plates, a collecting manifold M2, preferably including a condensate trough as described subsequently, is provided to collect the fluid traversing the stack of plates in the horizontal direction.
  • a further manifold M3 communicates with all of the passages open along the lower horizontal edge and feeds a gas upwardly through the stack of heat-exchanger plates, the fluid being collected by the upper manifold M4.
  • each pair of plates defining a flow passage is formed with profiles or crests C, and C2 which extend at different angles to a plumb line or fall line which has been illustrated as a dot-dash line L in FIG. 5.
  • this plumb line (vertical) or fall line is defined as the line described by a free-fall body upon which the gravitational force acts. Itis the line along which a stream of liquid will cascade or a trickle of liquid will flow if not intercepted.
  • crests C are shown to include a relatively small angle a with the fall line while the crests C2 include the anglev with the fall line, being greater than a.
  • each crest of the two plates intersect and bear upon one another. Furthermore, each stream of fluid encounters an array of crests which have a small inclination to the main flow direction and are responsiblefor only a small pressure drop and an array of crests intercepting the flow at a large angle and responsible for augmented tur bulence.
  • plates 31 and 32 in FIGS. l and 2, we have shown the principles of the invention in somewhat greater detail.
  • plates 31 and 32 in the plate stack of these Figures, it can be seen that plates 31 and 32, the latter being shown in phantom lines since the view has been taken behind, constitute a plate pair defining a flow path for the condensable fluid whose main flow direction has been indicated by the arrows 33 and 34.
  • the plate 31 has a sawtooth profile which, in the direction of flow (arrows 33 and 34) runs at a relatively small angle downwardly.
  • Plate 32 likewise has a sawtooth profile which, in the direction of flow (arrows 33 and 34) runs at a large angle downwardly.
  • the surfaces of the plates 3l and 32 are divided by the sawtooth profiles into horizontal steps or flanks 37, 37a and 38, 38a, as well as inclined wall portions 35, 35a or 36, 36a intersecting at the crests of the formations.
  • the crests 39 and 40 defined at the junctions between t'he inclined wall portions 35, A35a, 36 and 36a with the respective steps 37, 37a, 38 and 38a constitute intersection ledges which bearupon one another at points such as are shown at 41.
  • Points equivalent to those shown at 41 and 42 are distributed in the formof a network over the entire area of both plates in substantially a lattice work so that the two plates bear against one another in force-transmitting relationship and defined at passages by spacing each other properly at the contact points.
  • a further pair of sheet metal thermally conductive plates 43 and 44 define a flow passage for the condensable fluid as represented by arrow 45 and cooperate with the previously described pair of plates to define a flow passage 46 between plates 31 and 40.
  • each of the inclined wall portions of the surface of a plate defining the condensate passage constitutes a condensing surface.
  • condensate is formed at points A in the form of droplets which unite with other droplets as they move downwardly in a small streamlet under gravitational force along the fall lines 47.
  • similar droplets trickle downwardly until they encounter the inwardly extending generally horizontal ledges or steps formed by the profiles and represented by the ledge 37a.
  • Several streamlets and the droplets thereof may unite at each ledge 37a and flow along the ledge as best seen in FIG. 1 to form a layer stream 48.
  • the condensate is traveling along the ramp in the direction of the condensate outlet in a downward direction
  • droplets formed by condensation on the walls of the opposing plate, e.g., at 36a trickle downwardly along the fall lines 49 at points B which have been illustrated solely by way of example.
  • the streamlet accumulates additional condensate drops until it forms a stream and is intercepted by the ledge 38a along which it is guided at high speed until the contact point or intersection point is reached.
  • FIGS. 3 and 4 we have shown the preferred embodiment of the evaporator-condenser according tothe present invention.
