US3590917A - Plate-type heat exchanger - Google Patents

Plate-type heat exchanger Download PDF

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US3590917A
US3590917A US773268A US3590917DA US3590917A US 3590917 A US3590917 A US 3590917A US 773268 A US773268 A US 773268A US 3590917D A US3590917D A US 3590917DA US 3590917 A US3590917 A US 3590917A
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Prior art keywords
plate
plates
pair
corrugations
heat exchanger
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US773268A
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English (en)
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Johann Huber
Leonhard Poth
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Linde GmbH
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Linde GmbH
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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
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04406—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system
    • F25J3/04412—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system in a classical double column flowsheet, i.e. with thermal coupling by a main reboiler-condenser in the bottom of low pressure respectively top of high pressure column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0037—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 paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2205/00—Processes or apparatus using other separation and/or other processing means
    • F25J2205/24—Processes or apparatus using other separation and/or other processing means using regenerators, cold accumulators or reversible 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
    • 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
    • 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
    • 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
    • F25J2290/44—Particular materials used, e.g. copper, steel or alloys thereof or surface treatments used, e.g. enhanced surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/02—Fastening; Joining by using bonding materials; by embedding elements in particular materials
    • F28F2275/025—Fastening; Joining by using bonding materials; by embedding elements in particular materials by using adhesives
    • 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
    • Y10S165/373—Adjacent heat exchange plates having joined bent edge flanges for forming flow channels therebetween

