US3735810A - Plate heat exchanger - Google Patents

Plate heat exchanger Download PDF

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Publication number
US3735810A
US3735810A US00116423A US3735810DA US3735810A US 3735810 A US3735810 A US 3735810A US 00116423 A US00116423 A US 00116423A US 3735810D A US3735810D A US 3735810DA US 3735810 A US3735810 A US 3735810A
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United States
Prior art keywords
discs
conduit
shell
openings
heat exchanger
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Expired - Lifetime
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US00116423A
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English (en)
Inventor
Ostbo K R Tranemo Ambjorn
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Individual
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Classifications

    • 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
    • F28F3/086—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning having one or more openings therein forming tubular heat-exchange passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/12—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element

Definitions

  • ABSTRACT A plate heat exchanger of the type comprising a shell housing circular discs arranged in succession separated by sealing rings.
  • the discs are provided with two sets of openings for passage therethrough of a first medium and a second medium, respectively.
  • the first set of openings for the first medium is positioned close to the outer periphery of the discs, i.e., radially outside of the separating rings, while the second set of openings for the second medium is positioned radially inside the separating rings.
  • the second set of openings are notches formed at the edge portion of a central hole passing through the discs and through which hole flows one of said media.
  • the discs are mounted on an axial tube the inner end of which extends inside the shell and is formed with slots but is otherwise closed, this tube end being also provided with asleeve serving to guide medium flowing through the tube and passing through the slots, in through the notches at the central hole of the discs.
  • the present invention relates to a universal-type plate heat exchanger.
  • Prior-art plate heat exchangers are usually quite bulky and have a complicated structure, and for this reason they are expensive to manufacture.
  • the plates are generally interconnected by means of bolts passing through them and usually these bolts have to be reckoned with when choosing the path of flow of the media passing through the exchanger.
  • a heat exchanger of plate-type is designed with a particular function in mind, i.e. for particular through-flow media, the particular amount of heat transfer, etc.
  • dismantling of a plate heat exchanger for repairs,.cleaning, inspection and like purposes has hitherto been complicated.
  • the invention is characterized by the fact that the radially inner openings are notches formed at the edge portion of a center hole in the metal plates, adapted to the flowed through by one of the media. Because the radially inner openings made in the metal plates are designed as edge notches formed at the periphery of the central plate hole in which the first medium flows, heat transfer between one medium and the other one is extremely good, which imparts to the efficiency of the heat exchanger.
  • One embodiment of the invention is characterized by an axial tube presenting at its one end a flange for attachment to a flange formed at one end of the shell, and presenting at its opposite end, which end is positioned in the shell interior, through-passage openings formed in the tube jacket, said tube being here otherwise closed, and by a sleeve mounted on the latter tube end, said sleeve being adapted to guide medium introduced into the tube and passed out through said throughpassage openings, in through said edge notches formed at the center hole in the metal plates.
  • This embodiment of the heat exchanger provides the considerable advantage of making possible separation of the two media in the heat exchanger in a simple way without the use of complicated seals.
  • FIG. 3 is a perspective view of two plates and their intermediate sealing rings on a portion of the longitudinal tube;
  • FIG. 4 shows on an enlarged scale an end view of the heat exchanger plate assembly
  • FIG. 5 is a cross-sectional view of a portion of the plate assembly
  • FIGS. 6, 7, and 8 are cross-sectional views through three different sealing rings
  • FIG. 9 is a vertical longitudinal section through the heat exchanger in accordance with another embodiment of the invention.
  • FIG. III illustrates on an enlarged scale a vertical longitudinal section through the plate assembly of the heat exchanger in accordance with the second embodiment
  • FIG. 11 is a longitudinal section through a heat exchanger in accordance with a somewhat simplified embodiment
  • FIG. 12 shows on an enlarged scale a longitudinal section through the plate assembly of the heat exchanger
  • FIG. ]13 is an end view of one half of one of the metal plates of the heat exchanger
  • FIG. 14 is a longitudinal section through a heat exchanger provided not only with inner and outer through-passage channels for one of the media but in addition with an intermediate through-passage channel for the other medium;
