US3785435A - Thermal damper for plate type heat exchangers - Google Patents

Thermal damper for plate type heat exchangers Download PDF

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Publication number
US3785435A
US3785435A US00306968A US3785435DA US3785435A US 3785435 A US3785435 A US 3785435A US 00306968 A US00306968 A US 00306968A US 3785435D A US3785435D A US 3785435DA US 3785435 A US3785435 A US 3785435A
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United States
Prior art keywords
discs
heat exchanger
thermal
plates
thermal damper
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Expired - Lifetime
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US00306968A
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English (en)
Inventor
W Stein
S Straniti
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Avco Corp
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Avco Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another

Definitions

  • Adjacent plates define radial flow paths for the hot gas discharge which alter- 52 U.S. c1 165/76, 165/80, 165/166 i cmss PathS Plan"ms which are [51] Int. Cl F28f 7/00 respectwely connected to the engmes compressor and [58] Field of Search .L 165/164-167, 157, 170 cmbustr hereby iwetsing the energy level. the hot gas stream generated in the combustor.
  • ThlS stack of plates is connected to a frame member of relatively [56]
  • References Cited lalrlgehmass ltthroughl a series totgjtllijermal damlpjer discs w 1c are a erna e y connec e y seam we mg, pe- UNITED STATES PATENTS ripherally around their inner and outer diameters and 3,228,465 l/19 66 Vadot 165/167 then peripherally around openings which fi the 12:23 et plenum passageways for the flow of air from the com- 3:603:38] 9 1971 scherbaiiiii 1:............:::Ill:..
  • the present invention relates to heat exchangers and more particularly to improvements in mounting plate type heat exchangers.
  • a stack of corrugated annular discs defines a central entrance passageway for the hot gas discharge of the engine.
  • the hot gasses pass radially between alternate pairs of discs to a discharge duct.
  • Compressor air enters longitudinally extending plenums and then passes through cross flow paths between other alternate discs to exit plenums connecting with the engines combustor.
  • the discs are corrugated to facilitate the exchange of heat from the hot gas stream to the compressor air passing through the heat exchanger.
  • the waste heat energy of the engine is transferred to the pressurized air in transit between the compressor and combustor of the engine. Transfer of heat in this fashion increases the theoretical efficiency of the engine.
  • the heat exchanger is disposed downstream of the last turbine stage of the engine and must be secured in some fashion to the engine itself.
  • the thin disc of the heat exchanger in some fashion, must be secured to a relatively massive frame element which will surround the discharge flow path of the engine and usually include passageways connecting the plenums of the heat exchanger at the compressor and the combustor of the engine.
  • the thin corrugated discs of the heat exchanger are secured together be welding or the like in bellows fashion. Such discs being alternately joined at the inner and outer peripheries and peripherally of openings which define the referenced plenums. These thin discs have a high rate of. thermal growth,-as compared to the frame member to which they must be joined. During thermal transients a problem arises after repeated thermal cycles, as encountered in normal engine operation, of a failure at or adjacent the juncture between the discs and the frame. Such a failure can then lead to, leakage between the separate flow paths for the hot gas discharge and the pressurized air. Such leakage can lead to losses in engine efficiency or even engine failure.
  • the object of the invention is to provide an improved connection between relatively thin, flow path defining discs, or plates, of a heat exchanger and a mounting frame therefor and more specifically to devise such an improved mounting for heat exchanger discs having an annular configuration.
  • a heat exchanger comprising aseries of relatively thin plates which define alternate flow paths for different fluids between which heat energy is to be exchanged.
  • This series of plates is connected to a frame of relatively large mass and low rate of thermal growth through a thermal damper comprising a series of thermal damper plates which are successively connected to each other with the connection to each thermal damper plate, on opposite sides thereof, being laterally spaced.
  • thermal damper plates have their opposite adjacent surfaces in substantially contiguous relationship and also that the thermal damper plates adjacent the frame have a greater thickness than those adjacent the heat exchanger plates.
  • the heat exchanger plates and the thermal damper plates are in the form of annular discs defining a central passageway for one of the fluids which would be the hot gas discharge of the engine. Further, the heat exchanger discs and the thermal damper discs have inlet and outlet plenum passageways extending therethrough which are defined by openings therein.
  • the alternate flowpaths between the heat exchanger plates comprise cross flow paths between said plenums and radial flow paths communicating with said central passageway.
