EP0246942B1 - Tubular heat exchanger having double end plates - Google Patents

Tubular heat exchanger having double end plates Download PDF

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Publication number
EP0246942B1
EP0246942B1 EP87400982A EP87400982A EP0246942B1 EP 0246942 B1 EP0246942 B1 EP 0246942B1 EP 87400982 A EP87400982 A EP 87400982A EP 87400982 A EP87400982 A EP 87400982A EP 0246942 B1 EP0246942 B1 EP 0246942B1
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EP
European Patent Office
Prior art keywords
tubes
heat exchange
plates
plate
rigid
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
EP87400982A
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German (de)
French (fr)
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EP0246942A1 (en
Inventor
Gilbert Duponteil
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Babcock Entreprise
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Babcock Entreprise
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Filing date
Publication date
Application filed by Babcock Entreprise filed Critical Babcock Entreprise
Priority to AT87400982T priority Critical patent/ATE63636T1/en
Publication of EP0246942A1 publication Critical patent/EP0246942A1/en
Application granted granted Critical
Publication of EP0246942B1 publication Critical patent/EP0246942B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0229—Double end plates; Single end plates with hollow spaces

Abstract

A heat exchanger comprises a cylinder and a bundle of heat exchange tubes passing through its interior heat exchange chamber for receiving a hot fluid to be cooled while circulating through the tubes from an inlet to an outlet end. A support for the bundle of heat exchange tubes at each cylinder end comprises a relatively thin, cylinder end closing plate to which respective ends of the heat exchange tubes are affixed, a much thicker, rigid plate affixed to the interior cylinder wall at a distance from the thin plate, the heat exchange tubes passing through bores in the thicker, rigid plate with a clearance, the thin plates and the much thicker, rigid plates defining heat exchange chamber compartments therebetween and another heat exchange chamber compartment extending between the thicker, rigid plates, and rigid tubular sections extending through the heat exchange chamber compartments and interconnecting the thin plate and the much thicker, rigid plate for bracing the plates, the rigid tubular sections concentrically surrounding the ends of the heat exchange tubes whereby annular spaces are defined between the rigid tubular sections and the heat exchange tube ends, the annular spaces being in communication with the clearances, and the rigid tubular sections defining orifices wherethrough the heat exchange chamber compartments communicate with the annular spaces.

Description

L'invention se rapporte aux échangeurs de chaleur du type comportant une calandre munie à chacune de ses extrémités d'un support d'un faisceau de tubes d'échange thermique entre le fluide à refroidir qui circule dans lesdits tubes et un fluide de refroidissement qui circule autour desdits tubes dans la calandre.The invention relates to heat exchangers of the type comprising a calender provided at each of its ends with a support for a bundle of heat exchange tubes between the fluid to be cooled which circulates in said tubes and a cooling fluid which circulates around said tubes in the grille.

Les difficultés de construction posées par ces échangeurs croissent avec la température et la pression du gaz à refroidir et avec la pression de la vapeur du fluide de refroidissement que l'on veut produire, par exemple quand l'échangeur est destiné à la réalisation de chaudières de récupération.La composition du gaz augmente ces difficultés: par exemple, pour le refroidissement des gaz corrosifs de synthèse produits à des températures qui peuvent dépasser 450°C et sous haute pression. Il y a en effet alors risque de corrosion et d'affaiblissement mécanique du matériau qui les constitue et, pour réduire ce risque, il importe de maintenir les tubes à une température nettement plus basse, inférieure à 360°C par exemple.The construction difficulties posed by these exchangers increase with the temperature and the pressure of the gas to be cooled and with the pressure of the vapor of the cooling fluid which it is desired to produce, for example when the exchanger is intended for the production of boilers. The composition of the gas increases these difficulties: for example, for the cooling of corrosive synthesis gases produced at temperatures which can exceed 450 ° C and under high pressure. There is indeed then a risk of corrosion and mechanical weakening of the material which constitutes them and, to reduce this risk, it is important to maintain the tubes at a clearly lower temperature, lower than 360 ° C. for example.