Definitions

  • the present invention relates to plate-type heat exchanges and, more particularly, to heat exchangers for low-temperature applications such as air or gas liquefaction and/or rectification.
  • plate-type heat exchangers When plate-type heat exchangers" are concerned, they usually are characterized by rectangular plates which define the heat transfer partitions as well as the channels for the respective media, as opposed to tube-type heat exchangers in which a plurality of tubes or pipes carry one medium while the surrounding space is filled with the other medium.
  • a further object of this invention is to provide an improved plate-type heat exchanger of high efficieney and low cost which obviates the disadvantages of earlier heat exchanger devices of the same general type.
  • an improved plate-type heat exchanger particularly satisfactory for use in low-temperature processes, can be made at relatively low cost and yet be of high heat exchange efficiency, when the heat exchanger is constituted of a stack of heat exchange plates deformed into an undulating cross section at least along a center region of the plates and juxtaposed such that the longitudinally extending undulations of each plate are transversely offset from those of the adjacent plate by approximately one half of the distance between corresponding undulation peaks or troughs (i.e. one half the wave length or period of the undulations) so that the undulations define channels of uniform cross section, the stack being assembled by an adhesive at the contacting or closest approach regions of the plates, e.g. at the periphery or the undulations thereof.
  • thermosetting synthetic resins especially epoxy resins
  • adhesives indeed wet" the metal as they approach their cooling temperature in spite of the fact that at ambient temperatures that may not have appeared to be capable of wetting the plates.
  • the resulting plate-type heat exchanger is substantially less expensive than soldered heat exchangers, not only because of the lower cost of the adhesive, but also because the defect rate decreases with the use of such adhesives.
  • the apparatus used in the manufacture of the heat exchanger is of lower cost and the process steps are of decreased complexity.
  • the undulating profile or cross section of the heat exchanger plates is substantially periodic in the manner of corrugations which may be generally sinusoidal or angular when, for example, the undulations have trapezoidal profiles.
  • the crests on one side of one of the plates of the stack bear directly upon the crests at the opposite side of the juxtaposed plate, the latter crest forming floors of troughs in line with the first-mentioned crests.
  • the duct for the several heat exchange fluids will have a generally hexagonal cross section, especially when the offset of the crests or the troughs of juxtaposed mutually adjacent plates is one half the intercrest spacing and one half the intertrough spacing.
  • an advantage of this construction wherein each crest abuts the floor of the trough of an adjoining compartment and vice versa, is that the assembly has a honeycomb structure capable of supporting the assembly mechanically against pressure differentials which may develop between the fluids traversing the respective channels. Furthermore, spacers within the channels can be avoided or omitted and vibrations in the form of alternate contractions and expansions of the channels are prevented. Since there is little change in flow cross section as a result of pressure differentials across the walls of the heat exchanger, the device is particularly suitable for use as a reversing heat exchanger in low-temperature technology wherein, for example, a gas to be liquefied is passed through one set of channels and impurities condensed therefrom as the gas traverses these channels in one direction.
  • a warm gas must flow through the same channels in the opposite direction at a subsequent stage while some arrangements provide for temporary evacuation of the channels and the use of sparging gases at various stages of the process. Since all of the channels have the identical flow cross section in the system of the present invention, such use of the heat exchanger as a reversing or reversible heat exchanger is facilitated.
  • the zone of contact between the crest of one plate and the floor of the trough of an adjacent plate lies substantially along a line. It has been found that such structures are susceptible to deformation, especially when the adhesive is applied only along marginal zones of the heat exchanger plates. Consequently, the adhesive should also be applied at the crest-contacting surfaces of the sinusoidal profiles.
  • the adhesive When trapezoidal profiles are provided, contact occurs along the small base of the trapezoid between the crest and trough of the adjacent plates; the adhesive thus may be applied to the crests and troughs as well as along the marginal zones of contact.
  • the adhesive at the crests is not vital but may be used if additional stability is desired. It may be noted, however, that it is the preferred arrangement to apply the adhesive at all contacting surfaces. This ensures total lack of movement of the plates of the heat exchanger relatively to one another both in their planes and transverse to their planes and also precludes any fluid flow transverse to the crests of the undulations.
  • the plates have a generally rectangular configurationwith the flow channels defined between and within the corrugations extending in the longitudinal direction of the rectangle.
  • the u'ndulate portion of each plate is formed by the central re gion thereof and is flanked at the small ends of the rectangle by an inlet and outlet zone free from the undulations and extending practically over the entire width thereof, these zones being identical on all the plates.
  • the plates are thus not only mutually coextensive but preferably have coextensive central corrugated zones and coextensive inlet and outlet zones at either end of theu ndulatin'g zone. These inlet and outlet zones are provided with guide structures, e.g.
  • the incoming fluid is bent through9 at'the inlet zone and traverses the undulating'zone before being diverted through 90 again at the outlet zone.
  • the result is a Z-shaped or U-shaped path for the heat exchange fluid.
  • the inlet and outlet openings may be located at the same longitudinal side of the rectangle.
  • the inlet and outlet zones of 'each plate are not corrugated or of wave configuration and are subject of deformation as a result of any pressure differential across these plates or between the heat exchange fluids.