  • the evaporator-condenser comprises a cylindrical vessel 1 which is partitioned by an upwardly concave cup-shaped wall 2 into an upper portion 3 and a lower portion 4.
  • the lower portion 4 ofthe receptacle can be a pressure column of an air rectification installation while the upper housing portion 3 may form a low-pressure column or upper column of the gas-separation unit.
  • the partition 2 which forms a tray, according to the invention, there is provided a circular stack of heat-exchange plates represented generally at 5 and comprising a pair of plates 6 and 7 hermetically sealed at two opposing vertical edges 8 and 9.
  • the neighboring plates 6, 10 are sealed to the plates of the first-mentioned pair at opposite horizontal edges as represented at 12 and 13.
  • the plates thus lie in vertical planes through the axis of the cylindrical vessel and define generally radial passages between the plates sealed at the upper and lower edges. Accordingly, the other passages run generally axially.
  • the fluid to be condensed is, in the present embodiment, a gas which gathers at the head of column 4 and is in this case nitrogen.
  • the gas passes through the slotlike openings 14 between the plates 6 and 10 and traverses horizontally through passage l in the radial direction inwardly, i.e., in the direction in which the chamber converges in a wedge configuration.
  • the chamber constriction is proportional to the reduction in volume of the fluid with increasing condensation. As a consequence the passage creates a minimum flow resistance.
  • the liquid (condensate) passes along the ledges of the plates through opening 16 into an annular collecting trough 17 and is led via the pipe 18 back to the tower 4, e.g. for refluxing.
  • the other fluid collects as a liquid phase in tray 2 so that the space between ⁇ plates 6 and 7 is filled with a boiling f'luid.
  • the boiling fluid passes from an inlet slot 19 to an outlet slot 20 in the upward direction.
  • the liquid in the upper column is oxygen.
  • Profile free zones 11 run vertically along the plates defining the condensable-fiuid passage or chamber and separate the wider profiled zones from one another; the crests of the profiled zones are of alternating inclinations to the fall line.
  • a heat exchanger for effecting heat transfer between at least two fluids including a condensable fluid comprising a stack of generally rectangular upright heat-exchanger plates of thermally conductive material defining between successive pairs of said plates respective fiow compartments alternating for said fluids, means for passing said condensable fluid through the passages of first pairs of said plates, and means for passing another of said fiuids through the passages of second pairs of said plates, adjoining first and second pairs of plates having one plate in common for heat transfer between said fluids, said plates of said first pairs having transversely spaced linearly extending mutually parallel sawtooth profiles of acute-angle vertices extending inwardly into the passage for the condensable fluid and running at different angles to a condensate fall line along the plates defining the condensable-fiuid passages whereby crests of said profiles bear against one another at spaced locations over the areas of the plates defining the condensable fluid passages, said profiles forming liquid-fi
  • a heat exchanger for effecting heat transfer between at least two fluids including a condensable fiuid, said heat exchanger comprising a stack of generally rectangular upright heat exchanger plates of thermally conductive material defining between successive pairs of said plates respective flow compartments alternating for said fluids, means for passing said condensable fluid through the passages of first pairs of said plates, and means for passing another of said fluids through the passages of second pairs of said plates, adjoining first and second pairs of plates having one plate in common for heat transfer between said fluids, said plates of said first pairs having transversely spaced linearly extending mutually parallel profiles extending inwardly into the passage for the condensable fluid and running at different angles to a condensate fall line along the plates defining the condensable fiuid passages whereby crests of said profiles bear directly against one another at spaced locations over the areas of the plates defining the condensable fuid passages, said profiles forming liquidflow ramps leading downwardly toward a condensatedischarge side of said