  • FIG. 15 illustrates a vertical longitudinal section through a similar heat exchanger installed as an economizer in the flue gas outlet of a heater
  • FIG. 16 illustrates on an enlarged scale a longitudinal section through one end of a plate assembly of the heat exchanger illustrated in FIG. 14, and
  • FIG. 17 is a cross-sectional view through this plate assembly along line XVII--XVII in FIG. 16.
  • the external structure of the plate heat exchanger in accordance with the invention comprises an essentially cylindrical jacket or shell 1 with an inlet 2 and an outlet 3 for the outer through-flow medium and an inlet 41 and an outlet 5 for the inner through-flow medium.
  • the inlet 4 for the inner through-flow medium is arranged at the outer end of an axial tube 6 the inner end 7 of which extends into the far end of the shell 1 where the outlet 3 for the outer through-flow medium is positioned.
  • the outlet 5 for the innerv through-flow medium is arranged adjacent the outer end of a pipe 8 which together with tube 6 forms a passage 9 for the inner through-flow medium.
  • the pipe 8 is provided with a flange 10 fitting a similar flange 111 formed at one end of the shell.
  • a washer 12 is arranged between flanges 10 and 11, and a number of bolts 13 are arranged to tighten said washer.
  • a number of circular metal plates 14 are mounted on the tube 6, each one of said plates presenting a plurality of radially outer openings 15 and a plurality of radially inner openings 16.
  • a sealing ring 17 of rubber, copper, asbestos or the like is arranged between adjacent metal plates M.
  • the material of the sealing rings 17 is chosen in accordance with the nature of the throughflow media, the working temperature, and like factors of interest in each particular case. In addition to being medium separating means, the sealing rings 17 also serve as distance means between the metal plates M.
  • the radially outer openings preferably are formed through punching radial tongues 18 in the plates which tongues are thereafter bent at an angle so as to project from one side of the plate 14.
  • the radially inner openings 16 are notches formed at the edge 19 of a center hole 20 formed in each plate 14 and through which hole 20 the tube 6 extends.
  • the plates 14 are mounted on the tube 6 and so positioned that the openings 15 in adjacent plates become angularly displaced or staggered relatively each other, as appears from FIGS. 4 and 5 whereby the outer through-passage medium is forced to be repeatedly deflected when passing through the heat exchanger.
  • the inner end 7 of the tube 6 is provided with longitudinally extending slots 21 formed in the tube jacket.
  • This tube end 7 is otherwise closed by means of an externally threaded pin 22 which is provided with a nut 23.
  • Asleeve 24 is threaded onto tube end 7 and this sleeve is designed so as to form an annular gap 25 outside the slots 21.
  • a ring-shaped seal 26 In the outer end of the sleeve 24 is inserted a ring-shaped seal 26 with an abutment ring 27 and a number of disc springs 28 positioned between said ring and the nut 23.
  • the arrows indicated in FIG. 1 illustrate the flow direction of the two media.
  • the outer medium is introduced through inlet 2, flows through openings 15 formed in the plate 14 and further out through the outlet 3 in the far end of the shell 1.
  • the inner medium is introduced through inlet 4, flows through the tube 6 and further through the slots 21 and the annular gap 25 and through the notches 16 and into passage 9 and out through outlet 5. It is evident that the heat-transfer through plates 14 becomes very efficient, above all because of the short distance through the material in the plates 14 from the openings 15 to openings 16 or vice versa.
  • sealing rings 17, 17', 17" may be given different shapes.
  • Two O-rings 29 are used for sealing ring 17".
  • FIG. 9 is externally constructed in the same way as the embodiment shown in FIG. 1.
  • the pin 22, nut 23, sleeve 24 and spring means 28 are eliminated in the embodiment in accordance with FIG. 9.
  • the outer end 7' of the tube 6' in this embodiment is completely open.
  • the metal plates 14' are attached to their sealing rings 17 through projection welding such that the entire plate assembly forms one single, rigid unit.
  • To the metal plate positioned at the inner end of tube 6' is welded a sleeve 31 with an end portion 30 such that an annular channel 25' is formed between tube end 7 and the jacket of the sleeve 31.
  • the plates 14 are turned relatively each other before the welding such that both the radially outer through-passage openings l5 and the radially inner openings 16 will be angularly displaced or staggered relatively each other, thus forcing the media to flow through the heat exchanger in a zig-zag pattern or in constantly changing directions.
  • the metal plates 14 are preferably made from a non- .corrosive material having high coefficient of thermal conductivity, such as for instance stainless steel, aluminium-brass, niccolite etc.
  • the plate heat exchanger in accordance with the present invention may be used both for heating and cooling of media, it being possible to perform both liquid-liquid treatments, liquid-vapor treatments as well as condensation of gases.
