US3563303A - Method and apparatus for increasing uniformity of heat transfer - Google Patents

Method and apparatus for increasing uniformity of heat transfer Download PDF

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Publication number
US3563303A
US3563303A US785491A US3563303DA US3563303A US 3563303 A US3563303 A US 3563303A US 785491 A US785491 A US 785491A US 3563303D A US3563303D A US 3563303DA US 3563303 A US3563303 A US 3563303A
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United States
Prior art keywords
tubes
tubular means
medium
tubular
throttling
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Expired - Lifetime
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US785491A
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English (en)
Inventor
Paul Viktor Gilli
Kurt Fritz
Walter Roznovsky
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Waagner Biro AG
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Waagner Biro AG
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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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/38—Determining or indicating operating conditions in steam boilers, e.g. monitoring direction or rate of water flow through water tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/62—Component parts or details of steam boilers specially adapted for steam boilers of forced-flow type
    • F22B37/70—Arrangements for distributing water into water tubes
    • F22B37/74—Throttling arrangements for tubes or sets of 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • F28D7/082—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 otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration
    • F28D7/085—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 otherwise bent, e.g. in a serpentine or zig-zag with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
    • 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
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet

Definitions

  • SHEET 2 0F 3 1' A/ MIN 76/? 5 mm mm? fl/LL WA fE-R jaw R0 NoVsK y ATENTEU FEB I 6 I97! SHEET 0F 3 BACKGROUND OF THE INVENTION
  • the present invention relates to a method and apparatus for increasing the uniformity of heat transfer in heat exchangers.
  • the heat exchanger has a plurality of tubular means respectively provided with inlet and outlet ends.
  • the medium which is to be heated is directed through the plurality of tubular means in such a way that the temperature of this medium at the outlet ends of the tubular means is substantially uniform. in accordance with the invention, this result is achieved by throttling the flow of the medium which is to be heated into the inlet ends of the plurality of tubular means in such a way that this medium will have a uniform temperature at the outlet ends.
  • Each tubular means may take the form of a single tube or a group of tubes.
  • throttling at the inlet ends of the plurality of tubular means is brought about by a throttling means which preferably takes the formof a suitably apertured plate having throttling apertures which respectively communicate with these inlet ends.
  • the aperture plate has throttling apertures which respectively have such a size that the extent of flow of medium through tubes in the immediate vicinity of those which no longer operate is greater than the extent of flow through the tubes which are more distant from the part of the tubes which have been rendered inoperative.
  • Temperature measurements are carried out at the individual outlet ends of the plurality of operating tubular means for determining the temperatures at these several outlet ends, respectively, and in accordance with the latter temperatures a given throttling means is situated at the inlet ends to achieve the uniform temperature at the outlet ends.
  • the apertured throttling plates can have at the inlet ends immediately adjacent those tubes which no longer operate throttling apertures which are greater than more distant throttling apertures either absolutely or with respect to the latter apertures.
  • the lesser extent of throttling is provided at those tubes which surround any inoperative tube or tubes.
  • the lesser extent of throttling is provided at those tubes situated in the direction of flow of the medium which gives up its heat as well as, to a lesser extent, at those tubes which are in the immediate vicinity of any damaged tubes which no longer operate.
  • a throttling means is situated at the inlet ends of the plurality of tubular means to throttle the flow of the heated medium through the plurality of tubular means in a manner determined by the discharge temperatures at the outlet ends of the plurality of tubular means for regulating the flow of the heated medium through the operating tubes to achieve uniform temperatures at the outlet ends of the tubular means.
  • the throttling means preferably takes the form of an apertured plate which is situated in front of an inlet plate to which the inlet ends of the several tubular means are connected.
  • thermocouple means situated in accordance with the invention at the region of an outlet plate to which these outlet ends are connected, and the thermocouple means is capable of measuring the temperature of the medium which discharges at the outlet ends of the individual tubular means.
  • FIG. I is a partly sectional schematic elevation of a heat exchanger having helical heat-exchanging tubes
