US3882934A - Heat exchanger - Google Patents

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Publication number
US3882934A
US3882934A US259009A US25900972A US3882934A US 3882934 A US3882934 A US 3882934A US 259009 A US259009 A US 259009A US 25900972 A US25900972 A US 25900972A US 3882934 A US3882934 A US 3882934A
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US
United States
Prior art keywords
channels
fluid
heat exchanger
distributor
spiral
Prior art date
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Expired - Lifetime
Application number
US259009A
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English (en)
Inventor
Stellan Knoos
Soren F S Ljungdahl
Bertil Ingemar Bostrom
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Linde Sverige AB
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AGA AB
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
Application filed by AGA AB filed Critical AGA AB
Priority to US259009A priority Critical patent/US3882934A/en
Priority to SE7307165A priority patent/SE418223B/xx
Priority to DE19732327714 priority patent/DE2327714C3/de
Priority to GB2597973A priority patent/GB1437460A/en
Priority to SU731923471A priority patent/SU906395A3/ru
Priority to IT2495073A priority patent/IT993563B/it
Priority to NL7307679A priority patent/NL7307679A/xx
Priority to CA173,029A priority patent/CA991630A/en
Priority to JP6246873A priority patent/JPS5612795B2/ja
Priority to BE131835A priority patent/BE800401A/fr
Priority to AT484773A priority patent/AT325072B/de
Priority to FR7319989A priority patent/FR2186636B1/fr
Priority to CH801773A priority patent/CH591063A5/xx
Application granted granted Critical
Publication of US3882934A publication Critical patent/US3882934A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
    • 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
    • F28D9/04—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 being formed by spirally-wound plates or laminae
    • 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
    • Y10S165/398—Spirally bent heat exchange plate

Definitions

  • ABSTRACT A heat exchanger is formed from heat exchanger elements having coextensive parallel channels for carrying the fluids between which the heat transfer is to be accomplished. These channels are relatively narrow so as to permit efficient heat transfer from the fluid to United States Patent Knoos et al.
  • 21 Claims, 22 Drawing Figures the channel walls and may be formed from continuous strips of heat conducting material wound in a spiral. In order to minimize the pressure drop in the spiral shaped channels, they are fed into common channels after only a fraction of a full turn. Heat is transferred from the fluid in one of the heat exchange elements to the fluid in the other of such elements from the walls of the first element through a diaphragm which is interposed between the two elements to the walls of the second element. The components of the heat exchanger are mechanically clamped together so that they can readily be disassembled for replacement, repair or cleaning.
  • HEAT EXCHANGER This invention relates to heat exchangers, and more particularly to a heat exchanger for transferring heat energy between two fluid media which utilizes a pair of heat exchanger elements each having coextensive narrow parallel channels for carrying the fluid.
  • a number of prior art heat exchanger devices have been devised which utilize relatively narrow channels for carrying the heat exchanging fluids.
  • the channels are wound in a spiral configuration as well as other circular and linear configurations.
  • the channels for the two fluids, between which heat exchange is desired are run adjacent to each other with a common wall separating the fluids which also forms one of the walls for both of the adjacent channels.
  • Various prior art patents describing heat exchangers of this general type include U.S. Pat. Nos. 1,325,637; 2,995,344; 1,669,062; and 2,578,059. Swedish patents of interest along these lines include Swedish Pat. Nos.
  • the device of this invention overcomes the aforementioned shortcomings of prior art devices in the following rnanner: Firstly, the heat transfer fluxes are made very high by using extremely narrow channels for the fluid media. Despite the use of such narrow channels the pressure losses are kept under control by utilizing a plurality of coextensive channels which permit parallel flow. In the preferred embodiment, these channels are formed in a spiral winding with multiple inlets and exits along a turn of the winding so that a reasonably extensive channel length can be provided without the high pressure drop that would be presented if there were only a single inlet and outlet for each channel and the channels were fed singly rather than in parallel.
  • the device of the invention tends to be leaktight by virtue of the fact that the two fluid mediado not run in adjacent channels having a common channel wall, but rather are in two separate heat exchanger ele ments which are separated from each other by a diaphragm.
  • the channel walls themselves are subjected to extremely small mechanical loads and are less likely to leak than certain of the aforementioned prior art devices.
  • channel members and the associated components are not generally permanently attached to each other by soldering or welding or the like, the unit rather being held together by bolting or clamping techniques so as to enable ready disassembly for repair, cleaning or replacement of parts. Also, in view of the fact that no bonding medium is generally needed this obviates the aforementioned problems of achieving reliable bonding, particularly with operation under high temperatures.
  • the device of the invention lends itself to relatively economical and simple fabrication with relatively inexpensive materials.
