EP0246942A1 - Tubular heat exchanger having double end plates - Google Patents

Tubular heat exchanger having double end plates Download PDF

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Publication number
EP0246942A1
EP0246942A1 EP87400982A EP87400982A EP0246942A1 EP 0246942 A1 EP0246942 A1 EP 0246942A1 EP 87400982 A EP87400982 A EP 87400982A EP 87400982 A EP87400982 A EP 87400982A EP 0246942 A1 EP0246942 A1 EP 0246942A1
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EP
European Patent Office
Prior art keywords
tubes
plates
heat exchange
rigid
plate
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Granted
Application number
EP87400982A
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German (de)
French (fr)
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EP0246942B1 (en
Inventor
Gilbert Duponteil
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Babcock Entreprise
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Babcock Entreprise
STRUTHERS WELLS SA
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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
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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
    • 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

Definitions

  • the invention relates to heat exchangers of the type comprising a calender provided at at least one end 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.
  • 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.
  • 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 can also be significant corrosion at the passage of the tubes.
  • the invention proposes to overcome these drawbacks by constituting at least the inlet support for the tubes by two plates, one of which, which closes the grille, is relatively thin and is used for fixing the tubes, while the other, much thicker and more rigid, is fixed inside the grille at a certain distance from its closed end and connected to the previous one by portions of rigid tubes concentrically surrounding the corresponding terminal portions of the tubes and forming spacers, the chamber defined by the two plates and the calender comprising a coolant supply duct and said rigid tube portions being provided with holes for penetration of said fluid in the annular spaces between said rigid tube portions and the corresponding end portions of the tubes, spaces which are extended by annular intervals between the tubes and the thick plate which they pass through without contact.
  • FIG. 1 of the accompanying drawing schematically shows a straight tube bundle exchanger according to a preferred embodiment of the invention.
  • Figure 2 shows, on a larger scale, the detail of the tube attachments on the plates.
  • 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.
  • 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.
  • 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 by 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.
  • the plates 2 and 3 have a large thickness, for example 250mm, sufficient to withstand the background effect created by the pressure of the fluid contained in the grille, while the plates 5 and 6 have for example a thickness of 10 to 20mm and serve to support the tubes which are welded to said thin plates.
  • the diameter of the exchanger is for example 900mm.
  • the plates 5-6 are provided with a peripheral mounting flange 51-61.
  • the cooling fluid enters through a conduit 9 in the interval (having for example 150mm 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 in thickness for example) comprised between the tubes 4 and 7, in the part of the shell comprised between the plates 2 and 3. Its circulation is ensured by a pump or by effect thermosyphon.
  • 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.
  • 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.
  • the thick plates are not subjected to thermal gradients, the water-vapor mixture prevailing (at temperatures which can reach 300 to 350 P C) on their two faces and no contact with the tubes where circulates the gas to be cooled (which can have temperatures ranging from 600 to 1100 ° C under pressures of 200 bar) not existing.
  • 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.
  • the double plate structure is essential at the entry, while it can be replaced at the exit by a structure classic in some cases.

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 au moins une extrémité 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 at least one end 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. In addition, 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 can also be significant corrosion at 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.

L'invention propose de supprimer ces inconvénients en constituant au moins le support d'entrée des tubes par deux plaques dont l'une, qui ferme la calandre, est relativement mince et sert à la fixation des tubes, tandis que l'autre, beaucoup plus épaisse et rigide, est fixée à l'intérieur de la calandre à une certaine distance de son extrémité fermée et reliée à la précédente par des portions de tubes rigides entourant concentriquement les portions terminales correspondantes des tubes et formant entretoises, la chambre définie par les deux plaques et la calandre comportant un conduit d'amenée du fluide de refroidissement et lesdites portions de tubes rigides étant munies d'orifices de pénétration dudit fluide dans les espaces annulaires entré lesdites portions de tubes rigides et les portions terminales correspondantes des tubes, espaces qui se prolongent par des intervalles annulaires entre les tubes et la plaque épaisse qu'ils traversent sans contact.The invention proposes to overcome these drawbacks by constituting at least the inlet support for the tubes by two plates, one of which, which closes the grille, is relatively thin and is used for fixing the tubes, while the other, much thicker and more rigid, is fixed inside the grille at a certain distance from its closed end and connected to the previous one by portions of rigid tubes concentrically surrounding the corresponding terminal portions of the tubes and forming spacers, the chamber defined by the two plates and the calender comprising a coolant supply duct and said rigid tube portions being provided with holes for penetration of said fluid in the annular spaces between said rigid tube portions and the corresponding end portions of the tubes, spaces which are extended by annular intervals between the tubes and the thick plate which they pass through without contact.

D'autres particularités, ainsi que les avantages de l'invention, apparaîtront clairement à la lumière de la description ci-après.Other special features, as well as the advantages of the invention will become clear in the light of the description below.