  • each of the thermal damper discs within the series thereof is joined on one surface to the adjacent discby seam welding peripherally of both its inner and outer diameters and is joined on its opposite surface to the adjacent disc by seam welding peripherally of the plenum defining openings.
  • the adjacent surfaces of the thermal damper plates are disposed in substantially contiguous relationship to prevent a flow of fluid between the surfaces thereof. Also it is preferable that the thermal damper plates adjacent the frame have a thickness greater than those adjacent the heat exchanger plates.
  • the frame would have a conical annular seat throughwhich the plenum opening passageways thereof extend.
  • the thermal damper plates would comprise a part of a thermal damper assembly which includes an annular mounting disc having a seat sealingly engaging the frame seat and also having corresponding plenum passageways or openings therethrough.
  • a thermal damper plate of intermediate thickness, in substantially contiguous relationship with the mounting disc is joined thereto by seam welding peripherally of the passageway openings thereof, successive thermal damper plates are then joined to the intermediate plate, first by seam welding around the inner and outer peripheries thereof and then alternately by seam welding peripherally of the plenum defining openings and the inner and outer diameters.
  • a heat exchanger disc is joined to the last of the thermal discs by seam welding peripherally of the inner and outer diameters thereof.
  • This assembly is completed by a support disc joined to the last of the heat exchanger discs by seam welding peripherally of the inner and outer diameters thereof.
  • the heat exchanger is completed by a series of heat exchanger discs in sub-stacks defined at their opposite ends by support discs. This heat exchanger is then held in assembledrelation by tie rods means which exert an axial loading on the stack of discs relative to the frame and compress same to bring the thermal damper discs or the surfaces thereof into contiguous relationship.
  • thermal mounting assembly for use in a heat exchanger as referenced above.
  • This assembly comprises a plurality of thermal damper discs having plenum passageway openings therethrough.
  • the discs are joined together in pairs by seam welding peripherally of the openings therethrough. These pairs are divergently flared toward their inner and outer diameters which in turn are joined peripherally thereof to adjacent pairs.
  • the thermal damper By forming the thermal damper in this fashion, the welding of the component parts thereof is facilitated.
  • the assembly described is characterized by the fact that when subjected to an axial loading, the adjacent surfaces of the thermal damper plates can be brought into contiguous relationship without any undue stresses being induced therein.
  • FIG. 1 is a longitudinal cross section of a heat exchanger in which the present invention is embodied
  • FIG. 2 is a perspective view, partially exploded, of a stack of plates comprising the present heat exchanger
  • FIG. 3 is a fragmentary perspective view, on a greatly enlarged scale, of a thermal damper assembly for the discs of the heat exchanger prior to installation in the heat exchanger;
  • FIG. 4 is an enlarged longitudinal section of the thermal damper assembly of FIG. 3 after installation in the heat exchanger.
  • the heat exchanger illustrated in FIG. 1 and indicated by reference character 10 is adapted for attachment to a gas turbine engine at a point downstream of its last turbine stage.
  • the engine itself may be of conventional construction inaccordance with well known designs for a regenerative type engine.
  • the hot gas discharge of the engine enters the center of the heat exchanger and then is directed radially outwardly, through a stack of plates, or discs, 1 1, to an exhaust system which includes a surrounding duct 12.
  • the heat exchanger 10 comprises an adaptor frame 14 which may be attached to the load carrying structure of the engine.
  • the adaptor frame 14 has a plurality of passageways l6 and 18 which respectively connect with engine passageways (not shown) leading'from the engine compressor and leading to the engines combustor.
  • the compressor passageways 16 are aligned with a plurality of inlet plenums 20, see also FIG. 2, formed longitudinally through the stack of discs 11.
  • the combustor passageways 18 are aligned with a plurality of exit plenums 22 also extending longitudinally through the stack of discs 11. Radial flow paths for the hot gas discharge and cross flow paths, between adjacent plenums and 22, for the compressor air provide the primary area of heat exchange. These flows are indicated in FIG. 2.
  • the heat exchanger 10 also comprises an end frame 24 and an end disc 26 which define the downstream limit of the hot gas discharge flow path so that all of the hot gasses may be turned radially outwardly through the stack of discs 11 and discharged to the duct 12.
  • the frame 14 and 16 are connected by tie rods 27 to hold the heat exchanger in assembled relation.
  • the heat exchanger discs 11 have flanges peripherally of their inner and outer diameters which alternately project in opposite axial directions so that the discs are disposed in pairs joined at their matching flanges.
  • the discs also have openings which respectively define the plenums 20 and 22.