  • FIG. 2 is a schematic sectional elevation of that type of heat exchanger where the tubes are respectively arranged in planes to form partition walls in the heatexchanger;
  • FIG. 3 is a fragmentary longitudinal sectional elevation schematically illustrating one embodiment of a throttling DESCRIPTION OF PREFERRED EMBODIMENTS
  • the heat-exchanger installation illustrated therein includes a plurality of helical tubular means through which the medium to be heated flows.
  • the plurality of tubular means are in the form of individual helical tubes 5 which define tube cylinders I4.
  • the tube cylinder 1 is surrounded by the tube cylinder 2 which is itself surrounded by the tube cylinder 3, and this latter tube cylinder is, of course, surrounded by the outer tube cylinder 4.
  • Each of these cylinders is defined by a plurality of helical tubes 5 having convolutions of the same diameter.
  • each tube cylinder has convolutions of the smallest diameter
  • the tubes which define the cylinder 4 have convolutions of the largest diameter
  • the cylinders 2 and .3 have tubes of corresponding diameters between those of the cylinders l and 4.
  • each tube cylinder is composed of a given number of parallel-connected helical tubes all ofwhich are of equal length.
  • the heating medium in the form of a hot gas, enters at the top of the installation through the gas inlet 6, and heat is extracted from the hot gas entering through the inlet 6 to generate steam.
  • the heat is extracted from the gas through the walls of the helical tubes 5, and the cooled gas leaves the steam generator at the lower outlet 7 thereof.
  • the installation is situated within the elongated housing 8 which has the inlet 6 at its top end and the outlet 7 at its bottom end.
  • the number of parallel-connected tubes 5 in the several tube cylinders l--4 is different in the respect 'of cylinders.
  • the outer cylinder 4 which has the largest diameter there will be more parallel-connected tubes than in the remaining tube cylinders which successively have decreasing numbers of tubes from the outer to the inner cylinder 1, the latter of course having the smallest number of tubes.
  • the difference between the numbers of tubes of the several cylinders is such that the longitudinal pitch of all of the helical tubes 5 is identical for all of these tubes in the several cylinders l-4.
  • the feedwater flows from the feedwater inlet I5 into the supply chamber l3where the feedwater is collected. At this chamber 13 the feedwater has access to an inlet plate ll formed with bores which receive the inlet ends of the plurality of tubular means 5.
  • the throttling means of the invention is situated in front of this inlet plate 11 and the several tubular means 5 include, in addition to the helical portions thereof. the tubular extensions 9 respectively communicating with the several helical tubes and terminating in the bores of the inlet plate 11 in which the inlet ends of the extensions 9 are received in a fluidtight manner.
  • a communication is made with the feedwaterwhich is preheated, heated. converted into steam, and superheated within the helical tubes 5.
  • the live steam discharges from the plurality of tubular means 5 into tubular extensions 10 respectively communicating with and extending from the tubular means 5 and received in bores of an outlet plate 12 where the outlet ends of several tubular means are located, these outlet ends being defined by the outlet ends of the extensions 10 of the several tubular means.
  • the live steam will flow from the helical tubes 5 respectively through the extensions 10 thereof and the outlet plate 12, which fluidtightly receives the extensions 10 in bores of the plate 12, respectively, into the live-steam collecting chamber 14, from which the live steam flows to the conduit 16.
  • the outer cylindrical housing 8 for the entire installation is capable of withstanding high pressure and is suitable for use with gas at high pressure, particularly with gas issuing from a nuclear reactor.
  • the several tubular means are respectively arranged in planes so that the assemblies of tubular means form partition-walls.
  • several bundles 17 of individual tubular means are assembled together to form a partition wall such as that which is schematically illustrated in FIG. 2.
  • the several tubes are curved so as to have horizontal portions extending back and forth in the manner shown in FIG. 2. Therefore, while with the embodiment of FIG. 2 the downwardly flowing heating gas will flow transversely across the horizontally extending portions of the several tubular means 17, in the embodiment of FIG. I the downwardly flowing heating gas will flow transversely across the helically extending portions of the several tubular means 5.
  • FIG. 2 Except for the fact that the several tubular means 17 have the configurations indicated in FIG. 2 so as to form walls of tubes, the construction of FIG. 2 is identical with that of FIG. 1 and the corresponding components are indicated with the same reference characters. It is of course apparent that with FIG. 2 the feedwater inlet 15 and chamber 13 are situated at the opposite side of the housing 8, but this of course is an immaterial distinction.
  • Both of the heat exchangers of FIGS. 1 and 2 operate in the same way, the only difference being that the embodiment of FIG. 2 is particularly suited for a heat exchanger adapted to operate with a heating gas of relatively low pressure and having a rectangular or square cross section whereas the heat exchanger of FIG. 1 is ofa cylindrical cross section and is particularly adapted for operation with high pressure gas.