  • the limits of maximum pressure is entirely determined by the shell, and particularly by the flat short end surfaces thereof, whereas the sealing rings are only exposed to the differential pressure between the through-flow media.
  • the end portion 32 is provided with a central opening 34 to which is welded the inner end of an admission pipe 35 for one of the treatment media, and also the other end portion 33 is provided with a central opening 36 to which the outlet pipe 37 for said medium is attached through welding.
  • the outlet pipe 37 passes through a stuffing box 38 at one 39 of the short sides of the heat exchanger such that the pipe 37 may slide in the stuff'mg box 38 upon occurrence of thermal expansions or contractions of the heat exchanger.
  • each metal plate 14" consists of a circular disc or round 14a having a somewhat larger diameter and one circular disc or round 14b with a slightly smaller diameter.
  • the circular discs 14a are together with their sealing rings 17a interconnected by means of a projection and resistance welding assembly and the inner discs 14b together with their sealings rings 17b are in a similar way interconnected by means of pressure welding.
  • the radially inner edge 43 of the rounds 14a has ondulating configuration and also the radially outer edge 44 of the rounds 14b has ondulating configuration. Both edges 43 and 44 project into the annular space 42 between sealing rings 17a and 17b. In this way extensive surface expansion is obtained which favors heat transfer from one to the other of the media.
  • annular collection tubes 45, 46 having through-flow openings 47 for one of the treatment media. Collection tube 46 is through manifolds 48 connected to inlet tube 49 for one of the treatment media and collection tube 45 is via manifolds 50 connected to the outlet pipe 51 for this same medium.
  • the outlet pipe 51 passes through a stuffing box 52 in one end portion 53 of the heat exchanger (FIG. 14).
  • FIG. 15 illustrates installation of a heat exchanger assembly similar to the one shown in FIGS. 14, 16, 17 in a flue gas pipe 54 of a heater 55.
  • Collection tube 45 at the upper end of the plate assembly is via pipes 56 connected at the upper portion of the water container 56 of the heater 55 whereas collection tube 46 at the lower end of the plate assembly via pipes 57 is connected to the water container 56 immediately above the hearth 58 of the heater.
  • thelower collection tube 46 may be connected to the water container 56 at an even lower point.
  • the radially inner through-passage openings 41 are arranged in a central portion 59 of the inner rounds 14b. This has a favorable effect on the heat transfer between the two media.
  • the sealing rings 17b welded to the annular discs 14b may be said to have the same effect as tube 6 in the embodiment according to FIGS. 1 and 9.
  • This invention provides a space-saving, simple and comparatively cheap plate heat exchanger having a high heat transfer coefficient.
  • the openings in the metal plates may be displaced or offset relatively each other in many various ways.
  • the tongues 18 may be turned in opposite directions in adjacent plates, whereby a zig-zag through-flow pattern with 180 turning directions of themedia is obtained.
  • the metal plates may be formed with concentric corrugations, which considerably increases the heat transfer surface area.
  • a heat exchanger comprising an elongated hollow shell, means for supplying a first fluid to one end of said shell and removing it from the other end thereof, a first tubular conduit extending axially within said shell from one end thereof and terminating adjacent the other end of said shell, a plurality of discs surrounding andspaced from said first tubular conduit and extending fi om the outer surface of said conduit to the inner surface of said shell, each of said discs having a series of inner openings adjacent said conduit and outer openings adjacent said shell, annular sealing rings in the gaps between adjacent discs, said rings lying in the space between said inner and outer openings, a second tubular conduit surrounding and spaced from said first tubular conduit and extending into said hollow shell to a point intermediate between said one end of said shell and the terminal portion of said first tubular conduit, said plurality of discs being so arranged that one end disc of the plurality sealingly engages the end of said second tubular conduit within said shell through out an annular area intermediate the inner and outer openings in said disc, a
  • a heat exchanger as in claim 1 wherein one end of said hollow shell is sealingly closed by a removable plate having a central opening and said second tubular conduit is sealingly mounted in said opening and wherein said first tubular conduit is sealingly mounted in said first tubular conduit and extends through it into said shell.
  • a heat exchanger as in claim 2 wherein the opening connecting the interior of said first conduit with said closed chamber comprises a longitudinally extending slot.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00116423A 1970-08-21 1971-02-18 Plate heat exchanger Expired - Lifetime US3735810A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE11446/70A SE356124B (de) 1970-08-21 1970-08-21