  • the bosses which are spaced apart in both the longitudinal and transverse directions at the inlet and outlet zones of the plates and'are of frustoconical configuration, bear upon the adjoining plates and reinforce the stack against platedeformation under this pressure differential.
  • the bosses of each plate are alternately recessed therein and pressed outwardly therefrom to opposite sides of the plate for engagement with theinverse- ,ly shaped bosses of the adjoining plate.
  • the circular contact surfaces of these plates may also be provided with adhesive to bond the plates together.
  • bosses constitute projections in the path of the heat exchange fluid and thus increase the turbulence of the fluid flow and the heat exchange efficiency.
  • one or more bores or holes can be provided in the inlet and/or 'outlet region by means of which the heat exchange medium can be delivered to the respective sets of channels. Fluid supply in this manner is analogous to that of the radiator art.
  • each plate is provided with a profiled ridge over part or all of the periphery, the ridge being pressed transversely from the plate during the stamping operation which forms the crests and troughs and the bosses.
  • profiled bars of a cross section corresponding to these passages can be inserted and bonded with a thermosetting adhesive to the plates.
  • Theends of the heat exhanger can be supported in part by comblike structure whose arms are inserted into the openings between each pair of two interconnected plate edges.
  • the profiled bars and comb structures increase the rigidity of the assembly as well as the fluid tightness thereof.
  • profiled reinforcing bars or combs should be disposed so as not to obstruct the openings for introduction or removal of the fluid. They may, however, act as supports for housing structures designed to enclose the stack of plates and to introduce or remove the fluids from the channels.
  • the stack of relatively thin sheet metal plates is flanked along their broad surfaces by a pair of relatively'thick-walled cover plates whose surfaces turnedaway from the stack are smooth or flat while the surfaces of these thick plates turned toward the stack are corrugated or undulated corresponding to the corrugations of the plates against which they bear.
  • the stack of plates forming the body of the heat exchanger is composed of plates of unit construction and is symmetrical about a median plane through the stack whereby the plates may merely be reversed with respect to one another, stacked, cemented together with adhesive and assembled into the desired configuration.
  • Morcover it has been found to be advantageous to secure between plates of each pair defining an array of channels or passages for the fluids with their respective corrugations, throughs or crests, spring-ribbed sheet metal strips, preferably of profiled cross section, which increase the turbulence'of the fluids passing through the channels.
  • the strips may be of sinusoidal configuration or trapezoidal configuration, as willbe apparent hereinafter, and formed with flanks generally parallel to the direction of fluid flow through the channel and to the crests and/or troughs in which they are housed. These flanks'may extend along the channels to subdivide them into a plurality of parallel compartments and may be formed with pockets, projections, protuberances or other formations which interfere with laminar flow along these flanks and promote turbulence.
  • The, plates of the stack of the present heat exchanger are preferably formed of a material of high thermal conductivity which also is usually stamped, e.g. copper, brass, aluminum or aluminum alloy. Best results are obtained with aluminum and its alloys although chromium-nickel-steel plates may also be employed.
  • FIG. 1A and FIG. IB are plan views from the top ofa lower plate and upper. plate, respectively, forming a stack in accordance with the'present invention for a plate-type heat exchanger;
  • FIG. 2 is a perspective view in exploded form of the plate stack of a heat exchanger inaccordance with another embodiment ofour invention.
  • FIG. 3 is a view similar to FIG, 2 illustrating yet another embodiment
  • FIG. 4 is a perspective exploded view of the plate stack of a heat exchanger according to this invention wherein one fluid describes a U-shaped path while the other fluid a substantially straight path;
  • I i FIG. 5 is a cross-sectional view through a plate-type heat exchanger embodying thepresent invention;
  • FIG. 6 and FIG. 7 are fragmentary perspective views of heat transfer elements adaptEd to be used in the system of FIG. 5;
  • FIG. 8 is an enlarged cross-sectional view of a fragment of a heat exchanger stack showing the use of the thermosetting resin to bond the plates together;
  • FIG. 9 is a partial perspectlve view of another plate assembly
  • FlG..l0 is a view similar to FIG. 8, showing the application of the principles of the present invention to a heat exchanger using plates of sinusoidal profile;
  • FIG. I1 is a cross-sectional view of another embodiment of this invention.
  • FIG. 12 is a plan view of a plate according to another feature of this invention.
  • FIG. 13 is a fragmentary elevational view diagrammatically illustrating a method of assembling and stiffening the stack.
  • FIG. 14 is a crossssectional view of the boss arrangement of the plates in FIGS. 1-4..
  • FIGS. 1A and IB we have shown a pair of plates 1 and 11 for a plate-type heat exchanger in which the plates may be stacked (FIG. 5 or 8), reinforced by the fingers of a comb support (FIG. 13) and bonded at its boss structure (FIG. 14).
  • the lower plate of this embodiment shown in FIG. 1A, is a pressed or stamped rectangular sheet metal body 1 havinga central zone C spaced inwardly from the narrow ends of the plate by the zones l and 0 respectively constituting the inlet and outlet sides of the plates and which are free from corrugations.
  • the central zone C of the plate is formed with a plurality of mutually parallel transversely spaced corrugations of trapezoidal cross section both in the longitudinal plane P and in the transverse plane P, the crests 3 of the corrugations rising out of the plane ofthe paper in FIG. 1A.
  • each trapezoid 3 rests upon the downwardly turned narrow face of the troughs of an upper plate.
  • the trapezoids are open at their wide bases.
  • the plate 1 has a zone 4 which is free from the corrugations 2, 3 and is provided with stamped bosses 6 which rise out of the plane of the paper and are of frustoconical configuration as shown, for example, in FIG. 14.
  • the bosses 6 have a height corresponding to that of the crests 3.
  • sealing ridges 7, 8, 9 and 10 which completely surround the formations 2, 3, 6 except at inlet 18 and outlet 19 along the right-hand longitudinal side of plate 1.