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US00230729A 1971-03-08 1972-03-01 Evaporator-condenser Expired - Lifetime US3840070A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19712111026 DE2111026C (de) 1971-03-08 Kondensator-Plattenwärmetauscher

Publications (1)

Publication Number Publication Date
US3840070A true US3840070A (en) 1974-10-08

Family

ID=5800865

Family Applications (1)

Application Number Title Priority Date Filing Date
US00230729A Expired - Lifetime US3840070A (en) 1971-03-08 1972-03-01 Evaporator-condenser

Country Status (6)

Country Link
US (1) US3840070A (fr)
BE (1) BE779763A (fr)
CA (1) CA946827A (fr)
DE (1) DE2111026B1 (fr)
FR (1) FR2128289B1 (fr)
GB (1) GB1375503A (fr)

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4180129A (en) * 1976-09-08 1979-12-25 Hisaka Works, Ltd. Plate type condenser
US4182410A (en) * 1976-02-28 1980-01-08 Hisaka Works Ltd. Plate type condenser
US4182411A (en) * 1975-12-19 1980-01-08 Hisaka Works Ltd. Plate type condenser
US4195692A (en) * 1977-01-28 1980-04-01 Dion Biro Guy Fire-fighting nozzle assembly
US4230179A (en) * 1979-07-09 1980-10-28 Haruo Uehara Plate type condensers
US4237970A (en) * 1979-05-07 1980-12-09 Haruo Uehara Plate type condensers
US4314605A (en) * 1976-02-28 1982-02-09 Hisaka Works Ltd. Condenser
US4347897A (en) * 1977-01-19 1982-09-07 Hisaka Works, Ltd. Plate type heat exchanger
US4699209A (en) * 1986-03-27 1987-10-13 Air Products And Chemicals, Inc. Heat exchanger design for cryogenic reboiler or condenser service
US4715433A (en) * 1986-06-09 1987-12-29 Air Products And Chemicals, Inc. Reboiler-condenser with doubly-enhanced plates
US5259927A (en) * 1991-02-27 1993-11-09 Vaclav Feres Apparatus for thickening liquids
US5264083A (en) * 1990-05-07 1993-11-23 Metaleurop S.A. Distillation column tray
US5316628A (en) * 1989-06-30 1994-05-31 Institut Francais Du Petrole Process and device for the simultaneous transfer of material and heat
US5538593A (en) * 1991-06-27 1996-07-23 Hisaka Works Limited Thin film flow-down type concentrating apparatus
US5597453A (en) * 1992-10-16 1997-01-28 Superstill Technology, Inc. Apparatus and method for vapor compression distillation device
EP1058078A2 (fr) * 1999-05-31 2000-12-06 Haruo Uehara Condenseur
US20030132096A1 (en) * 2002-01-17 2003-07-17 Zebuhr William H. Rotating heat exchanger
US6666262B1 (en) * 1999-12-28 2003-12-23 Alstom (Switzerland) Ltd Arrangement for cooling a flow-passage wall surrounding a flow passage, having at least one rib feature
US6846387B1 (en) 2000-07-05 2005-01-25 Ovation Products Corporation Rotating fluid evaporator and condenser
US20050039486A1 (en) * 2002-01-17 2005-02-24 York Refrigeration Aps Submerged evaporator with integrated heat exchanger
US20050279620A1 (en) * 2004-06-17 2005-12-22 Ovation Products Corporation Blade heat exchanger
US20080047259A1 (en) * 2006-08-21 2008-02-28 General Electric Company Condensor unit for NOx emission reduction system
US20080099324A1 (en) * 2006-10-26 2008-05-01 Yun-Nan Chiu Solar energy seawater desalination device
US20140090822A1 (en) * 2009-08-19 2014-04-03 Alstom Technology Ltd Heat transfer element for a rotary regenerative heat exchanger
EP2920539A4 (fr) * 2012-11-07 2016-09-07 Vent Group B V R Échangeur de chaleur et ensemble de ventilation le comprenant
CN113091486A (zh) * 2021-04-21 2021-07-09 衡水新工质能源科技有限公司 一种微通道换热器
CN113701545A (zh) * 2021-09-09 2021-11-26 浙江锦欣节能科技有限公司 换热板片组以及换热器
US20220341637A1 (en) * 2020-01-14 2022-10-27 Daikin Industries, Ltd. Shell-and-plate heat exchanger
US11592238B2 (en) 2017-11-23 2023-02-28 Watergen Ltd. Plate heat exchanger with overlapping fins and tubes heat exchanger