Dans les échangeurs classiques, la plaque qui remplit la fonction de support des tubes doit supporter par ailleurs la forte pression de vapeur du côté de la calandre; elle doit donc avoir une épaisseur importante. Par ailleurs, la plaque d'entrée, en contact avec les tubes dans toute son épaisseur, est fortement chauffée par les gaz et est soumise à des gradients thermiques considérables entre ses deux faces; il peut de plus exister une corrosion importante aux passages des tubes.In conventional exchangers, the plate which fulfills the function of supporting the tubes must also withstand the high vapor pressure on the side of the shell; it must therefore have a significant thickness. Furthermore, the inlet plate, in contact with the tubes throughout its thickness, is strongly heated by gases and is subjected to considerable thermal gradients between its two faces; there may also be significant corrosion in the passage of the tubes.

On est alors conduit à utiliser des aciers spéciaux pour réaliser ou revêtir les plaques, ce qui entraine un coût de fabrication élevé et un poids relativement important.We are then led to use special steels to make or coat the plates, which results in a high manufacturing cost and a relatively large weight.

Pour supprimer ces inconvénients, on a proposé (FR.A.2005156) de constituer le support d'entrée des tubes par deux plaques dont l'une est relativement mince tandis que l'autre est beaucoup plus épaisse et rigide, et des portions de tubes rigides qui entourent concentriquement les portions terminales correspondantes des tubes et forment des espaces annulaires qui communiquent avec une chambre définie par les deux plaques, et dans laquelle est admis le fluide de refroidissement, lesdits espaces annulaires débouchant dans la calandre à travers la plaque intérieure et lesdits tubes traversant cette plaque sans contact.To overcome these drawbacks, it has been proposed (FR.A.2005156) to constitute the inlet support for the tubes by two plates, one of which is relatively thin while the other is much thicker and rigid, and portions of rigid tubes which concentrically surround the corresponding end portions of the tubes and form annular spaces which communicate with a chamber defined by the two plates, and into which the coolant is admitted, said annular spaces opening into the shell through the internal plate and said tubes passing through this contactless plate.

Le but de la présente invention est de proposer une construction plus simple des extrémités dudit échangeur de chaleur assurant une meilleure circulation du fluide de refroidissement sans élévation des gradients thermiques sur la plaque épaisse et évitant les déformations de la plaque mince, notamment au niveau de l'attache des tubes.The object of the present invention is to provide a simpler construction of the ends of said heat exchanger ensuring better circulation of the cooling fluid without elevation of the thermal gradients on the thick plate and avoiding deformations of the thin plate, in particular at the level of the 'attaches tubes.

L'échangeur de chaleur objet de l'invention est caractérisé par le fait que la plaque mince ferme la calandre et sert à la fixation des tubes, que l'autre plaque est fixée à la calandre à une certaine distance de son extrémité fermée, et que les portions de tubes rigides relient les deux plaques en formant des entretoises et sont munies d'orifices faisant communiquer la chambre définie par les deux plaques avec lesdits espaces annulaires.The heat exchanger which is the subject of the invention is characterized in that the thin plate closes the shell and is used for fixing the tubes, that the other plate is fixed to the shell at a certain distance from its closed end, and that the portions of rigid tubes connect the two plates by forming spacers and are provided with orifices making the chamber defined by the two plates communicate with said annular spaces.

D'autres particularités, ainsi que les avantages de l'invention, apparaitront clairement à la lumière de la description ci-après.

  • La figure 1 du dessin annexé représente schématiquement un échangeur à faisceau de tubes droits conforme à un mode d'exécution préféré de l'invention; et
  • La figure 2 montre, à plus grande échelle, le détail des fixations des tubes sur les plaques.
Other special features, as well as the advantages of the invention will become clear in the light of the description below.
  • Figure 1 of the accompanying drawing schematically shows a straight tube bundle exchanger according to a preferred embodiment of the invention; and
  • Figure 2 shows, on a larger scale, the detail of the tube attachments on the plates.

