US1930879A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US1930879A
US1930879A US638220A US63822032A US1930879A US 1930879 A US1930879 A US 1930879A US 638220 A US638220 A US 638220A US 63822032 A US63822032 A US 63822032A US 1930879 A US1930879 A US 1930879A
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United States
Prior art keywords
plates
spiral
channels
edges
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US638220A
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English (en)
Inventor
Linderoth Erik Torvald
Rosenblad Curt Fredrik
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Rosenblad Corp
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Rosenblad Corp
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Filing date
Publication date
Application filed by Rosenblad Corp filed Critical Rosenblad Corp
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Publication of US1930879A publication Critical patent/US1930879A/en
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Expired - Lifetime legal-status Critical Current

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    • 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

Definitions

  • This invention refers to heat-exchangers, and more particularly to heat-exchangers having heat transmitting surfaces of sheet metal bent to a spiral shape. Heat-exchangers of said latter type are very advantageous in respect of their heat economy but have had heretofore no practical use because the apparatus could not fulfil the requirements necessary for practical operation, viz:
  • the apparatus should be able to resist high pressures from the liquids, between which the transmission of heat is effected, without any deionnation 01' the spiral plates and without any change of the distance between said plates, because otherwise the resistance to the flow would be considerably increased and consequently one oi the most important advantages of such apparatus be lost. Moreover, the apparatus should be able to resist all stresses and strains to which i a heat-exchanger oi the type referred to and ilt' for resisting all strains and stresses metin normal operation. The apparatus shall also have such compactness and stability as to withstand transportation without damage.
  • a further object of this invention is to reduce the losses oi energy to a minimum.
  • Fig. 1 shows a vertical section through them:- paratus on the line II in Fig. 2.
  • Figr2 is a vertical section on the line IIII in Fig. 1.
  • Fig. 3 shows a section on the broken line III- m in Fig. 2, on a somewhat'larger scale.
  • Fig. 4 is 8.
  • FIG. 5 shows, partly in section, aperspective 'view 01' the rubber packing shown in Fig. 4.
  • Figs. 6 and-'7 are sections of details, illustrating modifications of the sealing device shown in Fig. 4.
  • Fig. 8 isa partial section through one of the connecting'pipes at the periphery and shows a modification oi the device for stabilizing the same.
  • 1 and 2 indi- 35 cates two rectangular plates, or sheets oi' metal, which are bent.to parallel spirals, thus forming 29 areboredto enable said plate 8 to be secured.
  • Each plate 1, 2 then forms a heat transmitting surface, in contact with the hot liquid on-one side and with so the cold liquid on the other side.
  • the innermost winding oi the spiral is provided with two smaller side plates 13 to form a cylindrical chamber 14.
  • Said chamber encloses a central tube or connection pipe 15, closed at one end by one of the side plates 13 and at the other end by a end closure plate 16, the chamber formed within the tube 15 being thus entirely sealed from the chamber 14.
  • a pipe 1'7 is mounted, communicating with the chamber 15 and in the other of said side plates 13 another connecting pipe 18 directly communicates with the chamber 14.
  • the tube 15 is cut .or slotted axially at 19 substantially throughout its whole length and liquidtightly connected with the channel 3 at said slot.
  • the channel 4 discharges into the chamber 14 substantially throughout the whole axial width thereof at 20. "Just as the other ends of the channels at 11 the ends of the channels at 19 and 20 have, for a certain length, a radial width successively increasing indirection to 19 and 20.
  • a number of stays or tierods 21 are secured, for instance, riveted or weld-' ed, across the openingsll and 19. Said stays have a narrow width in the direction at right angles to the direction of flow.
  • a number of stays 23 are provided between the tubes 9, 10 to stabilize them further and absorb thecouple of forces acting on said tubes.
  • the plates-and also the tubes 9, 10 are further secured against displacement so that the widened parts of the channels 3 or 4- at 12 cannot be diminished and thus the resistances to the flow cannot be increased.