  • the tubes in the immediate vicinity of the inoperative tube for example the operating tubes of the cylinders I, 2, and 3 in the case where a tube of the cylinder 2 has been rendered inoperative, have the amount of medium flowing therethrough increased either absolutely or relatively with respect to the tubes in the cylinder 4, in this particular example.
  • the throttling apertures of a throttling means at the inlet ends of the several tubular means will respectively have diameters which are enlarged at the inlet ends of the tubular means in the immediate vicinity of the inoperative tubular means either absolutely or relatively with respect to the diameters of the plurality of tubular means relatively distant from the inoperative tubular means.
  • a particular wall of tubes 17 which has one of its tubes rendered inoperative will have the flow of heating medium through the remaining tubes of this wall throttled to an extent less than through the tubes of all of the other walls.
  • all of the remaining operative tubes will have the flow of heating medium therethrough throttled to an extent less than in all of the other tubes of the entire assembly
  • the immediately adjacent tubes whether in a pair of immediately adjacent tube walls 17 or immediately adjacent involute or helical tubes will also be throttled to a lesser extent, but the extent of throttling in such immediately adjacent tubes will be somewhat greater than those tubes which remain in the same cylinder or wall.
  • the tubes of the cylinders I and 3 will be throttled to a lesser extent than the tubes of the cylinder 4 but a greater extent than'the'remaining operative tubes ofthe cylinder 2.
  • the throttling means takes the form of an apertured plate situated in front of the inlet plate 11.
  • a change in the structure subsequent to the building and operation thereof can then be fully carried out by providing several apertured plates having different arrangements and sizes of apertures therein, so that by exchanging one apertured plate for another it is possible to adjust the operations.
  • a sealing means is provided to achieve a fluidtight connection between such an apertured throttling plate and the inlet plate 11, and this sealing means preferably takes the form of precisely flat ground surfaces of the throttling plate and inlet plate 11 directly engaging each other to form a fluidtightly sealed interface therebetween.
  • the feedwater inlet region of the heat exchanger is shown in detail.
  • the throttling means takes the form of the apertured plate 19 provided with the throttling orifices 20.
  • the inlet extensions 9 of the several tubular means which form the inlet ends thereof are welded into the bores of the feedwater inlet plate 11.
  • the apertured plate 19 with its orifices 20 is bolted to the inlet plate II. To improve the seal the surfaces of plates 11 and 19 which engage each other are ground at their interface.
  • the illustrated embodiment has a throttling means in the form of individual throttling nozzles 21 threaded directly into the bores of the inlet plate 11. Where the extensions 9 extend all the way to the upstream end face of the plate 11, the nozzles 21 can be threaded directly into the extensions 9, respectively.
  • the throttling means either in the form of the individual nozzles of FIG.-4 or apertured plate of FIG. 3 is made in a precalculated manner so that approximately identical discharge conditions will be achieved at the several outlet ends of the individual tubes or strings of tubes.
  • the deviation from uniform outlet temperatures will be determined by measuring the outlet temperatures of the heated medium at the outlet ends of the individual tubes. After these outlet temperatures are measured it is possible in a known way to estimate the throttling required for the individual tubes or the extent of throttling can be newly calculated. Under certain circumstances, however, it is desirable to carry out an estimate of the required throttling structure.
  • the throttling structure constructed as estimated is used and the discharge temperatures are measured. If required, the estimated throttling structures is changed a second time for a new throttling structure which will give the required uniform discharge temperatures. Thus, an empirical trial-and-error method may be used.
  • the live-steam collector is illustrated therein. With the construction shown in FIG. 5 it is possible to measure the temperature of the steam at the outlet ends of the several individual tubular means, respectively, upon discharge of the steam into the: collecting chamber.
  • the live-steam tube extensions 10 of the several tubular means are fluidtightly welded, for example, to the outlet plate I2 in bores of the latter, respectively, the welding being located at the interior of the bores of the outlet plate, 12.
  • An auxiliary plate 22 is bolted to the outer, downstream end face of the outlet plate 12, and this auxiliary plate 22 is formed with openings respectively forming extensions of the bores of the plate 12.
  • a plurality of relatively short tubes 23 are fixed, as by welding, to the auxiliary plate 22 in a manner where these several short tubes 23 respectively form coaxial extensions of the extensions 10. Moreover, the inner diameters of the short tubes 23 are respectively equal to the inner diameters of the bores of the outlet plate 12.