A la figure 1, on a représenté un échangeur tubulaire composé d'une calandre allongée 1 munie au voisinage de ses extrémités de deux plaques 2 et 3 et logeant un faisceau de tubes tels que 4.In FIG. 1, there is shown a tubular exchanger composed of an elongated calender 1 provided in the vicinity of its ends with two plates 2 and 3 and housing a bundle of tubes such as 4.

On voit que les tubes 4 traversent avec jeu les plaques 2 et 3 et se prolongent jusqu'à leur extrémité de fixation dans deux plaques minces supplémentaires 5 et 6 qui ferment la calandre, à l'exception des passages d'entrée et de sortie des tubes 4. Des tubes 7-8 formant entretoises entre les plaques mince et épaisse entourent concentriquement chacun des tubes 4 à ses deux portions terminales comprises entre les paires de plaques 2-5 d'une part, 3-6 d'autre part. L'intervalle annulaire entre les tubes 4 et les tubes 7 et 8 comporte des ouvertures 70-80 disposées à proximité des plaques 5-6 et 2-3, de manière à assurer un refroidissement convenable.It can be seen that the tubes 4 cross the plates 2 and 3 with play and extend to their fixing end in two additional thin plates 5 and 6 which close the grille, with the exception of the inlet and outlet passages of the tubes 4. Tubes 7-8 forming spacers between the thin and thick plates concentrically surround each of the tubes 4 at its two end portions comprised between the pairs of plates 2-5 on the one hand, 3-6 on the other. The annular gap between the tubes 4 and the tubes 7 and 8 has openings 70-80 arranged near the plates 5-6 and 2-3, so as to ensure proper cooling.

La figure 2 montre comment les tronçons de tube 7-8 sont fixés à leurs deux extrémités aux plaques 2-3 et 5-6, par des cordons de soudure 20, 22 et comment les tubes 4 sont fixés aux plaques 5-6 pur des cordons de soudure 24 qui les réunissent aux extrémités adjacentes des tronçons de tubes 7-8. D'autres moyens classiques pourraient éventuellement être utilisés pour fixer les tronçons de tube 7, 8 aux plaques 2-3.Figure 2 shows how the tube sections 7-8 are fixed at their two ends to the plates 2-3 and 5-6, by weld beads 20, 22 and how the tubes 4 are fixed to the plates 5-6 for weld beads 24 which join them to the adjacent ends of the sections of tubes 7-8. Other conventional means could possibly be used to fix the tube sections 7, 8 to the plates 2-3.

Les plaques 2 et 3 ont une forte épaisseur, par exemple 250 mm, suffisante pour résister à l'effet de fond créé par la pression du fluide contenu dans la calandre, tandis que les plaques 5 et 6 ont par exemple une épaisseur de 10 à 20 mm et servent à supporter les tubes qui sont soudés auxdites plaques minces. Le diamètre de l'échangeur est par exemple de 900 mm. Les plaques 5-6 sont munies d'une bride de montage périphérique 51-61.The plates 2 and 3 have a large thickness, for example 250 mm, sufficient to withstand the background effect created by the pressure of the fluid contained in the calender, while the plates 5 and 6 have for example a thickness of 10 to 20 mm and are used to support the tubes which are welded to said thin plates. The diameter of the exchanger is for example 900 mm. The plates 5-6 are provided with a peripheral mounting flange 51-61.

Le fluide de refroidissement, eau par exemple, pénètre par un conduit 9 dans l'intervalle (ayant par exemple 150 mm de hauteur) compris entre les plaques 2 et 5 (représentées en bas de la figure 1, l'échangeur étant ici supposé vertical). Les tubes 7 présentent des ouvertures telles que 70 si bien que le fluide pénètre, par l'intervalle annulaire 30 (de 3 à 10 mm d'épaisseur par exemple) compris entre les tubes 4 et 7, dans la partie de la calandre comprise entre les plaques 2 et 3. Sa circulation est assurée par une pompe ou par effet de thermosiphon.The cooling fluid, water for example, enters through a conduit 9 in the interval (having for example 150 mm in height) between the plates 2 and 5 (shown at the bottom of FIG. 1, the exchanger here being assumed to be vertical ). The tubes 7 have openings such as 70 so that the fluid penetrates, through the annular gap 30 (from 3 to 10 mm thick for example) comprised between the tubes 4 and 7, in the part of the calender comprised between plates 2 and 3. Its circulation is ensured by a pump or by effect thermosyphon.