  • FIG. 1 is a perspective view illustrating a first embodiment of the invention
  • FIG. 2 is a cross-sectional view taken along the plane indicated by 22 in FIG. 1;
  • FIG. 3 is a bottom plan view of the first embodiment with partial cutaway sections
  • FIG. 4 is a perspective view illustrating the inlet and outlet flow channels of the embodiment of FIG. 1;
  • FIG. 5 is a flow diagram illustrating the fluid flow in the embodiment of FIG. 1;
  • FIG. 6 is a cross-sectional view illustrating the fluid channels of the heat exchange elements of the embodiment of FIG. 1;
  • FIG. 7 is a side elevational view, partially in crosssection, of a second embodiment of the invention.
  • FIG. 8 is a bottom plan view of the second embodiment
  • FIG. 9 is a perspective view illustrating a heat exchange element of a further embodiment of the invention.
  • FIG. 10 is a top plan view of a heat exchanger element of another embodiment of the invention.
  • FIG. 11 is a crosssectional view taken along the plane indicated by 11l1 in FIG. l0;
  • FIG. 12 is a top plan view of a heat exchanger element of a further embodiment of the invention.
  • FIG. 13 is a cross-sectional view taken along the plane indicated by 13-13 in FIG. 12;
  • FIG. 14 is a cross-sectional view of a heat exchanger element of a further embodiment of the invention.
  • FIG. 15 is a cross-sectional view taken along the plane indicated by l515 in FIG. 14;
  • FIG. 16 is a cross-sectional view illustrating an embodiment of the invention utilizing stacked heat exchanging elements
  • FIG. 17 is a cross-sectional view taken along the plane indicated by l7--l7 in FIG. 16;
  • FIG. 18 is a side elevational view partially in section illustrating a further embodiment of the invention.
  • FIG. 19 is a bottom plan view with partial cutaway sections of the embodiment.
  • FIG. 20 is a side elevation view partially in section illustrating an alternate form of the channels utilized in the heat exchangers of the invention which employs heat pipes;
  • FIG. 21 is a side elevation view partially in section illustrating an alternative configuration for a casing that may be utilized in the heat exchanger device of the invention.
  • FIG. 22 is a cross sectional view illustrating an embodiment of the invention utilizing a single heat exchanger element.
  • the device of the invention comprises fluid heat exchanger elements having a plurality of coextensive narrow fluid channels which may be formed by a spiral winding or the like made from a flat strip of conductive material.
  • the input is in parallel to the channels thus formed, with a plurality of common outlet and/or inlet channels being provided along the extent of the channels so as to minimize pressure drop therealong.
  • a plurality of such common channels is provided along a single turn of the spiral.
  • the channels for the fluid media providing the heat energy and those for the fluid media receiving such energy are separate units and are placed on opposite sides of a separating diaphragm through which the heat energy is transferred, such transfer occurring principally from the walls of the narrow channels to the diaphragm.
  • the heat exchanger elements with the diaphragm therebetween are mechanically joined together by mechanical bolting or clamping means such that the device can be readily disassembled for cleaning, replacement or repair.
  • Housing 11 has first and second similar heat exchange elements 12 and 13 mounted therein, these elements being separated from each other by diaphragm 15, preferably fabricated of a high thermal conductive material.
  • the heat exchange elements l2 and 13 are held in tight engagement with diaphragm 15 within housing 11 by means of bolts 17 which threadably engage ring member 19.
  • Ring member 19 is threadably attached to housing 11, the ends of the bolts applying force against the bottom wall of circular pan-shaped member 22 which drives against heat exchange element 13.
  • Heat exchange elements 12 and 13 are generally similar in configuration and have a plurality of coextensive generally circular channels 23a and 23b formed therein.
  • each of these channels is one turn of the spiral windings from which they are joined.
  • These channels are formed by spiral windings 25a and 25b, which are wound around central core portions 27a and 27b respectively.
  • Spiral windings 25a and 25b may be fabricated of a metallic strip or ribbon of a material having high thermal conductivity, such as copper, aluminum or steel.
  • the channels 23a and 23b are relatively narrow such as to provide highly efficient heat transfer from the fluid flowing in the channel to the walls of the strip material.
  • the winding thereof may be facilitated by placing a wire 30 along the edge of the strip as it is wound, which effectively separates the windings from each other.
  • radial pins 32 may be utilized at several points along the windings to provide stiffening, these pins of course not being placed in the channels in such manner as to block the fluid flow therethrough.
  • the spiral windings may be formed by the techniques described in our copending application Ser. No.
  • Distributor channels 41a provide parallel fluid communication with flow channels 23a at 120 intervals around each turn of channels 23a.
  • Collector channels 48a-50a are formed in plate member 450 and are spaced at 120 intervals located between distributor channels 41a-43a.