Publications (1)

Publication Number Publication Date
US3735810A true US3735810A (en) 1973-05-29

Family

ID=20293988

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US00116423A Expired - Lifetime US3735810A (en) 1970-08-21 1971-02-18 Plate heat exchanger

Country Status (14)

Country Link
US (1) US3735810A (de)
AR (1) AR200477A1 (de)
AT (1) AT310204B (de)
BE (1) BE762543A (de)
CA (1) CA928287A (de)
CH (1) CH541789A (de)
DE (1) DE2103508A1 (de)
ES (1) ES394876A1 (de)
FR (1) FR2108203B1 (de)
GB (1) GB1315055A (de)
LU (1) LU62611A1 (de)
NL (1) NL7100930A (de)
SE (1) SE356124B (de)
ZA (1) ZA71991B (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3835923A (en) * 1972-09-13 1974-09-17 Saab Scania Ab Heat exchanger for fluid media having unequal surface conductances
FR2369526A1 (fr) * 1976-10-28 1978-05-26 Gen Electric Echangeur de chaleur perfectionne pour moteur a turbine a gaz
US4369835A (en) * 1980-05-08 1983-01-25 Bruce J. Landis Thermal energy transfer apparatus and method
US4395976A (en) * 1979-11-26 1983-08-02 Commissariat A L'energie Atomique Heat exchanger
US6354597B1 (en) * 1998-11-26 2002-03-12 Institut Francais Du Petrole Sealed rotating connection device allowing great motions
US20020162652A1 (en) * 1999-10-18 2002-11-07 Andersen Jens Otto Ravn Flue gas heat exchanger and fin therefor
CN101975521A (zh) * 2010-11-07 2011-02-16 上海交通大学 直管间壁式换热器
US20130118421A1 (en) * 2010-07-28 2013-05-16 Sgl Carbon Se Method for protecting heat exchanger pipes in steam boiler systems, moulded body, heat exchanger pipe and steam boiler system
US10139167B1 (en) * 2018-05-17 2018-11-27 Michael W. Courson Heat exchanger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE455813B (sv) * 1982-12-29 1988-08-08 Hypeco Ab Vermevexlare der atminstone kanalen for det ena mediet er uppdelad i ett stort antal stromningsmessigt parallellkopplade kanaler, varvid turbulens undviks