Le gaz à refroidir pénètre dans les tubes 4 au niveau de la plaque 5 et l'eau se trouve vaporisée au contact de la plaque 5 ainsi chauffée par le gaz. La vapeur d'eau pénètre dans les tubes 7 par les ouvertures 70 et le mélange eau-vapeur refroidit les tubes 4.The gas to be cooled enters the tubes 4 at the level of the plate 5 and the water is vaporized on contact with the plate 5 thus heated by the gas. The steam enters the tubes 7 through the openings 70 and the water-steam mixture cools the tubes 4.

A l'extrémité supérieure de la calandre, la structure étant la même qu'à l'extrémité inférieure, les gaz refroidi s'évacue par les tubes 4 à travers la plaque 6, tandis que le mélange eau-vapeur réchauffé s'évacue par l'intervalle annulaire compris entre les tubes 4 et 8, les ouvertures 80 des tubes 8 et un conduit de sortie 10.At the upper end of the grille, the structure being the same as at the lower end, the cooled gases are evacuated by the tubes 4 through the plate 6, while the heated water-vapor mixture is evacuated by the annular gap between the tubes 4 and 8, the openings 80 of the tubes 8 and an outlet conduit 10.

Dans le mode d'exécution non limitatif décrit, il existe en 11 une amenée complémentaire de fluide de refroidissement à l'intérieur de la calandre au-dessus de la plaque 2 et en 12 une évacuation complémentaire. On peut ainsi faire pénétrer en 9 la quantité de liquide juste nécessaire pour assurer le refroidissement de l'espace compris entre les plaques 2 et 5 et de la portion des tubes 4 comprise entre la plaque 5 et la face intérieure (supérieure) de la plaque 2, et n'évacuer de même en 10 que l'excédent de vapeur non évacuée en 12.In the non-limiting embodiment described, there is at 11 an additional supply of cooling fluid inside the calender above the plate 2 and at 12 an additional discharge. It is thus possible to introduce in 9 the quantity of liquid just necessary to ensure the cooling of the space between the plates 2 and 5 and of the portion of the tubes 4 between the plate 5 and the inner (upper) face of the plate 2, and in the same way evacuate in 10 only the excess vapor not evacuated in 12.

On notera que, grâce à la structure à deux plaques entretoisées par des tubes décrite, des pressions de mélange eau-vapeur très élevées (par exemple de 100 à 150 bars) peuvent être supportées sans déformation des plaques épaisses. Les plaques minces, munies de brides de montage (51-61) peuvent subir une légère flexion sans inconvénient, celle-ci ne se produisant pas au niveau de l'attache des tubes. Elles se maintiennent à basse température grâce à leur faible épaisseur.It will be noted that, thanks to the structure with two plates braced by tubes described, mixing pressures very high water vapor (for example from 100 to 150 bar) can be supported without deformation of the thick plates. Thin plates, provided with mounting flanges (51-61) can undergo a slight bending without inconvenience, this does not occur at the attachment of the tubes. They are kept at low temperature thanks to their thin thickness.

Les plaques épaisses ne sont pas soumises à des gradients thermiques, le mélange eau-vapeur régnant (à des températures qui peuvent atteindre 300 à 350°C) sur leurs deux faces et aucun contact avec les tubes où circule le gaz à refroidir (qui peut avoir des températures allant de 600 à 1100°C sous des pressions de 200 bars) n'existant.The thick plates are not subjected to thermal gradients, the water-vapor mixture prevailing (at temperatures which can reach 300 to 350 ° C) on their two faces and no contact with the tubes where the gas to be cooled circulates (which can have temperatures ranging from 600 to 1100 ° C under pressures of 200 bar) not existing.