  • Collector channels 48a-50a provide fluid communication with the parallel flow channels 23a at points halfway in between the distributor channels. Fluid communication is provided from collector channels 48a-50a to outlet tube 33a by means of the channel formed by grooved portion 52a of plate 45a.
  • the fluid input is fed from distributor channels 4la-43a into the heat exchange flow channels 23a in parallel, flowing in the channels axially in opposite directions to the adjoining collector channels 48a-50a, from where they are appropriately fed to outlet member 33a.
  • the fluid flows through an angular passage only 60 axially in the parallel spiral channels, thus minimizing the pressure drop.
  • the fluid flow path is schematically shown of the fluid flow from inlet channel 28a through distribution channel 43a through the heat exchanger channels 23a to adjacent collector channels 48a and 50a, and thence through channel 42a to the outlet 33a. Flow of course occurs in the same manner for each of the other distributor channels and adjoining collector channels.
  • the construction and operation of the heat exchanger element 13 is the same as that just described for the heat exchanger element 12, the 12 designated components having the same function as the corresponding a designated components with the same numerals described for unit 12. It is to be noted that FIG.
  • the channels 23a and 23b have a relatively narrow width, w, to the assure high heat-transfer rates between the channels walls and the fluid media. Further, the channels have a relatively large height, h, as compared with the width, this to assure large wetted areas and to lessen the pressure drop. It is also to be noted that the thickness dimension, t, of the channel walls is relatively large as compared with the width, w, this to give a low characteristic value for the temperature differential within the solid associated with the transfer of heat energy from the walls of the input heat exchange element to diaphragm 15 and from this diaphragm to the walls of the other heat exchange element. It is to be noted in this regard that the principal heat transfer between the fluids is accomplished through the channel walls and the diaphragm.
  • the dimensions of typical operating embodiments of the device of the invention are as follows:
  • Thickness t0.5 3 mm
  • Diameter of the spiral 100 mm Diameter of the spiral 100 mm. It is to be noted that these dimensions are given for illustrative purposes only and that these various dimensions could vary widely in different designs.
  • the design is governed by the following considerations.
  • three temperature differentials must be taken into consideration for a certain total heat transfer rate in the exchanger. These are: (l) the temperature differential between the first fluid and the wall material adjacent to that fluid; (2) the temperature differential between the second fluid and the wall material adjacent to that fluid; and (3) the temperature differential that occurs over the body of the wall material.
  • the characteristic effective temperature differential between the two fluids for carrying out the overall heat transfer rate is the sum of these three differences. The object in most heat exchange designs is to minimize this total temperature difference.
  • this end result is furthered in this invention by making the channels very narrow, such that very high vlaues of heat flux between the fluid and the channel wall material can be achieved. Further, this object is attained by providing a large wetted area by making a large number of coextensive channels and the height of the spiral windings relatively large. Also, for optimum heat transfer from the windings to the diaphragm it is important that there be good thermal contact therebetween. This can be accomplished by grinding the edges of the windings perfectly flat such that when pressure is applied with the tightening of the bolts which are used to hold the device together, intimate contact at these interfaces is achieved.
  • the heat exchanger of the invention can be utilized for both gaseous and liquid fluids, or for heat exchange between a gas and a liquid as well as between two liquids or two gases. As to be explained further on in the specification, it is also possible to utilize the device of the invention for transferring heat between fluids and solids.
  • FIGS. 7 and 8 another embodiment of the invention is shown.
  • This embodiment utilizes heat exchanger elements 12 and 13 which are spirally wound around central cores 27a and 27b respectively to form the fluid channels in the same fashion as the first embodiment.
  • This embodiment principally differs from the first embodiment in the implementation of its distributor and collector channels and in the structure used for assembling the units together in sealed relationship with seal 15 which in interposed therebetween.
  • Distribution of the incoming fluid from inlets 28a and 28b is provided directly to the spiral channels 23a and 23b respectively by means of grooves or slots 60 which are milled in the top portions of the channel walls adjacent to the inlets.
  • the collecting channels are implemented in the same fashion with slots 62 being milled in the channel walls in the vicinity of outlets 33a and 33b.
  • the inlets 28a and 28b and outlets 33a and 33b are located along the periphery of the windings and the channels 60 and 62 are tapered towards the center to produce a more uniform flow velocity in the various channels, the objective in this regard being to provide resistance to decrease the velocity for the flow in the more centrally located channels.
  • the flow passage is l, in opposite directions from the inlets 28a, 28b, to the outlets 33a, 33b, as indicated by arrows 65.
  • the device has end plates 66 and 67 which are spaced apart by cylindrical members 71 and 72, sealing for the fluid conveying portions being provided by means of seals 68 and 69.