  • the sealing surfaces 7-10 may be coated with adhesive (FIG. 11) and are of the same height as the bosses 6 and the crests 2 and 3.
  • a similar array of bosses 6 is provided at the noncorrugated outlet side as represented at 5.
  • the upper plate 11 (FIG. 1B), which is designed to be placed upon the plate 1 of FIG. 1A, may be identlcal with plate 1 but rotated in its plane through 180.
  • the raised surfaces 7-10 of the latter abut the nonraised sealing surfaces 12, 13, 14 and 15 of plate 11 and are hermetically sealed relatively thereto with a thermosetting adhesive as described in connection with FIGS. 8-12 and 14.
  • the crests 3 of plate 1 are brought to bear against the floors 16 of plate 11 so that hexagonal channels are formed as shown in FIGS. 5 and 8.
  • the bosses 6 are so constituted that they alternately project from the surface (boss 6) or are recessed therein (6"); thus the recessed bosses 6" of plate 11 rest upon the upstanding bosses 6 of the plate 1 (see FIG. 14).
  • thermosetting synthetic resin is provided between the juxtaposed sealing faces of these bosses. Plates 1 and 11 are hermetically sealed with this resin over all of their mutually contacting surfaces. The plates can be stacked without separators and the gaps between the plates formed by the corrugations 2 charged with the heat exchange media.
  • one heat exchange medium is introduced at 17 and passes through the inlet 18 about the bosses 6 and is then deflected through the spaces between the crests prior to deflection outwardly through the outlet 19.
  • the result is a U- shaped flow pattern.
  • a countercurrent flow of the other gas stream along the opposite surfaces of plate 11 is represented by arrows 20.
  • the gas here passes into the assembly through inlet 21 and then flows along the valleys or troughs 16 prior to emerging from the system in a U-shaped pattern.
  • the fluid stream in each case, is deflected twice through angles of 90.
  • FIG. 2 an exploded view of a modified stack of plates has been illustrated, the plates 25, 26, 27 and 28 being of totally identical configuration with every other plate being rotated in its plane through 180".
  • the marginal portions 29 and 30 of plate 26 project toward the corresponding marginal portions 33 and 34 of plate 25 by a distance I equal to one half the combined altitudes a of the bosses 37, 38 and, therefore, the altitudes A of the channels formed between the plates (FIG. 5).
  • the plates 25 and 27 and the plates 26 and 28 thus are oriented similarly.
  • the boundary surfaces 29, 30, 31 and 32 of the plate 26 engage the boundary surfaces 33, 34, 35 and 36 through layers of thermosetting adhesive applied as shown at TP to the boundary portions in FIG. 12.
  • the noncorrugated inlet and outlet sides 4 and 5 of the plates 25-28 are provided with the bosses 37 and 38 which correspond to the bosses 6, 6', 6", and which alternately stand out from the plate or are pressed rearwardly therefrom.
  • the bosses 37 of plate 26 for example, bear against the bosses 38 of plate 25 (see FIG. 14). This construction ofthe plate allows each plate to rest against the neighboring plate at a multiplicity oflocations, thereby rendering the entire assembly substantially resistant to pressure differentials between the fluids.
  • the adhesive is preferably applied to the plates over all of their hearing locations and the system thereafter assembled and subjected to heat treatment at the curing temperature of the resin.
  • reinforcements in the form of the arms of a comb 101 or as profiled rods which fill the space between the surfaces 41 and 29 of plates 26 and 27, (see FIG. 13).
  • Manifold chambers are provided at 103.
  • Similar arms can be received in the openings 102 inwardly of the marginal portions 29 and 33 or 39 and 40 of the pairs of plates.
  • the arms 100 of course, have a cross section identical to that of the openings in which they are received. Suitable profiled bars for insertion in these openings have been shown at 91 and are received in the openings in the narrow end sides of the stack.
  • the thermosetting bonding agent is applied to the bearing surfaces of the plates, the profiled bars 91 and/or the arms 100 of the assembly.
  • the bars 91 increase the compressive strength, stiffness and fluid tightness of the assembly.
  • the profiled bars neednot extend the full length of the openings in which they are inserted to accommodate inlets and outlets for the heat exchange medium which, in the embodiments ofFlG. 2, is represented by the arrow 42 and passed in a U-shaped path from the inlet openings 43 to the outlet openings 44 between the plates.
  • the other heat exchange medium is represented by the arrow 45 and flows along an inserted U-shaped path through the inlet 46 to the outlet 47 between the plates 26 and 27 in countercurrent to the first-mentioned medium 42.
  • the collecting and manifold chambers of the heat exchanger are represented at 103 in which they are shown to be attached to bosses or other formations on the profiled bars 91 and/or the support comb 101.
  • the chambers may be hoods welded to these members (FIG. 13).
  • the flow cross section of the fluid mediums 42 and 45 can be interchanged for operation of the heat exchanger as a so called reversing exchanger" inasmuch as the flow cross section between each pair of plates is identical.
  • the two mediums which are passed in heat-exchanging relationship may have inlets in the form of two manifold chambers on the left side of the stack and two manifold chambers on the right side of the stack respectively for the functional interchange of the mediums in their flows through the respective channels.
  • the heat exchanger stack illustrated in FIG. 3 comprises the plates 50-53 which operate with three different mediums.
  • the plates are basically similar to those of FIGS. 1A, 1B and FIG. 2 and have trapezoidal section longitudinal undulations over the central region as described in connection with these Figures.
  • the inlet and outlet ends of the plates are free from such crests or troughs but are formed with frustoconical bosses which bear upon one another and are bonded together by the thermosetting synthetic resin.
  • Plates 50 and 51 When the plates 50 and 51 are bonded together at their peripheral surfaces 54-57 and 58-61, respectively, the usually confronting bosses and crests are similarly joined. Plates 50 and 51 define between them a U-shaped flow path wherein a first medium (represented by arrow 62) enters at an inlet 63 and exits through an outlet 64 between this pair of plates.
  • the boundary surfaces 58-61 of plates 51 are so contoured that between the plates 51 and 52 a linear flow path exists for a second medium 65 which, when the plates are bonded together by the thermosetting resin, cannot mix with the medium 62 and which enters at the narrow side 66 while departing at the narrow sides 67 of the assembly.