Les tubes sont refroidis sur toute leur longueur, y compris à leur passage à travers les plaques épaisses si bien que le risque de corrosion ou d'affaiblissement mécanique par le gaz est partiquement supprimé.The tubes are cooled over their entire length, including when they pass through the thick plates so that the risk of corrosion or mechanical weakening by the gas is partially eliminated.

Il est évident que les problèmes de gradient thermique et de corrosion étant plus importants à l'entrée qu'à la sortie, la structure à double plaque est indispensable à l'entrée, tandis qu'elle pourra être remplacée à la sortie par une structure classique, dans certains cas.It is obvious that the problems of thermal gradient and corrosion being more important at the entry than at the exit, the double plate structure is essential at the entry, while it can be replaced at the exit by a structure classic in some cases.

L'invention s'applique à tous les types de faisceaux de tubes.The invention applies to all types of tube bundles.

Claims (4)

1. Heat exchanger comprising a shell provided at each one of its ends with a support for a nest of tubes for heat exchange between the fluid to be cooled which circulates within the said tubes and a cooling fluid which circulates around the said tubes within the shell, at least the inlet support of the tubes being constituted by two plates one of which is relatively thin whereas the other one is much thicker and stiff, and rigid tube portions which concentrically surround the corresponding end portions of the tubes and form annular spaces which communicate with a chamber defined by both plates, the said annular spaces opening into the shell through the inner plate and the said tubes extending through this plate without contact, characterized by the fact that the thin plate (5) closes off the shell (1) and serves to the fastening of the tubes (4), and that the other plate (2) is fastened to the shell at a certain distance from its closed end and that the rigid tube portions (7) connect both plates while forming spacers and are provided with openings (70) for making the said annular spaces.
2. Heat exchanger according to claim 1, characterized by an additional feed (11) for the cooling fluid into the shell.
3. Heat exchanger according to claim 1, characterized in that the outlet support of the tubes is designed like the inlet support, an outlet piping for the cooling fluid (10) being connected to the chamber defined between both plates (3, 6) of the said outlet support and in that an additional feed of cooling fluid (11) and an additional vapour discharge (12) are provided in the vicinity of the thick plates (2, 3) within the shell portion lying between both thick plates.
4. Heat exchanger according to claim 1, 2 or 3, characterized in that the thin plate(s) (5, 6) is or are provided with a peripheral mounting flange (51, 61).
EP87400982A 1986-05-21 1987-04-29 Tubular heat exchanger having double end plates Expired - Lifetime EP0246942B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87400982T ATE63636T1 (en) 1986-05-21 1987-04-29 TUBE BUNDLE HEAT EXCHANGER WITH DOUBLE WALL TUBE SHEET.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8607193A FR2599133B1 (en) 1986-05-21 1986-05-21 TUBULAR HEAT EXCHANGER WITH DOUBLE TUBE BEAM SUPPORT PLATE
FR8607193 1986-05-21

Publications (2)

Publication Number Publication Date
EP0246942A1 EP0246942A1 (en) 1987-11-25
EP0246942B1 true EP0246942B1 (en) 1991-05-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP87400982A Expired - Lifetime EP0246942B1 (en) 1986-05-21 1987-04-29 Tubular heat exchanger having double end plates

Country Status (6)

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US (1) US4770239A (en)
EP (1) EP0246942B1 (en)
JP (1) JPS62288496A (en)
AT (1) ATE63636T1 (en)
DE (1) DE3770047D1 (en)
FR (1) FR2599133B1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19714423C2 (en) * 1997-04-08 2003-05-08 Schnabel Gmbh & Co Kg Dr Shell and tube heat exchangers