  • the device is held together mechanically by means of bolts 78 which extend through end plates 66 and 67. These bolts are tightened up to provide the necessary pressure between the ends of spiral windings 25a and 25b and seal 15 to effect sealing therebetween.
  • fluid is introduced through inlet 28 and flows from here to four distributor channels 75 which are spaced at 90 intervals around the unit.
  • Distributor channels 75 are formed by holes in the heat exchanger windings 25.
  • Channels 77 are similarly formed in the spiral windings to provide collector channels, these collector channels being spaced halfway in between the distributor channels.
  • the collector channels 77 provide an exit for the fluid in a common channel (not shown) which may be formed around the periphery of unit 12. This embodiment thus provides 45 of angular flow.
  • embodiment distributor channels 79 are in the form of slots formed in the cover plate 80 of the device, with the collector channels 33 being in the form of milled out portions of the spiral windings.
  • the windings 25a and 25b and diaphragm are similar to those for the previous embodiments.
  • the fluid intake is distributed by means of distributor channels in the form of flow distributing meshes 87 which are placed over the top edges of the spiral windings 25a.
  • the collector channels are in the form of grooves 90 milled in the windings, these channels being covered by plates 91 to avoid the short circuiting of the flow paths.
  • the meshes 87 operate to produce a pressure drop for the flow passing therethrough of such a magnitude that the inlet flow is distributed relatively uniformly over the channels.
  • Other techniques may be used for implementing the function of meshes 87 in uniformly distributing the flow, such as for example the use of a porous plate.
  • Central plug unit 27a has four inlet channels 95 formed therein and four outlet channels 97 which communicate with a common channel 99 which is connected to outlet 33a.
  • Flow distributor channels for carrying the fluid flow to the channels 25a of windings 23a is provided by milled out portions 101 of the windings, each of which communicates with a separate one of channels 95.
  • the collector channels are similarly formed by milled out portions of the spiral windings (not shown) which connect with outlet channels 97.
  • FIGS. 16 and 17 a further embodiment of the invention is illustrated. Shown here is a section of a large heat exchanger utilizing a plurality of heat exchanger units stacked one on the other. These units are all contained within a cylindrical housing 11 having inlet channels 28 and outlet channels 33 formed in the walls thereof. As for the previous embodiments the spiral windings 25 are wound around a central core 27.
  • a cylinder 110 surrounds each of the heat exchanger elements and is joined to the housing 11 in sealed relationship.
  • the inner wall of the housing and the walls of cylinders 110 have a plurality of apertures 114 formed therethrough to permit the entrance and exit of the fluid to and from each of the heat exchanger units.
  • each heat exchanger system has its own separate inlet and outlet channels 28 and 33 respectively so that the fluid flows in each of these systems are separated from each other.
  • a convenient technique is provided for integrating a number of heat exchange devices of the invention, having separate fluid inputs and outputs, in a single stack.
  • the cylinder members are utilized around each of the spiral elements to assure proper sealing and clamping pressure around the units.
  • O-ring seals 120 are provided between housing 11 and cylinders 110 to assure that there are no leaks between the different fluid systems.
  • FIGS. 18 and 19 a heat exchanger in accordance with the invention that could be used for fluid flows with change of phase accompanying the heat exchange is illustrated.
  • This embodiment has a structure somewhat similar to the embodiment of FIGS. 7 and 8, and includes top and bottom plates 67 and 66 which are drawn together by means of bolts 78 and nuts 79 to clamp the heat exchange elements 12 and 13 in sealed relationship against diaphragm 15.
  • the distributor channels 120 and 121, and the collector channels 124 are milled out of the spiral windings.
  • the input fluid which may be a liquid is fed to each of the four inlets of heat exchanger element 13 which are located near the periphery of the spiral windings.
  • the liquid enters each of the four distributor channels 120. These channels extend inwardly only a fraction of the radius and hence cause distribution of liquid into only the outermost channels.
  • the fluid flows radially 45 in opposite directions as indicated by the arrows, to second distributor channels 121. Channels 121 extend all the way to core 27b, these channels being dead-ended at the core.
  • the fluid then flows radially 45 in opposite directions from channels 121 to collection channels 124, which are connected to fluid outlet 135.
  • this embodiment should preferably be located with diaphragm 15 horizontally oriented, with the liquid heat exchanger 13 below the diaphragm.
  • the bottom portions of the outer channel of exchanger 13 will be filled with liquid. After the fluid has gone through a turn and flows from channel 121 to channels 124, less liquid will be present in the channels. In the top portion of the inner channels 125, pure vapor will be present possibly in a superheated stage if temperature conditions so permit. In this way, pure vapor is drawn from the exit channel 135.
  • Upper heat exchanger element 12 may be of the type shown in FIG. 6.