  • the pairs of discs joined at their flanges are then joined with the next adjacent discs by seam welding or the like, peripherally of the plenum defining openings thus forming a bellows type of construction which defines the referenced flow paths for the radially flowing hot gas discharge and the cross flow of air from the inlet plenums to the exit plenums.
  • These discs are also corrugated, as in the above referenced patent, for increased heat transfer as well as to prove structural strength when the stack of discs is subjected to axial loading through the tie rods 28.
  • the stack of discs 11 may be formed as a series of sub-stacks as taught in U. S. Pat. No. 3,385,353 thus a plurality of discs 11 may be secured to somewhat thicker support discs 32 which also have corresponding plenums defining openings.
  • the support discs 32 are slotted around the peripheries to receive rods 28 which extend between the frames 13 and 24.
  • the stack of discs 11, or series of sub-stacks thereof, connect with the frame 14 through a thermal damper assembly 34 comprising in series relationship (FIG. 4), a mounting disc 36, an intermediate thickness disc 38, a plurality of thermal damper discs 40, a pair of heat exchange discs 11, and a support disc 32.
  • the discs 36, 38 and 40 also have openings corresponding to and aligned with the openings in discs 11, to further define the plenums 20 and 22.
  • FIG. 3 illustrates the thermal damper assembly 34 prior to its incorporation in the heat exchanger.
  • the mounting disc 36 is flanged peripherally of its inner and outer diameters to form a seat for sealingly engaging a correspondingly shaped, annular seat on the frame 14.
  • the disc 36 is joined to the somewhat thinner, intermediate thickness thermal damper disc 38 by seam welding peripherally of the openings defining the plenums 20 and 22.
  • Successive pairs of the thinner thermal damper discs 40 are also joined by seam welding peripherally of their plenum defining openings.
  • Each pair of discs so joined at their openings is joined to the adjacent disc pair by seam welding peripherally of their inner and outer diameters.
  • the inner and outer diameters of the disc pairs,joined at their openings, are divergently flared to facilitate seam welding of the inner and outer diameters of adjacent pairs.
  • the pair of discs 11 are also joined by seam welding peripherally of their plenum defining openings and have divergent flanges to facilitate seam welding of their respective inner and outer diameters to the last thermal damper disc 40 and the support disc 32.
  • the discs 42 are flattened by the compressive forces exerted through the tie rods 28.
  • the flared thermal damper discs are sufficiently'thin that they are not unduly stressed when so flattened.
  • the thermal damper discs thus have their opposite surfaces in contacting or substantially contiguous relation so that there is no gas or air flow therebetween.
  • the heat exchange discs 11 will quickly increase in temperature and will be subject to a relatively rapid thermal growth. This is particularly reflected in the-discs ll of the mounting assembly.
  • the disc 11 and the last thermal damper disc defines a relatively cool, air cross flow path, opposite which is radial flow path for the hot gas discharge.
  • the thermal growth of this disc 11 is then transferred through the succession of thermal damper discs 40 which provide respective increments of thermal growth as the heat transfers, or flows therebetween.
  • thermal damper plates may not be incorporated in a separate assembly or may be joined by other welding procedures such as brazing or the discs may take other plate form.
  • the spirit and scope of the invention is therefore to be derived from the following claims.
  • a heat exchanger comprising a series of relatively thin heat exchange plates which define alternate flow paths for different fluids between which heat energy is to be exchanged
  • thermal mounting interposed between said frame and series of heat exchange plates, said mounting including a series of successively connected, thermal damper plates with the connections between each thermal damper plate within the series thereof being laterally spaced on opposite sides thereof.
  • thermo damper plates are disposed with their adjacent surfaces in substantially contiguous relation.
  • thermal damper plates adjacent the frame have a thickness greater than the thermal damper plates adjacent said heat exchanger plates.
  • thermo damper plates and the thermal damper plates are annular discs and define a central passageway for one of said fluids
  • each thermal damper disc within the series thereof, is joined on one surface to the adjacent disc by seam welding peripherally of both its inner and outer diameters and is joined on its opposite surface to the adjacent disc be seam welding peripherally of said plenum defining openings.
  • the thermal mounting is in the form of an assembly comprising, in series relationship,
  • annular mounting disc having a correspondingly formed seat for sealingly engaging said frame seat and also having corresponding plenum passageways therethrough,
  • thermal damper disc in substantially contiguous relationship therewith and joined thereto by seam welding peripherally of the openings thereof
  • a thermal mounting assembly comprising a plurality of annular, thermal damper discs having aligned passageway openings therethrough and spaced around the central opening thereof,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00306968A 1972-11-15 1972-11-15 Thermal damper for plate type heat exchangers Expired - Lifetime US3785435A (en)