  • Plate 50 corresponds to the plates 25 and 27 of FIG.
  • plate 53 corresponds to plates 52 but is rotated in its plane l80 with respect to the other.
  • the space between plates 52 and 53 can sustain the flow of a third medium 68 in the same flow direction as medium 65.
  • the channels are formed as in plates 52 and 50 and a flow path is provided for the first medium 62.
  • the heat exchanger stack of FIG. 3 can be used with considerable advantage in air rectification wherein air, oxygen and nitrogen constitute the first, second and third medium. Since the flow cross sections of all the plates are identical, the channels my be used interchangeably for reversing heat exchanger relationship.
  • the stack of FIG. 3 requires two manifold chambers for the medium 62 and 68 on the right and left sides of the unit respectively and a further pair of collecting chambers along the upper and lower sides of the stack.
  • four mediums can be used, e.g. air, nitrogen, oxygen and a turbine gas which is to be heated for operating a low-temperature expansion turbine.
  • the latter stack requires eight collecting chambers, two at each longitudinal side and two at each of the narrow sides of the plates.
  • the stack of FIG. 4 provides the four plates 70, 71, 72 and 73 of which plates 70 and 72, and plates 7I and 73 are identical in form and position.
  • the direct stacking of the plates forms a heat exchanger assembly in which gas flow paths as represented by the arrows 80 and 83 can be sustained.
  • the trapezoidal corrugations 2 are pressed from the sheet metal plates and extend perpendicular to the plane of the paper but, with respect to the alternate plates, are offset from one another by half the intercorrugation distance.
  • a platetype heat exchanger as shown in FIG. 4 has been found to be particularly suitable for use as an evaporator-condenser, e.g. in the upper column ofa double rectification column for the separation of air into nitrogen and oxygen in accordance with the Linde-Frankl rectification system.
  • a central duct leads nitrogen vapor from the lower column to the heat exchanger as the first medium 80 to condense the latter while liquid oxygen passes directly through the unit and is vaporized.
  • the oxygen flow chamber may be closed by ultrasonic welding.
  • FIG. 5 shows the honeycomb section of a platelike heat exchanger in accordance with the invention and in which the broad open bases of the trapezoid register with one another to form hexagonal channels 90.
  • the crest of each one of the corrugations of a lower plate is bonded to the floor of the trough of a plate superimposed thereon.
  • Each of the channels may have a cross section with a hexagonal side length S of 2 to 3 mm.
  • openings which receive the profiled rods 91 or the arms I mentioned earlier.
  • one or more channels may be provided with a longitudinally extending heat transfer element 93 or 94 shown in enlarged scale in FIGS. 6 and 7.
  • the sheet metal elements which may span the width of the channels, act as partitions whose flanks 93a, 93b and 94a subdivide the channels into compartments on opposite sides of these partitions.
  • the partitions are provided with pockets 95, 96 which project into the path of the fluid to produce turbulence.
  • a sinusoidal heat transfer element is shown at 94 while the element 93 is of trapezoidal configuration.
  • FIG. 8 I have shown the honeycomb structure of FIG. 5 wherein contact is made between the small bases of the trapezoidal channels.
  • the synthetic resin layer TP is here coextensive with the small-base portions I08 and bonds the plates I09, 110, III and 112 together.
  • a sheet metal partition 113 can be introduced between the small bases I08 of the trapezoids, with the usual intervening layer TP. of thermosetting synthetic resin.
  • the undulating portions 115 and M6 on opposite sides of the plate I13 may be perforated as shown at 117 (FIG. 9) or provided with teeth (FIG. I l).
  • the corrugations may be of generally sinusoidal configuration as is shown, for example, for the plates 118, I19 and I20 in FIG. 10.
  • strips TP of thermoplastic synthetic resin are provided to bond the stack into a heat exchange unit.
  • a partition 121 can be disposed (FIG 11) and bonded to the plates I22 and 123 by thermosetting synthetic strips TF
  • the plates may be perforated or formed with teeth as shown at 124 in FIG. 11.
  • FIG. I2 has shown a plate to be stacked with similar plates in a heat exchange structure and herein the marginal edge 125 of the plate is continuous but is provided with the thermoplastic adhesive coating previously mentioned.
  • a pair of bores 127 at the uncorrugated inlet side ofthe plate 128 serve to admit the heat exchange fluid (129) and permit it to pass the bosses I30 which extend alternately upwardly and downwardly from the plane of the plate.
  • the flow paths (arrows 13]) are of Z-shaped configuration and lead to the outlet bores 132.
  • a plate-type heat exchanger using the configuration of FIG. 2 is assembled so that the six-sided longitudinally extending channel have a hexagonal side length S of 3 mm. or 2 mm. in tests A and B while the wall thickness s of the plates is 0.3 mm. and 0.2 mm.
  • the plates were composed of aluminum and eemented together with epoxy heated at the curing temperature in the usual manner. The following table lists the parameters and the results achieved:
  • a plate-type heat exchanger comprising a stack of at least two pairs of geometrically similar and registering rectangular plates having congruently registering outlines, each plate being formed with a plurality of transversely spaced corrugations parallel to its longitudinal edges and projecting out of the principal plane of the plate over only a central region thereof whereby the corrugation crests define a secondary plane parallel to the principal plane of the respective plate, each plate further having a pair of substantially noncorrugated regions at opposite ends of said central region lying in said principal plane and forming fluid distribution compartments com municating with troughs between the respective corrugations the corrugations of each plate being transversely offset from the corrugations of adjacent plates by about half the transverse spacing of the corrugations, one plate of each pair being formed with first edge portions lying in its principal plane and second edge portions lying in its secondary plane while the other plate of the pair is provided with second edge portions lying in its secondary plane and sealed to the first edge portions of said one plate of the pair while defining openings along said edge portions communicating with