  • the upper spiral winding rather than being formed of a single strip as for the previous embodiments, is formed from two strips 140 separated by a spacer 142, the spiral heat pipe channel 146 being formed between the strips.
  • the inner walls 140a of this channel are covered with a capillary pumping wick of sintered metal or the like, as is conventionally utilized in heat pipes.
  • Flow channels 148 are formed between the walls of adjacent windings of channel 146, spacer wire 150 being utilized to space these walls from each other. Proper sealing between channels 146 and 148 can be achieved by soldering the strips to diaphragm in conjunction with spacer wire 19.
  • the advantage of using the heat pipe spiral in implementing the invention provides better heat conduction in the spiral system in a direction perpendicular to diaphragm 15.
  • the use of heat pipe spiral permits a spiral height that is typically one order of magnitude greater than possible with a solid core ribbon.
  • this approach presents drawbacks, such as added heat conduction along the channels, added overall complexity, sealing problems, and less rigidity.
  • Spiral strip 25 may be of solid material as for the previous embodiments.
  • the cover plates 162 of the assembly have thin highstrength diaphragms 160 which cover them.
  • These cover plates can be molded from a material which preferably has low thermal conductivity, such as a suitable plastic or ceramic material, and need not have especially high strength. With a system of this kind, very high working pressures can be used and still the weight and size can be kept small.
  • the package is held together by means of clamping rings 170 and bolts 171, with ring member 173 being used to provide a guide for positioning rings 174 which encircle the heat exchange elements 12 and 13. Diaphragms 160 could initially be made flat so that they will buckle to the appropriate shape on the tightening of bolts 17].
  • Top wall portion thus replaces the diaphragm of the previous embodiments and transfers thermal energy between element 12 and member 180, which may comprise a solid body or other device which functions as a heat source or sink for heat exchanger element 12.
  • element 12 and member 180 which may comprise a solid body or other device which functions as a heat source or sink for heat exchanger element 12.
  • the heat exchanger element is clamped to member 180 by means of bolts 78 which threadably engage the walls of this member.
  • the device of this invention thus provides a highly efficient heat exchanger which is of simple and economical fabrication and which can be readily disassembled for replacement, repair or cleaning of components.
  • a heat exchanger comprising:
  • heat exchange element for receiving the flow of said fluid
  • said heat exchange element comprising a member having a plurality of coextensive narrow fluid channels formed on a single surface thereof, said channels being defined by walls extending from said surface, multiple distributor means spaced at intervals along said channels for distributing the fluid from said inlet means to all of said fluid channels in parallel, multiple collector means spaced from said distributor means at intervals along said channels for collecting the fluid in all of said channels in common channels at intermediate positions along said fluid channels located at distances from the distributor means which are substantially less in extent than the full length of said coextensive channels and means for feeding the fluid from said last mentioned common channel to said outlet means, and
  • a heat exchanger for transferring thermal energy between a pair of heat conductive media comprising:
  • one of said media comprising a heat exchanger element for receiving the flow of said fluid
  • said heat exchanger element comprising a member having a plurality of coextensive narrow fluid channels formed on a single surface thereof, said channels being defined by walls extending from said surface, multiple distributor means spaced at intervals along said channels for distributing the fluid from said inlet means to all of said fluid channels in parallel, multiple collector means spaced from said distributor means at intervals along said channels for collecting the fluid in all of said channels in common channels at position along said fluid channels located at distance from the distributor means which are substantially less in extent than the full length of said coextensive channels and means for feeding the fluid from said last mentioned common channel to said outlet means, and
  • the other of said heat conductive media comprises a second heat exchanger element similar to said first heat exchanger element and a fluid flowing in said second element, said means interposed between said units comprising a diaphragm forming an edge seal for each of said channels.
  • each of said heat exchanger elements are formed from a single conductive strip wound in a spiral configuration, one of the edges of the strip of one of said elements abutting against one side of said diaphragm, one of the edges of the strip of the other of said elements abutting against the opposite side of said diaphragm.
  • said means for applying mechanical pressure against said elements comprises a housing for said heat exchanger elements and screw means threadably attached to said housing for tightening said elements against each other within said housing.
  • said distributor means for distributing fluid to said channels and said collector means for collecting fluid from said channels comprises apertures extending through said channels and spaced from each other at intervals around the spiral, said apertures extending through separate sections of said spiral.