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US30696872A 1972-11-15 1972-11-15

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US (1) US3785435A (fr)
JP (1) JPS5215817B2 (fr)
DE (1) DE2342174C3 (fr)
FR (1) FR2206488B1 (fr)
GB (1) GB1419839A (fr)
IT (1) IT996410B (fr)
SE (1) SE414828B (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3895492A (en) * 1972-12-27 1975-07-22 Kernforschungsanlage Juelich Power plant
US4073340A (en) * 1973-04-16 1978-02-14 The Garrett Corporation Formed plate type heat exchanger
US4134195A (en) * 1973-04-16 1979-01-16 The Garrett Corporation Method of manifold construction for formed tube-sheet heat exchanger and structure formed thereby
US4310960A (en) * 1973-04-16 1982-01-19 The Garrett Corporation Method of fabrication of a formed plate, counterflow fluid heat exchanger and apparatus thereof
EP0077656A1 (fr) * 1981-10-16 1983-04-27 Avco Corporation Echangeur de chaleur du type à plaques
US4993223A (en) * 1989-09-11 1991-02-19 Allied-Signal Inc. Annular recuperator
US5050668A (en) * 1989-09-11 1991-09-24 Allied-Signal Inc. Stress relief for an annular recuperator
US5060721A (en) * 1990-05-29 1991-10-29 Solar Turbines Incorporated Circular heat exchanger
WO1991019152A1 (fr) * 1990-05-29 1991-12-12 Solar Turbines Incorporated Systeme d'etancheite pour un echangeur de chaleur circulaire
US5082050A (en) * 1990-05-29 1992-01-21 Solar Turbines Incorporated Thermal restraint system for a circular heat exchanger
WO1999030099A1 (fr) * 1997-12-10 1999-06-17 Vahterus Oy Echangeur de chaleur a plaques
US5918368A (en) * 1997-08-27 1999-07-06 Solar Turbines, Inc. Method for making a recuperator cell
US6631757B2 (en) * 2000-08-08 2003-10-14 Ballard Power Systems Ag Combined heat exchanger and reactor component
US20040194932A1 (en) * 2003-02-25 2004-10-07 Honeywell International Inc. Solid buffer rods in high temperature heat exchanger
US20170307307A1 (en) * 2016-04-26 2017-10-26 Orbital Atk, Inc. Heat exchangers, weld configurations for heat exchangers and related systems and methods
US20190154348A1 (en) * 2015-07-01 2019-05-23 Alfa Laval Corporate Ab Plate heat exchanger
EP3546873A1 (fr) * 2018-03-29 2019-10-02 Technische Hochshule Mittelhessen Échangeur de chaleur à flux croisé radial
US10612414B2 (en) * 2016-08-22 2020-04-07 United Technologies Corporation Panel based heat exchanger

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111023880A (zh) * 2019-11-05 2020-04-17 浙江大学 一种可拆分组合式换热容器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3228465A (en) * 1960-11-21 1966-01-11 Grenobloise Etude Appl Heat exchanger
US3385353A (en) * 1967-01-31 1968-05-28 Avco Corp Mounting and support for the stacked sheets of a heat exchanger
US3568765A (en) * 1968-11-18 1971-03-09 Basf Ag Plate-type heat exchanger
US3603381A (en) * 1969-03-22 1971-09-07 Siemens Ag Liquid-cooled assembly of disc cells