  • the temperature measuring means takes the form of a plurality of thermocouple means 24 in the form thermocouple elements situated in suitable openings formed in the short tubes 23, and these thermocouple means 24 are capable of measuring the temperature of the discharging live steam in a well-known manner.
  • thermocouple means include the thermocouple cables or conductors 26 which are shielded from live steam by way of a relatively large boxlike shielding sleeve 25 which is bolted to the auxiliary plate 22 in the manner shown schematically in FIG. 5. In this way the sleeve 25 forms a protecting means to protect the conductors 26 from the heated medium.
  • FIG. 6 a different construction of a live-steam collector 14 is illustrated.
  • the live-steam tubular extensions 10 are respectively welded in the bores of the outlet plate 12 by way of welding rods.
  • the welding of the extremities of the tubes to the outlet plate 12 is carried out in the interior of the bores of the latter, in the case of FIG. 6 the welding of the tubes 10 takes place at the downstream end face of the outlet plate 12, and with the embodiment of FIG. 6 the auxiliary plate 22 is spaced slightly from the plate 12.
  • the collecting chamber 14 for the live steam is defined by a wall means which includes a removable cover shown at the top of FIG. 6, and the auxiliary plate 12 is fixed to this removable cover by way of suitable bolts.
  • the auxiliary plate 22 of FIG. 6 carries the relatively short tubes 23 which respectively form coaxial extensions of the extensions 10 and which carry the several thermocouple means 24.
  • the conductors 26 of the thermocouple means in the embodiment of FIG. 6 are respectively guided through the interiors of protective tubes 27 along the bolts 28 which interconnect the plate 22 with the removable cover, so that in this case it is the tubes 27 which form the means for protecting the conductors 26 from the live steam. Further shielding of the conductors can be provided by way of a top shielding sheet 29 carried by the several connecting bolts 28 and formed withopenings receiving the upper open ends of the shielding tubes 27 in the manner shown in FIG. 6.
  • thermocouple means used to measure the temperature can be arranged in the path of gas flow or at the exterior of the heat exchanging tubes, in particular at the extensions 10 thereof.
  • the invention described above is of course not limited to use with steam generators. It can be used with heat exchangers such as, for example, those which use liquid metal for heat exchange or with regenerators in MHD circuits. Also, the invention is not limited to bundles of tubes arranged so that the heating gas flows directly across or primarily across the tubes. The invention also can be used in installations where the heating gas flows longitudinally along the heating tubes. In this latter case the method and apparatus of the invention are such that the tubes which immediately surround the tube which is rendered inoperative receive the larger amounts of the medium which is to be heated while the remaining tubes which are situated more distant from the inoperative tube receive the heated medium also in larger amounts but to a lesser extent than those tubes which immediately surround the inoperative tube.
  • the step of converting the heated water into steam within the plurality of tubular means without any intermediate collection of the heated medium and then superheating the resulting steam.
  • a plurality of tubular means through which medium to be heated flows, said plurality of tubular means respectively having inlet ends and opposed outlet ends. and throttling means situated at said inlet ends of said plurality of tubular means for throttling the flow of medium through the plurality of tubular means to an extent which will provide at the outlet ends of the plurality of tubular means substantially uniform temperatures the degree of uniformity of which is beyond that which would prevail without said throttling means, and a plurality of thermocouple means situated at and respectively coacting with said outlet ends of said plurality of tubular means for measuring the temperature of the medium discharging through the latter outlet ends, said throttling means having a construction selected in accordance with the temperatures .measured by the plurality of thermocouple means for achieving said degree of uniformity in the temperatures of the heated medium at the outlet ends of said plurality of tubular means.
  • sealing means includes flat-ground surfaces of said plates which engage each other and form a fluidtight interface therebetween.
  • an outlet plate is formed with bores respectively receiving the outlet ends of the plurality of tubular means, and a plurality of relatively short tubes respectively communicating with said outlet ends of said plurality of tubular means and at which said plurality of thermocouple means are respectively located.
  • a chamber means communicates with said outlet ends for receiving the medium discharging therefrom, said chamber means having a removable cover, and connecting means connecting said tubes tors extending through said wall means and protecting means coacting with said conductors for protecting the latter from the heated medium discharging from said outlet ends of said plurality of tubular means.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US785491A 1968-01-15 1968-12-20 Method and apparatus for increasing uniformity of heat transfer Expired - Lifetime US3563303A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT38068A AT278863B (de) 1968-01-15 1968-01-15 Verfahren und Einrichtung zur Vergleichmäßigung des Wärmeüberganges