  • a heat exchanger for transferring heat energy from one fluid to another comprising:
  • each of said elements including a plurality of coextensive fluid channels formed from a strip of material wound in a spiral, a fluid inlet and outlet in said housing, multiple fluid distributor channel means extending essentially radially across said spiral and spaced at intervals about a full turn of said spiral, said fluid distributor channel means receiving fluid from said inlet and feeding said fluid in parallel to said channels, and multiple fluid collector channel means extending essentially radially across said spiral, said collector channel means being spaced from said distributor channel means so as to receive in parallel the fluid flow from said distributor channel means after it has passed through a portion of a single turn of said spiral channels, said collector channel means feeding fluid to said outlet, and a diaphragm interposed between the spiral windings of said first and second heat exchanger elements, one of the edges of each of said spiral windings of said first and second heat exchanger abutting against an opposite surface of said diaphragm, thermal energy being transferred between said heat exchanger elements through said diaphragm,
  • said housing means comprises a hollow cylinder having an open end and a closed end, said heat exchanger elements, said diaphragm and said distributor and collector channel means being contained within said cylinder, said means for mechanically clamping said heat exchanger elements together comprising a pan member fitted into the open end of said cylinder to cover said open end and bolt means threadably attached to the edge portion of the open end of said cylinder, said bolt means driving against said pan member thereby applying force thereagainst to drive said heat exchanger elements together.
  • said means for clamping said heat exchanger elements together comprises a pair of end plate members, said heat exchanger elements being sandwiched between said end plate members, and bolt means for drawing said end plate members towards each other.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US259009A 1972-06-02 1972-06-02 Heat exchanger Expired - Lifetime US3882934A (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
US259009A US3882934A (en) 1972-06-02 1972-06-02 Heat exchanger
SE7307165A SE418223B (sv) 1972-06-02 1973-05-22 Vermevexlare
DE19732327714 DE2327714C3 (de) 1972-06-02 1973-05-30 Wärmetauscher zum Wärmetausch zwischen zwei Strömungsmitteln, der beiderseits einer Scheidewand je einen von zwei gleichen Wärmetauschkörpern aufweist
GB2597973A GB1437460A (en) 1972-06-02 1973-05-31 Heat exchanger
IT2495073A IT993563B (it) 1972-06-02 1973-06-01 Scambiatore di calore
NL7307679A NL7307679A (fr) 1972-06-02 1973-06-01
SU731923471A SU906395A3 (ru) 1972-06-02 1973-06-01 Теплообменник
CA173,029A CA991630A (en) 1972-06-02 1973-06-01 Heat exchanger
JP6246873A JPS5612795B2 (fr) 1972-06-02 1973-06-01
BE131835A BE800401A (fr) 1972-06-02 1973-06-01 Echangeur de chaleur
AT484773A AT325072B (de) 1972-06-02 1973-06-01 Wärmeaustauscher
FR7319989A FR2186636B1 (fr) 1972-06-02 1973-06-01
CH801773A CH591063A5 (fr) 1972-06-02 1973-06-04

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US259009A US3882934A (en) 1972-06-02 1972-06-02 Heat exchanger

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US3882934A true US3882934A (en) 1975-05-13

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BE (1) BE800401A (fr)

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4074751A (en) * 1974-10-25 1978-02-21 Unice Machine Company Multiflow rotary heat exchanger element
US4397303A (en) * 1981-02-09 1983-08-09 Armco Inc. Heat exchanger for concentrating solar collectors and method for making the heat exchanger
US4678028A (en) * 1985-02-20 1987-07-07 Intertec Associates Inc. Plastic laboratory condenser
US5901783A (en) * 1995-10-12 1999-05-11 Croyogen, Inc. Cryogenic heat exchanger
US6796370B1 (en) * 2000-11-03 2004-09-28 Cray Inc. Semiconductor circular and radial flow cooler
US20060032611A1 (en) * 2004-08-13 2006-02-16 Fujitsu Limited Semiconductor device cooling apparatus
EP1308684A4 (fr) * 2000-08-10 2006-06-07 Kankyo Co Ltd Echangeur de chaleur, procede de fabrication correspondant et deshumidificateur comprenant ledit echangeur de chaleur