  • said packings consist of sealing strips having a V- or U- or Ll-shaped cross section with the bottom or base turned towards the adjacent side plate 8, so that the pressure above atmospheric in the channels 3 or 4 presses the packings outwards against the side plate 8 and also against the plates '1, 2.
  • the strips 24 may easily be removed, because they are loosely inserted between the plates.
  • the legs or flanges 24a of the packing should, as shown in Fig. 5, have a greater distance from each other in their free and unstrained state before they are inserted between the plates than they have after such insertion so as to cause the packing to engage the plates with a certain initial pressure.
  • the bottom or base of the packing should also at all places be secured in such manner that a good scaling is attained.
  • Special filling pieces 12, 25 are welded to the plates 1, 2 at the widened parts of the channels 3 or 4, i. e. adjacent to the slots 11, 19, 20, to make the space for the packing wedge-shaped, decreasing to about the half of the width at 'said places, as is best seen at 26 in Fig. 3. when mounting said packings, it is, therefore, necessary to press the ends of the packings with force into said spaces and consequently a good sealing is attained and the ends of the packings are securely fixed to the channels.
  • sealing strips in accordance with this invention may be removed and again inserted several times without being destroyed, while on the contrary a plane packing can, as a .rule, be used only once, because the edges of the plates make deep impressions in the packing as a result of the strong tightening of the side plates necessary when packings of said lastmentioned type are used.
  • the plates 1, 2 may also be provided with low collars or flanges 31 at their edges along their whole peripheral length, as shown in Fig. 6. Said collars or flanges need only be small and then they'hinder neither the removal of the packings nor the cleaning of the channels 3 or 4.
  • recesses 32 may be substituted for said flanges at the peripheral edges of the plates, as shown in g. 7
  • the packing . is preferably constructed with a U-shaped section to fit snugly in said recesses.
  • the tube 9 forms one end of the channel 3 and the tube 17 the other end of the same channel, while the tubes 10 and 18 constitute the two ends of the channel 4.
  • the liquids may. be caused to flow in counter-current or inthe same direction through the apparatus, as desired.
  • the apparatus may of course be constructed with more than two parallel spiral channels for heat transmission between two or more liquids simultaneously.
  • Heat-exchangers having spiral heat transmitting surfaces have the double advantage of a great heat transmitting surface and a small volume and simultaneously a great length of the flow without sharp changes of the direction of.
  • the tubes 9 and 10 are stayed by means of cam flanges 33 welded to the outer surface of the tube atsuitable distances from each other.
  • Said flanges have preferably the shape of circular plates having eccentric holes for the tubes, as shown.
  • the flanges render the stays 21 superfluous, as shown in Fig. 8.
  • one single metal sheet may be used which is then doubled to form the tube 15 at the centre of the apparatus so that said tube 15 is integral with the walls of the two channels in which the two fluids flow in heat exchanging relation to each other.
  • the single doubled plate becomes in efiect two plates.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals forming channels between themselves, said channels having successively increasing cross-sectional areas at their ends, distance p eces secured between said plates adjacent to their spiral edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, and removable packings of a resilient non-metallic material in the open spaces at the spiral edges of said plates to seal said channels at those surfaces of the spirals, which are substantially at right angles to the axis thereof.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals forming channels betweenthemselves, distance pieces between said plates and welded to said plates adjacent to their spiral edges, said distance pieces being narrow in the peripheral direct on and also in the axial direction of said spiral plates, tubes at the periphery and at the centre of said spiral plates and provided with slots which extend substantially the entire axial width of said spiral plates, l'quid-tight connections between said plates and said tubes on both sides of said slots, stays secured'across said slots between the edges thereof and removable packings of a resilient material in the open spaces at the spral edges of said plates to seal said channels at those surfaces of the spirals, which are substantially at right angles to the axis thereof.