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3228465A (en) * 1960-11-21 1966-01-11 Grenobloise Etude Appl Heat exchanger
US3385353A (en) * 1967-01-31 1968-05-28 Avco Corp Mounting and support for the stacked sheets of a heat exchanger
US3568765A (en) * 1968-11-18 1971-03-09 Basf Ag Plate-type heat exchanger
US3603381A (en) * 1969-03-22 1971-09-07 Siemens Ag Liquid-cooled assembly of disc cells

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3895492A (en) * 1972-12-27 1975-07-22 Kernforschungsanlage Juelich Power plant
US4073340A (en) * 1973-04-16 1978-02-14 The Garrett Corporation Formed plate type heat exchanger
US4134195A (en) * 1973-04-16 1979-01-16 The Garrett Corporation Method of manifold construction for formed tube-sheet heat exchanger and structure formed thereby
US4310960A (en) * 1973-04-16 1982-01-19 The Garrett Corporation Method of fabrication of a formed plate, counterflow fluid heat exchanger and apparatus thereof
EP0077656A1 (fr) * 1981-10-16 1983-04-27 Avco Corporation Echangeur de chaleur du type à plaques
US4431050A (en) * 1981-10-16 1984-02-14 Avco Corporation Stacked-plate heat exchanger made of identical corrugated plates
US4993223A (en) * 1989-09-11 1991-02-19 Allied-Signal Inc. Annular recuperator
WO1991003695A1 (fr) * 1989-09-11 1991-03-21 Allied-Signal Inc. Recuperateur annulaire
US5050668A (en) * 1989-09-11 1991-09-24 Allied-Signal Inc. Stress relief for an annular recuperator
US5060721A (en) * 1990-05-29 1991-10-29 Solar Turbines Incorporated Circular heat exchanger
WO1991019152A1 (fr) * 1990-05-29 1991-12-12 Solar Turbines Incorporated Systeme d'etancheite pour un echangeur de chaleur circulaire
US5082050A (en) * 1990-05-29 1992-01-21 Solar Turbines Incorporated Thermal restraint system for a circular heat exchanger
US6158121A (en) * 1997-08-27 2000-12-12 Solar Turbines Incorporated Method and apparatus for making a recuperator cell
US5918368A (en) * 1997-08-27 1999-07-06 Solar Turbines, Inc. Method for making a recuperator cell
WO1999030099A1 (fr) * 1997-12-10 1999-06-17 Vahterus Oy Echangeur de chaleur a plaques
US6631757B2 (en) * 2000-08-08 2003-10-14 Ballard Power Systems Ag Combined heat exchanger and reactor component
US20040194932A1 (en) * 2003-02-25 2004-10-07 Honeywell International Inc. Solid buffer rods in high temperature heat exchanger
US6988540B2 (en) * 2003-02-25 2006-01-24 Honeywell International Inc. Solid buffer rods in high temperature heat exchanger
US20190154348A1 (en) * 2015-07-01 2019-05-23 Alfa Laval Corporate Ab Plate heat exchanger
US20170307307A1 (en) * 2016-04-26 2017-10-26 Orbital Atk, Inc. Heat exchangers, weld configurations for heat exchangers and related systems and methods
US11262142B2 (en) * 2016-04-26 2022-03-01 Northrop Grumman Systems Corporation Heat exchangers, weld configurations for heat exchangers and related systems and methods
US20220205742A1 (en) * 2016-04-26 2022-06-30 Northrop Grumman Systems Corporation Aerospace structures comprising heat exchangers, and related heat exchangers and apparatuses
US11768040B2 (en) * 2016-04-26 2023-09-26 Northrop Grumman Systems Corporation Aerospace structures comprising heat exchangers, and related heat exchangers and apparatuses
US10612414B2 (en) * 2016-08-22 2020-04-07 United Technologies Corporation Panel based heat exchanger
EP3546873A1 (fr) * 2018-03-29 2019-10-02 Technische Hochshule Mittelhessen Échangeur de chaleur à flux croisé radial

Also Published As

Publication number Publication date
SE414828B (sv) 1980-08-18
FR2206488B1 (fr) 1979-06-01
JPS4981948A (fr) 1974-08-07
DE2342174C3 (de) 1978-10-19
GB1419839A (en) 1975-12-31
JPS5215817B2 (fr) 1977-05-04
FR2206488A1 (fr) 1974-06-07
DE2342174A1 (de) 1974-05-30
DE2342174B2 (de) 1978-02-16
IT996410B (it) 1975-12-10

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