US20060266498A1 (en) * 2005-05-27 2006-11-30 Tay-Jian Liu Liquid cooling system suitable for removing heat from electronic components
US20070221364A1 (en) * 2006-03-23 2007-09-27 Cheng-Tien Lai Liquid-cooling heat sink
US20080047139A1 (en) * 2006-08-17 2008-02-28 Hul-Chun Hsu Method For Combining Axially Heated Heat Pipes And Heat-Conducting Base
US20080257535A1 (en) * 2007-04-23 2008-10-23 Thomas Christopher Cournane Shower trap heat recovery apparatus
RU2422745C1 (ru) * 2010-07-01 2011-06-27 Государственное образовательное учреждение высшего профессионального образования "Московский энергетический институт (технический университет)" (ГОУВПО "МЭИ(ТУ)") Пластинчатый теплообменник
US8038957B1 (en) 2009-06-25 2011-10-18 Cleary James M Electric catalytic oxidizer
CN102985781A (zh) * 2010-05-23 2013-03-20 福斯德物理学有限责任公司 热量和能量交换
US8921702B1 (en) * 2010-01-21 2014-12-30 Hrl Laboratories, Llc Microtruss based thermal plane structures and microelectronics and printed wiring board embodiments
US9222736B2 (en) 2009-06-24 2015-12-29 Valorbec Societe En Commandite, Representee Par Gestion Valeo S.E.C. Heat-exchanger configuration
US20160138873A1 (en) * 2014-11-13 2016-05-19 Hamilton Sundstrand Corporation Round heat exchanger
US9405067B2 (en) 2013-03-13 2016-08-02 Hrl Laboratories, Llc Micro-truss materials having in-plane material property variations
US20160222508A1 (en) * 2015-01-30 2016-08-04 Lam Research Corporation Modular vaporizer
US9546826B1 (en) 2010-01-21 2017-01-17 Hrl Laboratories, Llc Microtruss based thermal heat spreading structures
US20170350011A1 (en) * 2016-06-01 2017-12-07 Asm Ip Holding B.V. Manifolds for uniform vapor deposition
WO2018095978A1 (fr) * 2016-11-22 2018-05-31 Cevap Technology Bv Appareil de distillation à cartouche et son utilisation pour distiller de l'eau
US10107490B2 (en) 2014-06-30 2018-10-23 Lam Research Corporation Configurable liquid precursor vaporizer
US11096422B2 (en) * 2018-02-09 2021-08-24 Shenzhen First Union Technology Co., Ltd. Atomizer and electronic cigarette having same
US11492701B2 (en) 2019-03-19 2022-11-08 Asm Ip Holding B.V. Reactor manifolds
US20220369496A1 (en) * 2021-05-12 2022-11-17 Erwin Quarder Systemtechnik Gmbh Cooling device for dissipating heat
US11830731B2 (en) 2019-10-22 2023-11-28 Asm Ip Holding B.V. Semiconductor deposition reactor manifolds
US12516414B2 (en) 2019-03-19 2026-01-06 Asm Ip Holding B.V. Reactor manifolds

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EP4261487B1 (fr) * 2022-04-13 2025-12-31 HAIER Germany GmbH Lave-vaisselle, avec une unité d'échangeur de chaleur ou un dispositif échangeur de chaleur,

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US1325637A (en) * 1919-12-23 harrison
US1922534A (en) * 1933-02-21 1933-08-15 Ellsworth John Edward Heat exchange device
US2011201A (en) * 1933-05-12 1935-08-13 Rosenblads Patenter Ab Heat exchange apparatus made of sheet metal
US2131265A (en) * 1937-03-01 1938-09-27 Dow Chemical Co Spiral heat interchanger and method of making same
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US1325637A (en) * 1919-12-23 harrison
US1296916A (en) * 1918-02-07 1919-03-11 Charles F Burroughs Heating or cooling plate for molding-presses.
US1922534A (en) * 1933-02-21 1933-08-15 Ellsworth John Edward Heat exchange device
US2011201A (en) * 1933-05-12 1935-08-13 Rosenblads Patenter Ab Heat exchange apparatus made of sheet metal
US2131265A (en) * 1937-03-01 1938-09-27 Dow Chemical Co Spiral heat interchanger and method of making same
US2217316A (en) * 1937-11-30 1940-10-08 American Heat Reclaiming Corp Plate stack heat exchanger
US2736533A (en) * 1953-03-26 1956-02-28 John L Allen Heat exchange apparatus

Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4074751A (en) * 1974-10-25 1978-02-21 Unice Machine Company Multiflow rotary heat exchanger element
US4397303A (en) * 1981-02-09 1983-08-09 Armco Inc. Heat exchanger for concentrating solar collectors and method for making the heat exchanger
US4678028A (en) * 1985-02-20 1987-07-07 Intertec Associates Inc. Plastic laboratory condenser
US5901783A (en) * 1995-10-12 1999-05-11 Croyogen, Inc. Cryogenic heat exchanger
US20060124286A1 (en) * 1999-04-16 2006-06-15 Hidetoshi Ike Heat exchanger, a method for producing the same and a dehumidifier containing the same