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2155610A (en) * 1984-03-13 1985-09-25 Petrocarbon Dev Ltd Heat exchanger
DE3501936A1 (de) * 1985-01-22 1986-07-24 Dieter Steinegg-Appenzell Steeb Kreuzstrom-waermetauscher mit mindestens zwei plattenpaketen
GB8700801D0 (en) * 1987-01-14 1987-02-18 Marston Palmer Ltd Heat exchanger
FR2647198B1 (fr) * 1989-05-22 1991-07-19 Packinox Sa Echangeur thermique a conduits a plaques
GR1001064B (el) * 1991-09-06 1993-04-28 Ioannis Chortis Εναλλακτης θερμοτητας σχηματος κοιλου κυλινδρου
CN118499152A (zh) * 2024-07-17 2024-08-16 西安航天动力研究所 一种集成式氧蒸发器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2616530A (en) * 1945-06-21 1952-11-04 Hartford Nat Bank & Trust Co Heat exchanger
US3631923A (en) * 1968-06-28 1972-01-04 Hisaka Works Ltd Plate-type condenser having condensed-liquid-collecting means

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2616530A (en) * 1945-06-21 1952-11-04 Hartford Nat Bank & Trust Co Heat exchanger
US3631923A (en) * 1968-06-28 1972-01-04 Hisaka Works Ltd Plate-type condenser having condensed-liquid-collecting means

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4182411A (en) * 1975-12-19 1980-01-08 Hisaka Works Ltd. Plate type condenser
US4182410A (en) * 1976-02-28 1980-01-08 Hisaka Works Ltd. Plate type condenser
US4314605A (en) * 1976-02-28 1982-02-09 Hisaka Works Ltd. Condenser
US4180129A (en) * 1976-09-08 1979-12-25 Hisaka Works, Ltd. Plate type condenser
US4347897A (en) * 1977-01-19 1982-09-07 Hisaka Works, Ltd. Plate type heat exchanger
US4195692A (en) * 1977-01-28 1980-04-01 Dion Biro Guy Fire-fighting nozzle assembly
US4237970A (en) * 1979-05-07 1980-12-09 Haruo Uehara Plate type condensers
US4230179A (en) * 1979-07-09 1980-10-28 Haruo Uehara Plate type condensers
US4699209A (en) * 1986-03-27 1987-10-13 Air Products And Chemicals, Inc. Heat exchanger design for cryogenic reboiler or condenser service
US4715433A (en) * 1986-06-09 1987-12-29 Air Products And Chemicals, Inc. Reboiler-condenser with doubly-enhanced plates
US5316628A (en) * 1989-06-30 1994-05-31 Institut Francais Du Petrole Process and device for the simultaneous transfer of material and heat
US5264083A (en) * 1990-05-07 1993-11-23 Metaleurop S.A. Distillation column tray
US5259927A (en) * 1991-02-27 1993-11-09 Vaclav Feres Apparatus for thickening liquids
US5538593A (en) * 1991-06-27 1996-07-23 Hisaka Works Limited Thin film flow-down type concentrating apparatus
US5597453A (en) * 1992-10-16 1997-01-28 Superstill Technology, Inc. Apparatus and method for vapor compression distillation device
EP1058078A2 (fr) * 1999-05-31 2000-12-06 Haruo Uehara Condenseur
EP1058078A3 (fr) * 1999-05-31 2002-03-27 Haruo Uehara Condenseur
US6666262B1 (en) * 1999-12-28 2003-12-23 Alstom (Switzerland) Ltd Arrangement for cooling a flow-passage wall surrounding a flow passage, having at least one rib feature
US6846387B1 (en) 2000-07-05 2005-01-25 Ovation Products Corporation Rotating fluid evaporator and condenser
US7472563B2 (en) 2002-01-17 2009-01-06 Alfa Laval Corporate Ab Submerged evaporator with integrated heat exchanger
US20050039486A1 (en) * 2002-01-17 2005-02-24 York Refrigeration Aps Submerged evaporator with integrated heat exchanger
US6908533B2 (en) * 2002-01-17 2005-06-21 Ovation Products Corporation Rotating heat exchanger
US20030132096A1 (en) * 2002-01-17 2003-07-17 Zebuhr William H. Rotating heat exchanger
US20050279620A1 (en) * 2004-06-17 2005-12-22 Ovation Products Corporation Blade heat exchanger
US7427336B2 (en) 2004-06-17 2008-09-23 Zanaqua Technologies, Inc. Blade heat exchanger
US20080047259A1 (en) * 2006-08-21 2008-02-28 General Electric Company Condensor unit for NOx emission reduction system
US7802423B2 (en) * 2006-08-21 2010-09-28 General Electric Company Condenser unit for NOx emission reduction system
US20080099324A1 (en) * 2006-10-26 2008-05-01 Yun-Nan Chiu Solar energy seawater desalination device
US9448015B2 (en) * 2009-08-19 2016-09-20 Arvos Technology Limited Heat transfer element for a rotary regenerative heat exchanger
US20140090822A1 (en) * 2009-08-19 2014-04-03 Alstom Technology Ltd Heat transfer element for a rotary regenerative heat exchanger
EP2920539A4 (fr) * 2012-11-07 2016-09-07 Vent Group B V R Échangeur de chaleur et ensemble de ventilation le comprenant
US11592238B2 (en) 2017-11-23 2023-02-28 Watergen Ltd. Plate heat exchanger with overlapping fins and tubes heat exchanger
US20220341637A1 (en) * 2020-01-14 2022-10-27 Daikin Industries, Ltd. Shell-and-plate heat exchanger
US11747061B2 (en) * 2020-01-14 2023-09-05 Daikin Industries, Ltd. Shell-and-plate heat exchanger
CN113091486A (zh) * 2021-04-21 2021-07-09 衡水新工质能源科技有限公司 一种微通道换热器
CN113701545A (zh) * 2021-09-09 2021-11-26 浙江锦欣节能科技有限公司 换热板片组以及换热器
CN113701545B (zh) * 2021-09-09 2024-04-26 浙江星煜机电科技股份有限公司 换热板片组以及换热器