  • a heat-exchanger in combination, two or more metal plates bent to substantially par allel spirals, forming channels between themselves, said channels having successively increasing cross-sectlonal areas at their ends, distance pieces secured between said plates adjacent to their spiral'edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, and sealing strips of a resilient, non-metallic material inserted into the open spiral ends of said channels to close and seal them in the axial direction.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals, formng channels between themselves, said channels having successively increasing cross-sectional areas at their ends, distance pieces secured between said plates adjacent to their spiral edges, said dstance pieces being nar row in the peripheral and the axial directions of said spiral plates, and sealing strips of a nonmetallic, resilient material inserted into the open spiral ends of said channels to close and seal them in the axial direction, said strips having a substantially U-shaped cross section.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals, forming channels between themselves, said channels having successively increasing cross-sectional areas at their ends, distance pieces secured between said plates adjacent to their spiral edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, sealing strips of a resilient, nonmetallic material inserted into the open spiral ends of said channels to close and seal them in 14,5 the axial direction, and shoulders on said plates at their spiral edges to prevent said strips from sliding outwards axially.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals forming channels between themselves, said channels having successively increasing cross-sectional areas at their ends, distance pieces secured between said plates adjacent; to their spiral edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, sealing strips of a. resilient, nonmetallic material inserted into the open spiral ends of said channels to close and seal them in the axial direction, and shoulders projecting radially from said plates at their spiral edges to prevent said strips from sliding outwards axially, said shoulders being so low in the radial direction that said plates are readily accessible for cleaning after removal of said strips.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals forming channels between themselves, distance pieces secured between said plates adjacent to their spiral edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, removable packings of a resilient, non-metallic material at those edges of said spiral plates, which are substantially at right angles to the axis thereof, to close said channels, substantially plane side plates at said edges of said spiral plates and oneor more slots in said side plates for draining off liquid possibly leaking out.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals, forming channels between themselves, said channels having successively increasing cross-sectional areas at their ends, distance pieces secured between said plates adjacent to their spiral edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, removable packings of a resilient, non-metallic material at those edges of said spiral plates, which are substantially at right angles to the axis thereof, to close said channels, substantially plane side plates at said edges of said spiral plates, one or more slots in said side plates for draining oil liquid possibly leaking out, and means for keeping said side plates at a determined distance from the spiral edges of said plates.
  • a heat-exchanger in combination, two or more metal plates bent to substantially parallel spirals, forming channels between themselves, said channels having successively increasing cross-sectional areas at their ends, distance pieces secured-between said plates adjacent to their spiral edges, said distance pieces being narrow in the peripheral and the axial directions of said spiral plates, removable packings of a resilient, non-metallic material at those edges of said splral plates, which are substantially at right angles to'theaxis; thereof, to close said channels axially, substantially plane side plates at said edges of said spiral plates, one or more slots in said side plates, for draining off liquid possibly leaking out, bolts for securing said side plates to said spiral plates, and distance sleeves on said bolts N ISO