US7147036B2 (en) 1999-04-16 2006-12-12 Kankyo Co., Ltd. Heat exchanger, a method for producing the same and a dehumidifier containing the same
EP1308684A4 (fr) * 2000-08-10 2006-06-07 Kankyo Co Ltd Echangeur de chaleur, procede de fabrication correspondant et deshumidificateur comprenant ledit echangeur de chaleur
US6796370B1 (en) * 2000-11-03 2004-09-28 Cray Inc. Semiconductor circular and radial flow cooler
US7278466B2 (en) * 2004-08-13 2007-10-09 Fujitsu Limited Semiconductor device cooling apparatus
US20060032611A1 (en) * 2004-08-13 2006-02-16 Fujitsu Limited Semiconductor device cooling apparatus
US20060266498A1 (en) * 2005-05-27 2006-11-30 Tay-Jian Liu Liquid cooling system suitable for removing heat from electronic components
US20070221364A1 (en) * 2006-03-23 2007-09-27 Cheng-Tien Lai Liquid-cooling heat sink
US7537047B2 (en) * 2006-03-23 2009-05-26 Foxconn Technology Co., Ltd. Liquid-cooling heat sink
US20080047139A1 (en) * 2006-08-17 2008-02-28 Hul-Chun Hsu Method For Combining Axially Heated Heat Pipes And Heat-Conducting Base
US7900353B2 (en) * 2006-08-17 2011-03-08 Jaffe Limited Method for combining axially heated heat pipes and heat-conducting base
US20080257535A1 (en) * 2007-04-23 2008-10-23 Thomas Christopher Cournane Shower trap heat recovery apparatus
US9222736B2 (en) 2009-06-24 2015-12-29 Valorbec Societe En Commandite, Representee Par Gestion Valeo S.E.C. Heat-exchanger configuration
US8038957B1 (en) 2009-06-25 2011-10-18 Cleary James M Electric catalytic oxidizer
US8921702B1 (en) * 2010-01-21 2014-12-30 Hrl Laboratories, Llc Microtruss based thermal plane structures and microelectronics and printed wiring board embodiments
US9546826B1 (en) 2010-01-21 2017-01-17 Hrl Laboratories, Llc Microtruss based thermal heat spreading structures
CN102985781A (zh) * 2010-05-23 2013-03-20 福斯德物理学有限责任公司 热量和能量交换
CN102985781B (zh) * 2010-05-23 2016-03-02 福斯德物理学有限责任公司 热量和能量交换
RU2422745C1 (ru) * 2010-07-01 2011-06-27 Государственное образовательное учреждение высшего профессионального образования "Московский энергетический институт (технический университет)" (ГОУВПО "МЭИ(ТУ)") Пластинчатый теплообменник
US9405067B2 (en) 2013-03-13 2016-08-02 Hrl Laboratories, Llc Micro-truss materials having in-plane material property variations
US10107490B2 (en) 2014-06-30 2018-10-23 Lam Research Corporation Configurable liquid precursor vaporizer
US20160138873A1 (en) * 2014-11-13 2016-05-19 Hamilton Sundstrand Corporation Round heat exchanger
US10113803B2 (en) * 2014-11-13 2018-10-30 Hamilton Sundstrand Corporation Round heat exchanger
US20160222508A1 (en) * 2015-01-30 2016-08-04 Lam Research Corporation Modular vaporizer
US9982341B2 (en) * 2015-01-30 2018-05-29 Lam Research Corporation Modular vaporizer
US11377737B2 (en) 2016-06-01 2022-07-05 Asm Ip Holding B.V. Manifolds for uniform vapor deposition
US10662527B2 (en) * 2016-06-01 2020-05-26 Asm Ip Holding B.V. Manifolds for uniform vapor deposition
US20170350011A1 (en) * 2016-06-01 2017-12-07 Asm Ip Holding B.V. Manifolds for uniform vapor deposition
US12416081B2 (en) 2016-06-01 2025-09-16 Asm Ip Holding B.V. Manifolds for uniform vapor deposition
WO2018095976A1 (fr) * 2016-11-22 2018-05-31 Cevap Technology Bv Appareil de distillation à cartouche et son utilisation pour distiller de l'eau
WO2018095978A1 (fr) * 2016-11-22 2018-05-31 Cevap Technology Bv Appareil de distillation à cartouche et son utilisation pour distiller de l'eau
US10751666B2 (en) 2016-11-22 2020-08-25 Cevap Technology B.V. Distillation apparatus with cartridge and use thereof for distilling water
US11096422B2 (en) * 2018-02-09 2021-08-24 Shenzhen First Union Technology Co., Ltd. Atomizer and electronic cigarette having same
US11492701B2 (en) 2019-03-19 2022-11-08 Asm Ip Holding B.V. Reactor manifolds
US12516414B2 (en) 2019-03-19 2026-01-06 Asm Ip Holding B.V. Reactor manifolds
US11830731B2 (en) 2019-10-22 2023-11-28 Asm Ip Holding B.V. Semiconductor deposition reactor manifolds
US20220369496A1 (en) * 2021-05-12 2022-11-17 Erwin Quarder Systemtechnik Gmbh Cooling device for dissipating heat
US12048130B2 (en) * 2021-05-12 2024-07-23 Erwin Quarder Systemtechnik Gmbh Cooling device for dissipating heat

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