Also Published As

Publication number Publication date
DE2111026B1 (de) 1972-08-03
CA946827A (en) 1974-05-07
BE779763A (fr) 1972-06-16
FR2128289A1 (fr) 1972-10-20
FR2128289B1 (fr) 1974-03-15
GB1375503A (fr) 1974-11-27

Similar Documents

Publication Publication Date Title
US3840070A (en) Evaporator-condenser
US4235281A (en) Condenser/evaporator heat exchange apparatus and method of utilizing the same
US3983191A (en) Brazed plate-type heat exchanger for nonadiabatic rectification
US4182411A (en) Plate type condenser
US4119140A (en) Air cooled atmospheric heat exchanger
JP2004536701A (ja) 流体混合物を蒸発並びにリボイラーするためのシステム
US5709264A (en) Heat exchanger
US4586565A (en) Plate evaporator
US11549760B2 (en) Heat dissipation assembly
US4361426A (en) Angularly grooved corrugated fill for water cooling tower
US6260830B1 (en) Film fill-pack for inducement of spiraling gas flow in heat and mass transfer contact apparatus with self-spacing fill-sheets
US5033539A (en) Heat exchanger apparatus
GB2172697A (en) Heat pipes
JPS6317394A (ja) 熱伝達用熱交換パイプ
US4899808A (en) Condensing surface for heat exchanger with fins arranged to drip condensate onto one side only
JP4199125B2 (ja) 内部熱交換型蒸留塔
US3720071A (en) Heat exchanger
WO1988007166A1 (fr) Structure de tour pour interaction gaz/liquide
EP0181662B1 (fr) Echangeur de chaleur comportant un tube à ailettes
KR102553541B1 (ko) 해수와 같은 공급물을 처리하기 위한 플레이트형 열교환기
US4574007A (en) Fractionating apparatus
US6314752B1 (en) Mass and heat transfer devices and methods of use
US2703701A (en) Heat exchanger
RU2294504C2 (ru) Теплообменная пластина, пакет пластин и пластинчатый теплообменник
US5213154A (en) Liquid desiccant regeneration system