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
US773268A 1967-11-03 1968-11-04 Plate-type heat exchanger Expired - Lifetime US3590917A (en)

Applications Claiming Priority (1)

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DE19671601216 DE1601216B2 (de) 1967-11-03 1967-11-03 Blechtafel fuer platten waermetauscher mit einem stapel solcher blechtafeln

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US3590917A true US3590917A (en) 1971-07-06

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US773268A Expired - Lifetime US3590917A (en) 1967-11-03 1968-11-04 Plate-type heat exchanger

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US (1) US3590917A (enrdf_load_stackoverflow)
BE (1) BE723137A (enrdf_load_stackoverflow)
DE (1) DE1601216B2 (enrdf_load_stackoverflow)
FR (1) FR1590755A (enrdf_load_stackoverflow)
GB (1) GB1238491A (enrdf_load_stackoverflow)

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US3757856A (en) * 1971-10-15 1973-09-11 Union Carbide Corp Primary surface heat exchanger and manufacture thereof
US3757855A (en) * 1971-10-15 1973-09-11 Union Carbide Corp Primary surface heat exchanger
US3810509A (en) * 1971-10-15 1974-05-14 Union Carbide Corp Cross flow heat exchanger
US3931854A (en) * 1973-08-24 1976-01-13 Viktor Vasilievich Ivakhnenko Plate-type heat-exchange apparatus
JPS52144852A (en) * 1976-05-28 1977-12-02 Panafacom Ltd Heat exchanger
JPS55160297A (en) * 1979-06-01 1980-12-13 Hitachi Ltd Heat exchanger
US4475589A (en) * 1981-01-21 1984-10-09 Tokyo Shibaura Denki Kabushiki Kaisha Heat exchanger device
US4572766A (en) * 1982-06-02 1986-02-25 W. Schmidt Gmbh & Co. K.G. Plate evaporator or condenser
US4758385A (en) * 1987-06-22 1988-07-19 Norsaire Systems Plate for evaporative heat exchanger and evaporative heat exchanger
US4872578A (en) * 1988-06-20 1989-10-10 Itt Standard Of Itt Corporation Plate type heat exchanger
US5114776A (en) * 1989-07-28 1992-05-19 Cesaroni Anthony Joseph Corrugated thermoplastic sheet having fluid flow passages
US5245693A (en) * 1991-03-15 1993-09-14 In-Touch Products Co. Parenteral fluid warmer apparatus and disposable cassette utilizing thin, flexible heat-exchange membrane
US5327958A (en) * 1992-07-16 1994-07-12 Tenez A.S. Stacked-plate heat exchanger
US5381510A (en) * 1991-03-15 1995-01-10 In-Touch Products Co. In-line fluid heating apparatus with gradation of heat energy from inlet to outlet
EP0844454A1 (de) * 1996-11-21 1998-05-27 Klingenburg GmbH Gegenstromwärmetauscher
US5846224A (en) * 1996-10-01 1998-12-08 Baxter International Inc. Container for use with blood warming apparatus
EP0803694A3 (de) * 1996-04-26 1999-03-03 SKS Stakusit Bautechnik GmbH Wärmetauscher in Plattenbauweise
US6047108A (en) * 1996-10-01 2000-04-04 Baxter International Inc. Blood warming apparatus
WO2000028271A1 (en) * 1998-11-10 2000-05-18 Centrax Limited Cylindrical plate-type heat exchanger
US6216774B1 (en) * 1996-10-17 2001-04-17 Honda Giken Kogyo Kabushiki Kaisha Heat exchanger
EP1099919A1 (en) * 1999-11-10 2001-05-16 The BOC Group plc Heat exchangers and dephlegmators
US6244072B1 (en) 1999-02-19 2001-06-12 The Boc Group Plc Air separation
US6394179B1 (en) * 1999-03-09 2002-05-28 Alfa Laval Ab Plate heat exchanger
US20040091735A1 (en) * 2001-01-08 2004-05-13 Frieder Flamm Method for producing evaporator boards
US20040149425A1 (en) * 1999-12-27 2004-08-05 Sumitomo Precision Products Co., Ltd. Plate Fin heat exchanger for a high temperature
US20050006077A1 (en) * 2003-06-25 2005-01-13 Somar Corporation Multi-layered adhesive sheet, material for forming heat exchanger, and heat exchanger
US6945321B2 (en) * 2001-02-15 2005-09-20 Sanden Corporation Heat exchangers
US20060065517A1 (en) * 2002-06-14 2006-03-30 Tosoh Smd, Inc. Target and method of diffusion bonding target to backing plate
US7044207B1 (en) * 1999-07-27 2006-05-16 Zie Pack Heat exchanger and related exchange module
US20070047209A1 (en) * 2005-09-01 2007-03-01 Alex Thompson Heat transfer plate
US20070151717A1 (en) * 2005-12-09 2007-07-05 Xenesys Inc. Heat exchange plate
US20090008073A1 (en) * 2005-12-22 2009-01-08 Hakan Larsson Means For Plate Heat Exchanger
US20090114369A1 (en) * 2007-11-02 2009-05-07 Kammerzell Larry L Air to air heat exchanger
US20090194268A1 (en) * 2006-08-28 2009-08-06 Dantherm Air Handling A/S Method for manufacturing a heat exchanger
CZ300999B6 (cs) * 2007-09-27 2009-10-07 2 V V S. R. O. Protiproudý rekuperacní výmeník
US20100139900A1 (en) * 2008-12-08 2010-06-10 Randy Thompson Gas Turbine Regenerator Apparatus and Method of Manufacture
US20110088417A1 (en) * 2009-10-19 2011-04-21 Kayser Kenneth W Energy Recovery Ventilator And Dehumidifier
FR2961892A1 (fr) * 2010-06-29 2011-12-30 Air Liquide Installation de separation d’air comprenant au moins un echangeur a surface primaire
US20120063973A1 (en) * 2009-05-22 2012-03-15 Agency For Science, Technology And Research Flexible Fluid Storage and Warming Bag and a Fluid Storage and Warming System
US20120255715A1 (en) * 2011-04-07 2012-10-11 Hamilton Sundstrand Corporation Liquid-to-air heat exchanger
US20130277024A1 (en) * 2012-04-23 2013-10-24 Gea Ecoflex Gmbh Plate Heat Exchanger
US20130277025A1 (en) * 2012-04-23 2013-10-24 Gea Ecoflex Gmbh Plate Heat Exchanger
US20130327513A1 (en) * 2010-06-30 2013-12-12 Sgl Carbon Se Heat exchanger plate, plate heat exchanger provided therewith and method for manufacturing a heat exchanger plate
US20140076527A1 (en) * 2012-09-20 2014-03-20 Airia Leasing Inc. Planar plate core and method of assembly
US20140305622A1 (en) * 2011-08-11 2014-10-16 Behr Gmbh & Co. Kg Device for controlling the temperature of an energy accumulator, more particularly for a vehicle, and method for production thereof
US20140335371A1 (en) * 2013-05-13 2014-11-13 Intri-Plex Technologies, Inc. Disk separator plates and method of making disk separator plates for hard disk drives
US9359952B2 (en) 2012-02-03 2016-06-07 Pratt & Whitney Canada Corp Turbine engine heat recuperator plate and plate stack
CN106054506A (zh) * 2015-04-08 2016-10-26 精工爱普生株式会社 热交换装置、冷却装置和投影仪
US20160333843A1 (en) * 2015-05-12 2016-11-17 Benteler Automobiltechnik Gmbh Motor vehicle heat exchanger system
US20160334170A1 (en) * 2015-05-12 2016-11-17 Benteler Automobiltechnik Gmbh Motor vehicle heat exchanger system
CN108779937A (zh) * 2016-03-09 2018-11-09 贝卡尔特燃烧技术股份有限公司 用于在热单元中使用的分段式热交换器
US10156405B2 (en) 2012-04-05 2018-12-18 Alfa Laval Corporate Ab Plate heat exchanger
EP1805471B1 (en) * 2004-10-07 2019-03-06 Brooks Automation, Inc. Method for exchanging heat
US10591220B2 (en) 2017-08-31 2020-03-17 Dana Canada Corporation Multi-fluid heat exchanger
EP3657116A1 (de) * 2018-10-30 2020-05-27 Cadro Industrial GmbH & Co. KG Verfahren zum herstellen eines wärmetauschers und wärmetauscher
EP3730890A1 (de) * 2019-04-24 2020-10-28 Vysoká Skola Bánská - Technická Univerzita Ostrava Plattenwärmeübertrager
EP3861270A1 (fr) * 2018-10-01 2021-08-11 Axens Plaque pour un échangeur de chaleur à plaques
CN113318466A (zh) * 2019-07-02 2021-08-31 江苏远卓设备制造有限公司 一种板式蒸发器的实现方法
US20220155031A1 (en) * 2019-03-28 2022-05-19 Zhejiang Sanhua Automotive Components Co., Ltd. Heat exchanger and heat exchange device
CN114753933A (zh) * 2022-06-15 2022-07-15 中国空气动力研究与发展中心设备设计与测试技术研究所 一种叶脉仿生主动冷却流道结构
US20220381519A1 (en) * 2020-02-10 2022-12-01 Daikin Industries, Ltd. Heat exchanger and heat pump system having same
US11745118B1 (en) 2022-06-02 2023-09-05 Ace Machine Design Llc Mechanical vapor recompression solvent recovery
US12044486B2 (en) * 2016-10-07 2024-07-23 Alfa Laval Corporate Ab Heat exchanging plate and heat exchanger

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US5385204A (en) * 1989-08-25 1995-01-31 Rolls-Royce Plc Heat exchanger and methods of manufacture thereof
US5287918A (en) * 1990-06-06 1994-02-22 Rolls-Royce Plc Heat exchangers
US5505256A (en) * 1991-02-19 1996-04-09 Rolls-Royce Plc Heat exchangers and methods of manufacture thereof
DE19635552C1 (de) * 1996-09-02 1998-03-12 Slg Pruef Und Zertifizierungs Wärmetauscher
FR2807828B1 (fr) * 2000-04-17 2002-07-12 Nordon Cryogenie Snc Ailette ondulee a decalage partiel pour echangeur de chaleur a plaques et echangeur de chaleur a plaques correspondant
CZ309357B6 (cs) 2021-07-28 2022-09-28 Vysoká Škola Báňská - Technická Univerzita Ostrava Rekuperační výměník tepla