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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)
US638220A 1930-07-26 1932-10-17 Heat exchanger Expired - Lifetime US1930879A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE1930879X 1930-07-26
SE48245X 1932-03-18

Publications (1)

Publication Number Publication Date
US1930879A true US1930879A (en) 1933-10-17

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ID=40786646

Family Applications (1)

Application Number Title Priority Date Filing Date
US638220A Expired - Lifetime US1930879A (en) 1930-07-26 1932-10-17 Heat exchanger

Country Status (4)

Country Link
US (1) US1930879A (de)
DE (1) DE595190C (de)
DK (1) DK48245C (de)
FR (1) FR747978A (de)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2507094A (en) * 1944-09-08 1950-05-09 Stewart Warner Corp Method of and apparatus for making spiral heat exchangers
US2610038A (en) * 1949-03-29 1952-09-09 Loyal G Goff Thermal respirator
US2736533A (en) * 1953-03-26 1956-02-28 John L Allen Heat exchange apparatus
US3259183A (en) * 1961-12-30 1966-07-05 Basf Ag Plate type heat exchanger utilizing movable plate
US3921713A (en) * 1973-12-26 1975-11-25 Zachry Co H B Heat exchanger
US4128125A (en) * 1975-08-28 1978-12-05 Alfa-Laval Ab Spiral heat exchanger
US4993487A (en) * 1989-03-29 1991-02-19 Sundstrand Corporation Spiral heat exchanger
WO2004102101A1 (en) * 2003-05-15 2004-11-25 Alfa Laval Corporate Ab A spiral heat exchanger
US20110176316A1 (en) * 2011-03-18 2011-07-21 Phipps J Michael Semiconductor lamp with thermal handling system
US20110176291A1 (en) * 2011-03-18 2011-07-21 Sanders Chad N Semiconductor lamp
US20110193473A1 (en) * 2011-03-18 2011-08-11 Sanders Chad N White light lamp using semiconductor light emitter(s) and remotely deployed phosphor(s)
US20130140010A1 (en) * 2011-12-05 2013-06-06 Autokuhler Gmbh & Co. Kg Heat exchanger
US10782074B2 (en) 2017-10-20 2020-09-22 Api Heat Transfer, Inc. Heat exchanger with a cooling medium bar

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010046913A1 (de) 2010-09-29 2012-03-29 Hydac Cooling Gmbh Wärmetauscher

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2507094A (en) * 1944-09-08 1950-05-09 Stewart Warner Corp Method of and apparatus for making spiral heat exchangers
US2610038A (en) * 1949-03-29 1952-09-09 Loyal G Goff Thermal respirator
US2736533A (en) * 1953-03-26 1956-02-28 John L Allen Heat exchange apparatus
US3259183A (en) * 1961-12-30 1966-07-05 Basf Ag Plate type heat exchanger utilizing movable plate
US3921713A (en) * 1973-12-26 1975-11-25 Zachry Co H B Heat exchanger
US4128125A (en) * 1975-08-28 1978-12-05 Alfa-Laval Ab Spiral heat exchanger
US4993487A (en) * 1989-03-29 1991-02-19 Sundstrand Corporation Spiral heat exchanger
US7640972B2 (en) 2003-05-15 2010-01-05 Alfa Laval Corporate Ab Spiral heat exchanger
US20070062680A1 (en) * 2003-05-15 2007-03-22 Philippe Maupetit Spiral heat exchanger
CN100464150C (zh) * 2003-05-15 2009-02-25 阿尔法拉瓦尔股份有限公司 螺旋式热交换器
WO2004102101A1 (en) * 2003-05-15 2004-11-25 Alfa Laval Corporate Ab A spiral heat exchanger
US20110176316A1 (en) * 2011-03-18 2011-07-21 Phipps J Michael Semiconductor lamp with thermal handling system
US20110176291A1 (en) * 2011-03-18 2011-07-21 Sanders Chad N Semiconductor lamp
US20110193473A1 (en) * 2011-03-18 2011-08-11 Sanders Chad N White light lamp using semiconductor light emitter(s) and remotely deployed phosphor(s)
US8272766B2 (en) * 2011-03-18 2012-09-25 Abl Ip Holding Llc Semiconductor lamp with thermal handling system
US8461752B2 (en) 2011-03-18 2013-06-11 Abl Ip Holding Llc White light lamp using semiconductor light emitter(s) and remotely deployed phosphor(s)
US8596827B2 (en) 2011-03-18 2013-12-03 Abl Ip Holding Llc Semiconductor lamp with thermal handling system
US8803412B2 (en) 2011-03-18 2014-08-12 Abl Ip Holding Llc Semiconductor lamp
US20130140010A1 (en) * 2011-12-05 2013-06-06 Autokuhler Gmbh & Co. Kg Heat exchanger
US10782074B2 (en) 2017-10-20 2020-09-22 Api Heat Transfer, Inc. Heat exchanger with a cooling medium bar

Also Published As

Publication number Publication date
DE595190C (de) 1934-04-11
DK48245C (da) 1934-01-08
FR747978A (fr) 1933-06-26

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