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3715712C1 (en) * 1987-05-12 1988-07-21 Borsig Gmbh Heat exchanger especially for cooling cracked gas
DE3820494C2 (en) * 1988-06-16 1994-05-19 Balcke Duerr Ag Heat exchanger
DE4404068C1 (en) * 1994-02-09 1995-08-17 Wolfgang Engelhardt Heat exchanger
DE4407594A1 (en) * 1994-03-08 1995-09-14 Borsig Babcock Ag Heat exchanger for cooling hot reaction gas
DE4445687A1 (en) * 1994-12-21 1996-06-27 Borsig Babcock Ag Heat exchanger for cooling cracked gas
DE19501422C2 (en) * 1995-01-19 2002-03-28 Borsig Gmbh Cooled transition piece between a heat exchanger and a reactor
JP4451520B2 (en) * 1999-11-08 2010-04-14 株式会社日本触媒 Vertical heat exchanger
KR100705482B1 (en) * 2000-11-10 2007-04-10 한라공조주식회사 Heat exchanger
ES2331082T3 (en) * 2004-05-25 2009-12-21 Shell Internationale Research Maatschappij B.V. APPARATUS TO COOL A HOT GAS MEDIUM.
JP4966834B2 (en) * 2007-11-30 2012-07-04 成雄 安藤 High-pressure homogenizer cooling device
US8672021B2 (en) * 2010-02-12 2014-03-18 Alfred N. Montestruc, III Simplified flow shell and tube type heat exchanger for transfer line exchangers and like applications
CN102997217B (en) * 2012-12-12 2014-07-09 江苏焱鑫科技股份有限公司 Protective lining structure for flexible tube plate of vertical waste heat boiler
CN105115324A (en) * 2015-09-15 2015-12-02 温州天旭机械设备有限公司 Multitubular cooler
CN108362155A (en) * 2018-02-08 2018-08-03 王萍 A kind of industrial waste gas heat-energy secondary based on hot swapping utilizes device

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1809915A (en) * 1930-08-13 1931-06-16 Westinghouse Electric & Mfg Co Condenser
US2145877A (en) * 1935-08-07 1939-02-07 Houdry Process Corp Apparatus for thermal control of contact masses
DE684736C (en) * 1938-02-25 1939-12-04 Atlas Werke Ag Tubular heat exchanger with two sealing tube bases arranged at a distance from one another
US3356135A (en) * 1964-12-24 1967-12-05 Robert K Sayre Once-through steam generator with means to provide saturated feed water
DE1817043A1 (en) * 1968-03-30 1970-10-08 Basf Ag Tube sheet for hot gas cooler for high differential pressures
NL6919308A (en) * 1968-12-27 1970-06-30
US3907026A (en) * 1973-08-21 1975-09-23 Westinghouse Electric Corp Double tube heat exchanger
NL159782B (en) * 1976-10-21 1979-03-15 Neratoom PIPE PLATE INCLUDING TWO SPACED PLATE PARTS; HEAT EXCHANGER CONTAINING AT LEAST SUCH PIPE PLATE.
US4100227A (en) * 1977-04-04 1978-07-11 The Dow Chemical Company Transparent impact-resistant polystyrene structure
GB1586935A (en) * 1977-06-28 1981-03-25 Westinghouse Electric Corp Heat exchanger with double wall tubes and three tube sheets
NL7905640A (en) * 1978-09-14 1980-03-18 Borsig Gmbh HEAT EXCHANGER PROVIDED WITH A PIPE BUNDLE.
JPS6042843B2 (en) * 1979-07-30 1985-09-25 東洋エンジニアリング株式会社 Waste heat boiler
FR2499212A1 (en) * 1981-02-02 1982-08-06 Commissariat Energie Atomique DEVICE FOR PROTECTING THE TUBULAR PLATE AT THE HOT END OF A VERTICAL HEAT EXCHANGER

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19714423C2 (en) * 1997-04-08 2003-05-08 Schnabel Gmbh & Co Kg Dr Shell and tube heat exchangers

Also Published As

Publication number Publication date
DE3770047D1 (en) 1991-06-20
FR2599133A1 (en) 1987-11-27
JPH0456238B2 (en) 1992-09-07
ATE63636T1 (en) 1991-06-15
JPS62288496A (en) 1987-12-15
US4770239A (en) 1988-09-13
EP0246942A1 (en) 1987-11-25
FR2599133B1 (en) 1990-09-21

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