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Cited By (84)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3757856A (en) * 1971-10-15 1973-09-11 Union Carbide Corp Primary surface heat exchanger and manufacture thereof
US3757855A (en) * 1971-10-15 1973-09-11 Union Carbide Corp Primary surface heat exchanger
US3810509A (en) * 1971-10-15 1974-05-14 Union Carbide Corp Cross flow heat exchanger
US3931854A (en) * 1973-08-24 1976-01-13 Viktor Vasilievich Ivakhnenko Plate-type heat-exchange apparatus
JPS52144852A (en) * 1976-05-28 1977-12-02 Panafacom Ltd Heat exchanger
JPS55160297A (en) * 1979-06-01 1980-12-13 Hitachi Ltd Heat exchanger
US4475589A (en) * 1981-01-21 1984-10-09 Tokyo Shibaura Denki Kabushiki Kaisha Heat exchanger device
US4572766A (en) * 1982-06-02 1986-02-25 W. Schmidt Gmbh & Co. K.G. Plate evaporator or condenser
US4758385A (en) * 1987-06-22 1988-07-19 Norsaire Systems Plate for evaporative heat exchanger and evaporative heat exchanger
US4872578A (en) * 1988-06-20 1989-10-10 Itt Standard Of Itt Corporation Plate type heat exchanger
US5114776A (en) * 1989-07-28 1992-05-19 Cesaroni Anthony Joseph Corrugated thermoplastic sheet having fluid flow passages
US5245693A (en) * 1991-03-15 1993-09-14 In-Touch Products Co. Parenteral fluid warmer apparatus and disposable cassette utilizing thin, flexible heat-exchange membrane
US5381510A (en) * 1991-03-15 1995-01-10 In-Touch Products Co. In-line fluid heating apparatus with gradation of heat energy from inlet to outlet
US5327958A (en) * 1992-07-16 1994-07-12 Tenez A.S. Stacked-plate heat exchanger
EP0803694A3 (de) * 1996-04-26 1999-03-03 SKS Stakusit Bautechnik GmbH Wärmetauscher in Plattenbauweise
US5846224A (en) * 1996-10-01 1998-12-08 Baxter International Inc. Container for use with blood warming apparatus
US6047108A (en) * 1996-10-01 2000-04-04 Baxter International Inc. Blood warming apparatus
US6216774B1 (en) * 1996-10-17 2001-04-17 Honda Giken Kogyo Kabushiki Kaisha Heat exchanger
EP0844454A1 (de) * 1996-11-21 1998-05-27 Klingenburg GmbH Gegenstromwärmetauscher
WO2000028271A1 (en) * 1998-11-10 2000-05-18 Centrax Limited Cylindrical plate-type heat exchanger
US6244072B1 (en) 1999-02-19 2001-06-12 The Boc Group Plc Air separation
US6394179B1 (en) * 1999-03-09 2002-05-28 Alfa Laval Ab Plate heat exchanger
US7044207B1 (en) * 1999-07-27 2006-05-16 Zie Pack Heat exchanger and related exchange module
EP1099919A1 (en) * 1999-11-10 2001-05-16 The BOC Group plc Heat exchangers and dephlegmators
US20040149425A1 (en) * 1999-12-27 2004-08-05 Sumitomo Precision Products Co., Ltd. Plate Fin heat exchanger for a high temperature
US6910528B2 (en) * 1999-12-27 2005-06-28 Sumitomo Precision Products Co., Ltd. Plate fin heat exchanger for a high temperature
US20040091735A1 (en) * 2001-01-08 2004-05-13 Frieder Flamm Method for producing evaporator boards
US6945321B2 (en) * 2001-02-15 2005-09-20 Sanden Corporation Heat exchangers
US20060065517A1 (en) * 2002-06-14 2006-03-30 Tosoh Smd, Inc. Target and method of diffusion bonding target to backing plate
US20050006077A1 (en) * 2003-06-25 2005-01-13 Somar Corporation Multi-layered adhesive sheet, material for forming heat exchanger, and heat exchanger
US7124814B2 (en) * 2003-06-25 2006-10-24 Somar Corporation Multi-layered adhesive sheet, material for forming heat exchanger, and heat exchanger
EP1805471B1 (en) * 2004-10-07 2019-03-06 Brooks Automation, Inc. Method for exchanging heat
US7646608B2 (en) * 2005-09-01 2010-01-12 Gm Global Technology Operations, Inc. Heat transfer plate
US20070047209A1 (en) * 2005-09-01 2007-03-01 Alex Thompson Heat transfer plate
US20070151717A1 (en) * 2005-12-09 2007-07-05 Xenesys Inc. Heat exchange plate
US20090008073A1 (en) * 2005-12-22 2009-01-08 Hakan Larsson Means For Plate Heat Exchanger
KR101300946B1 (ko) * 2005-12-22 2013-08-27 알파 라발 코포레이트 에이비 플레이트형 열교환기용 수단
US20090194268A1 (en) * 2006-08-28 2009-08-06 Dantherm Air Handling A/S Method for manufacturing a heat exchanger
CZ300999B6 (cs) * 2007-09-27 2009-10-07 2 V V S. R. O. Protiproudý rekuperacní výmeník
US20090114369A1 (en) * 2007-11-02 2009-05-07 Kammerzell Larry L Air to air heat exchanger
US8376036B2 (en) * 2007-11-02 2013-02-19 Az Evap, Llc Air to air heat exchanger
US20100139900A1 (en) * 2008-12-08 2010-06-10 Randy Thompson Gas Turbine Regenerator Apparatus and Method of Manufacture
WO2010068246A1 (en) * 2008-12-08 2010-06-17 Randy Thompson Gas turbine regenerator apparatus and method of manufacture
US8028410B2 (en) 2008-12-08 2011-10-04 Randy Thompson Gas turbine regenerator apparatus and method of manufacture
AU2009325121B2 (en) * 2008-12-08 2015-02-26 Randy Thompson Gas turbine regenerator apparatus and method of manufacture