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 ; etFigure 1 of the accompanying drawing schematically shows a straight tube bundle exchanger according to a preferred embodiment of the invention; and

La figure 2 montre, à plus grande échelle, le détail des fixations des tubes sur les plaques.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 par 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 by 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 250mm, 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 20mm et servent à supporter les tubes qui sont soudés auxdites plaques minces. Le diamètre de l'échangeur est par exemple de 900mm. 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 250mm, sufficient to withstand the background effect created by the pressure of the fluid contained in the grille, while the plates 5 and 6 have for example a thickness of 10 to 20mm and serve to support the tubes which are welded to said thin plates. The diameter of the exchanger is for example 900mm. 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 150mm 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 10mm 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 150mm 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 in thickness for example) comprised between the tubes 4 and 7, in the part of the shell comprised between the 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 350PC) 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 P C) on their two faces and no contact with the tubes where circulates the gas to be cooled (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.

Il va de soit que diverses modifications pourront être apportées au dispositif décrit et représenté, sans s'écarter de l'esprit de l'invention. En particulier, l'invention s'applique à tous les types de faisceaux de tubes.It goes without saying that various modifications may be made to the device described and shown, without departing from the spirit of the invention. In particular, the invention applies to all types of tube bundles.

Claims (4)

1. Echangeur de chaleur comportant une calandre (1) munie à chacune de ses extrémités d'un support d'un faisceau de tubes (4) 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, au moins le support d'entrée des tubes étant constitué par deux plaques dont l'une (5), qui ferme la calandre, est relativement mince et sert à la fixation des tubes tandis que l'autre (2), beaucoup plus épaisse et rigide, est fixée à l'intérieur de la calandre à une certaine distance de son extrémité fermée, caractérisé en ce que les deux plaques (2 , 5) sont reliées l'une à l'autre par des portions de tubes rigides (7) entourant concentriquement les portions terminales correspondantes des tubes (4) et formant entretoises, en ce que les dites portions de tubes rigides sont munies d'orifices (70) faisant communiquer la chambre définie par les deux plaques (2, 5) avec les espaces annulaires formés entre lesdites portions de tubes rigides et lesdites portions terminales correspondantes des tubes (4), et en ce que lesdits espaces annulaires débouchent dans la calandre (1) à travers la plaque épaisse (2), lesdits tubes (4) traversant cette plaque sans contact, pour permettre la circulation dans lesdits espaces annulaires d'un fluide de refroidissement admis par un conduit (9) dans ladite chambre.1. Heat exchanger comprising a shell (1) provided at each of its ends with a support for a bundle of tubes (4) for heat exchange between the fluid to be cooled which circulates in said tubes and a cooling fluid which circulates around said tubes in the shell, at least the tube inlet support being constituted by two plates, one of which (5), which closes the shell, is relatively thin and is used for fixing the tubes while the other (2), which is much thicker and more rigid, is fixed inside the grille at a certain distance from its closed end, characterized in that the two plates (2, 5) are connected to each other by portions of rigid tubes (7) concentrically surrounding the corresponding end portions of the tubes (4) and forming spacers, in that said portions of rigid tubes are provided with orifices (70) making the chamber defined by the two plates communicate ( 2, 5) with the annular spaces formed between said portions of rigid tubes and said corresponding end portions of tubes (4), and in that said annular spaces open into the shell (1) through the thick plate (2), said tubes (4) passing through this plate without contact, to allow the circulation in said annular spaces of a cooling fluid admitted by a conduit (9) in said chamber. 2. Echangeur de chaleur selon la revendication 1, caractérisé par une amenée supplémentaire (11) du fluide de refroidissement dans la calandre.2. Heat exchanger according to claim 1, characterized by an additional supply (11) of the cooling fluid in the shell. 3. Echangeur de chaleur selon la revendication 1, caractérisé en ce que le support de sortie des tubes est conçu comme le support d'entrée, un conduit de sortie du fluide de refroidissement (10) étant raccordé à la chambre définie entre les deux plaques (3, 6) dudit support de sortie, et en ce qu'une amenée de fluide de refroidissement supplémentaire (11) et une évacuation de vapeur supplémentaire (12) sont prévues au voisinage des plaques épaisses (2, 3) dans la portion de calandre comprise entre les plaques épaisses.3. Heat exchanger according to claim 1, characterized in that the outlet support of the tubes is designed as the inlet support, an outlet duct for the coolant (10) being connected to the chamber defined between the two plates (3, 6) of said outlet support, and in that an additional coolant supply (11) and an additional steam outlet (12) are provided in the vicinity of the thick plates (2, 3) in the portion of grille between the thick plates. 4. Echangeur de chaleur selon la revendication 1, 2 ou 3, caractérisé en ce que la ou les plaques minces (5, 6) sont munies d'une bride périphérique de montage (51, 61).4. Heat exchanger according to claim 1, 2 or 3, characterized in that the thin plate or plates (5, 6) 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 true EP0246942A1 (en) 1987-11-25
EP0246942B1 EP0246942B1 (en) 1991-05-15

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EP87400982A Expired - Lifetime EP0246942B1 (en) 1986-05-21 1987-04-29 Tubular heat exchanger having double end plates

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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)

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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
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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
CN105115324A (en) * 2015-09-15 2015-12-02 温州天旭机械设备有限公司 Multitubular cooler

Also Published As

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JPH0456238B2 (en) 1992-09-07
US4770239A (en) 1988-09-13
FR2599133B1 (en) 1990-09-21
DE3770047D1 (en) 1991-06-20
JPS62288496A (en) 1987-12-15
ATE63636T1 (en) 1991-06-15
FR2599133A1 (en) 1987-11-27
EP0246942B1 (en) 1991-05-15

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