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB188818516A (en) * 1888-12-18 1889-10-19 Improvements in apparatus for utilizing the waste heat of gas engines
US1508860A (en) * 1921-08-22 1924-09-16 Alexander T Stuart Radiator
US2003593A (en) * 1935-02-23 1935-06-04 Duriron Co Heat exchanger
US2185484A (en) * 1938-05-02 1940-01-02 Manufacturers Nat Bank Of Detr Heater
FR851821A (fr) * 1939-03-18 1940-01-16 Perfectionnements aux échangeurs de chaleur
US2451629A (en) * 1943-06-11 1948-10-19 Stewart Warner Corp Sectional hot-air heater
DE800248C (de) * 1948-11-13 1950-10-25 Ludwig Dipl-Ing Kort Rauchheizkoerper
US3407876A (en) * 1966-10-17 1968-10-29 Westinghouse Electric Corp Heat exchangers having plate-type fins
US3477504A (en) * 1967-05-29 1969-11-11 Gen Electric Porous metal and plastic heat exchanger

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1467264A (fr) * 1965-12-17 1967-01-27 élément d'échange thermique

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB188818516A (en) * 1888-12-18 1889-10-19 Improvements in apparatus for utilizing the waste heat of gas engines
US1508860A (en) * 1921-08-22 1924-09-16 Alexander T Stuart Radiator
US2003593A (en) * 1935-02-23 1935-06-04 Duriron Co Heat exchanger
US2185484A (en) * 1938-05-02 1940-01-02 Manufacturers Nat Bank Of Detr Heater
FR851821A (fr) * 1939-03-18 1940-01-16 Perfectionnements aux échangeurs de chaleur
US2451629A (en) * 1943-06-11 1948-10-19 Stewart Warner Corp Sectional hot-air heater
DE800248C (de) * 1948-11-13 1950-10-25 Ludwig Dipl-Ing Kort Rauchheizkoerper
US3407876A (en) * 1966-10-17 1968-10-29 Westinghouse Electric Corp Heat exchangers having plate-type fins
US3477504A (en) * 1967-05-29 1969-11-11 Gen Electric Porous metal and plastic heat exchanger

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3835923A (en) * 1972-09-13 1974-09-17 Saab Scania Ab Heat exchanger for fluid media having unequal surface conductances
FR2369526A1 (fr) * 1976-10-28 1978-05-26 Gen Electric Echangeur de chaleur perfectionne pour moteur a turbine a gaz
US4395976A (en) * 1979-11-26 1983-08-02 Commissariat A L'energie Atomique Heat exchanger
US4369835A (en) * 1980-05-08 1983-01-25 Bruce J. Landis Thermal energy transfer apparatus and method
US6354597B1 (en) * 1998-11-26 2002-03-12 Institut Francais Du Petrole Sealed rotating connection device allowing great motions
US20020162652A1 (en) * 1999-10-18 2002-11-07 Andersen Jens Otto Ravn Flue gas heat exchanger and fin therefor
US20130118421A1 (en) * 2010-07-28 2013-05-16 Sgl Carbon Se Method for protecting heat exchanger pipes in steam boiler systems, moulded body, heat exchanger pipe and steam boiler system
CN101975521A (zh) * 2010-11-07 2011-02-16 上海交通大学 直管间壁式换热器
US10139167B1 (en) * 2018-05-17 2018-11-27 Michael W. Courson Heat exchanger

Also Published As

Publication number Publication date
AT310204B (de) 1973-09-25
NL7100930A (de) 1972-02-23
CH541789A (de) 1973-10-31
SE356124B (de) 1973-05-14
FR2108203A1 (de) 1972-05-19
ES394876A1 (es) 1974-03-01
FR2108203B1 (de) 1976-03-19
CA928287A (en) 1973-06-12
GB1315055A (en) 1973-04-26
LU62611A1 (de) 1971-08-18
DE2103508A1 (de) 1972-02-24
AR200477A1 (es) 1974-11-15
BE762543A (fr) 1971-07-16
ZA71991B (en) 1971-10-27

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