US20120063973A1 (en) * 2009-05-22 2012-03-15 Agency For Science, Technology And Research Flexible Fluid Storage and Warming Bag and a Fluid Storage and Warming System
US20110088417A1 (en) * 2009-10-19 2011-04-21 Kayser Kenneth W Energy Recovery Ventilator And Dehumidifier
FR2961892A1 (fr) * 2010-06-29 2011-12-30 Air Liquide Installation de separation d’air comprenant au moins un echangeur a surface primaire
US20130327513A1 (en) * 2010-06-30 2013-12-12 Sgl Carbon Se Heat exchanger plate, plate heat exchanger provided therewith and method for manufacturing a heat exchanger plate
US20120255715A1 (en) * 2011-04-07 2012-10-11 Hamilton Sundstrand Corporation Liquid-to-air heat exchanger
US9151539B2 (en) * 2011-04-07 2015-10-06 Hamilton Sundstrand Corporation Heat exchanger having a core angled between two headers
US9643391B2 (en) * 2011-08-11 2017-05-09 Mahle International Gmbh Device for controlling the temperature of an energy accumulator, more particularly for a vehicle, and method for production thereof
US20140305622A1 (en) * 2011-08-11 2014-10-16 Behr Gmbh & Co. Kg Device for controlling the temperature of an energy accumulator, more particularly for a vehicle, and method for production thereof
US9359952B2 (en) 2012-02-03 2016-06-07 Pratt & Whitney Canada Corp Turbine engine heat recuperator plate and plate stack
US10156405B2 (en) 2012-04-05 2018-12-18 Alfa Laval Corporate Ab Plate heat exchanger
US20130277024A1 (en) * 2012-04-23 2013-10-24 Gea Ecoflex Gmbh Plate Heat Exchanger
US9546825B2 (en) * 2012-04-23 2017-01-17 Kelvion Phe Gmbh Plate heat exchanger
US20130277025A1 (en) * 2012-04-23 2013-10-24 Gea Ecoflex Gmbh Plate Heat Exchanger
US20140076527A1 (en) * 2012-09-20 2014-03-20 Airia Leasing Inc. Planar plate core and method of assembly
US10208979B2 (en) * 2012-09-20 2019-02-19 Airia Leasing Inc. Planar plate core and method of assembly
US20170023273A1 (en) * 2012-09-20 2017-01-26 Airia Leasing Inc. Planar plate core and method of assembly
US9283608B2 (en) * 2013-05-13 2016-03-15 Intri-Plex Technologies, Inc. Disk separator plates and method of making disk separator plates for hard disk drives
US20140335371A1 (en) * 2013-05-13 2014-11-13 Intri-Plex Technologies, Inc. Disk separator plates and method of making disk separator plates for hard disk drives
US10262689B2 (en) 2013-05-13 2019-04-16 Intri-Plex Technologies, Inc. Nesting disk separator plates for use in hard disk drives
CN106054506A (zh) * 2015-04-08 2016-10-26 精工爱普生株式会社 热交换装置、冷却装置和投影仪
CN106054506B (zh) * 2015-04-08 2018-06-29 精工爱普生株式会社 热交换装置、冷却装置和投影仪
US20160334170A1 (en) * 2015-05-12 2016-11-17 Benteler Automobiltechnik Gmbh Motor vehicle heat exchanger system
US20160333843A1 (en) * 2015-05-12 2016-11-17 Benteler Automobiltechnik Gmbh Motor vehicle heat exchanger system
CN108779937A (zh) * 2016-03-09 2018-11-09 贝卡尔特燃烧技术股份有限公司 用于在热单元中使用的分段式热交换器
US20190011149A1 (en) * 2016-03-09 2019-01-10 Bekaert Combustion Technology B.V. Sectional heat exchanger for use in a heat cell
US12044486B2 (en) * 2016-10-07 2024-07-23 Alfa Laval Corporate Ab Heat exchanging plate and heat exchanger
US10591220B2 (en) 2017-08-31 2020-03-17 Dana Canada Corporation Multi-fluid heat exchanger
EP3861270A1 (fr) * 2018-10-01 2021-08-11 Axens Plaque pour un échangeur de chaleur à plaques
EP3861270B1 (fr) * 2018-10-01 2025-08-20 Axens Paire de plaques pour un échangeur de chaleur à plaques
EP3657116A1 (de) * 2018-10-30 2020-05-27 Cadro Industrial GmbH & Co. KG Verfahren zum herstellen eines wärmetauschers und wärmetauscher
US20220155031A1 (en) * 2019-03-28 2022-05-19 Zhejiang Sanhua Automotive Components Co., Ltd. Heat exchanger and heat exchange device
US12140389B2 (en) * 2019-03-28 2024-11-12 Zhejiang Sanhua Automotive Components Co., Ltd. Heat exchanger and heat exchange device
EP3730890A1 (de) * 2019-04-24 2020-10-28 Vysoká Skola Bánská - Technická Univerzita Ostrava Plattenwärmeübertrager
CN113318466A (zh) * 2019-07-02 2021-08-31 江苏远卓设备制造有限公司 一种板式蒸发器的实现方法
US20220381519A1 (en) * 2020-02-10 2022-12-01 Daikin Industries, Ltd. Heat exchanger and heat pump system having same
US11815316B2 (en) * 2020-02-10 2023-11-14 Daikin Industries, Ltd. Heat exchanger and heat pump system having same
US11745118B1 (en) 2022-06-02 2023-09-05 Ace Machine Design Llc Mechanical vapor recompression solvent recovery
CN114753933B (zh) * 2022-06-15 2022-09-02 中国空气动力研究与发展中心设备设计与测试技术研究所 一种叶脉仿生主动冷却流道结构
CN114753933A (zh) * 2022-06-15 2022-07-15 中国空气动力研究与发展中心设备设计与测试技术研究所 一种叶脉仿生主动冷却流道结构

Also Published As

Publication number Publication date
BE723137A (enrdf_load_stackoverflow) 1969-04-01
FR1590755A (enrdf_load_stackoverflow) 1970-04-20
DE1601216B2 (de) 1971-06-16
GB1238491A (enrdf_load_stackoverflow) 1971-07-07
DE1601216A1 (de) 1970-03-26

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