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US3563303A true US3563303A (en) 1971-02-16

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US (1) US3563303A (de)
AT (1) AT278863B (de)
CH (1) CH496225A (de)
DE (1) DE1811596B2 (de)
GB (1) GB1239854A (de)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4050506A (en) * 1976-03-25 1977-09-27 Phillips Petroleum Company Stepwise turndown by closing heat exchanger passageways responsive to measured flow
US4697634A (en) * 1986-03-14 1987-10-06 Stein Industrie Device for fixing a perforated sheet against the perforated tube plate of a heat exchanger
US4899814A (en) * 1986-12-31 1990-02-13 Price Richard C High pressure gas/liquid heat exchanger
US5617457A (en) * 1993-03-16 1997-04-01 Siemens Aktiengesellschaft Pressurized-water reactor with individually adapted pressure distribution in the coolant
US6338383B1 (en) 1999-12-22 2002-01-15 Visteon Global Technologies, Inc. Heat exchanger and method of making same
US20100096115A1 (en) * 2008-10-07 2010-04-22 Donald Charles Erickson Multiple concentric cylindrical co-coiled heat exchanger
US20120048527A1 (en) * 2009-05-06 2012-03-01 Shuyan He Steam generator
WO2012028494A3 (de) * 2010-09-03 2012-06-21 Siemens Aktiengesellschaft Solarthermische durchlaufverdampfer-heizfläche mit lokaler querschnittsverengung an ihrem eintritt
US20130111947A1 (en) * 2010-03-31 2013-05-09 Linde Aktiengesellschaft Rebalancing a main heat exchanger in a process for liquefying a tube side stream
US20140090827A1 (en) * 2012-09-29 2014-04-03 Nortiz Corporation Heat exchanger and production method thereof
CN104697378A (zh) * 2015-03-10 2015-06-10 苏州道众机械制造有限公司 一种螺栓固定管板
CN107702557A (zh) * 2017-11-07 2018-02-16 国电科学技术研究院 冷却柱及其防冻结构、冷却三角
US20180292141A1 (en) * 2012-10-18 2018-10-11 Linde Aktiengesellschaft Heat exchanger
US20210231383A1 (en) * 2020-01-24 2021-07-29 Hamilton Sundstrand Corporation Fractal heat exchanger

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Publication number Priority date Publication date Assignee Title
CH640631A5 (de) * 1979-06-20 1984-01-13 Bbc Brown Boveri & Cie Waermeaustauscher.
DE3173329D1 (en) * 1981-07-06 1986-02-06 Azote & Prod Chim Nitration reactor for hydrocarbons in the gas phase
GB8307568D0 (en) * 1983-03-18 1983-04-27 Secretary Industry Brit Heat exchangers
CA1240890A (en) * 1983-04-08 1988-08-23 John P. Archibald Steam generators and combined cycle power plants employing the same
FR2565322B1 (fr) * 1984-05-29 1986-08-01 Commissariat Energie Atomique Dispositif d'injection d'un liquide dans un tube et generateur de vapeur comportant ce dispositif
FR2591729A1 (fr) * 1985-12-13 1987-06-19 Chausson Usines Sa Echangeur du type evaporateur a faisceau tubulaire
EP0387377A1 (de) * 1989-03-16 1990-09-19 VIA Gesellschaft für Verfahrenstechnik mbH Rohrbündelwärmetauscher

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US2070427A (en) * 1935-05-22 1937-02-09 Faunce Benjamin Rice Heat extractor
US3406745A (en) * 1965-10-22 1968-10-22 Renault Air heaters

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Publication number Priority date Publication date Assignee Title
US2070427A (en) * 1935-05-22 1937-02-09 Faunce Benjamin Rice Heat extractor
US3406745A (en) * 1965-10-22 1968-10-22 Renault Air heaters

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4050506A (en) * 1976-03-25 1977-09-27 Phillips Petroleum Company Stepwise turndown by closing heat exchanger passageways responsive to measured flow
US4697634A (en) * 1986-03-14 1987-10-06 Stein Industrie Device for fixing a perforated sheet against the perforated tube plate of a heat exchanger
US4899814A (en) * 1986-12-31 1990-02-13 Price Richard C High pressure gas/liquid heat exchanger
US5617457A (en) * 1993-03-16 1997-04-01 Siemens Aktiengesellschaft Pressurized-water reactor with individually adapted pressure distribution in the coolant
US6338383B1 (en) 1999-12-22 2002-01-15 Visteon Global Technologies, Inc. Heat exchanger and method of making same
US6571866B2 (en) 1999-12-22 2003-06-03 Visteon Global Technologies, Inc. Heat exchanger and method of making same
US6612367B2 (en) 1999-12-22 2003-09-02 Visteon Global Technologies, Inc. Heat exchanger and method of making same
US20100096115A1 (en) * 2008-10-07 2010-04-22 Donald Charles Erickson Multiple concentric cylindrical co-coiled heat exchanger
US20120048527A1 (en) * 2009-05-06 2012-03-01 Shuyan He Steam generator
US9062918B2 (en) * 2009-05-06 2015-06-23 Tsinghua University Steam generator
US20130111947A1 (en) * 2010-03-31 2013-05-09 Linde Aktiengesellschaft Rebalancing a main heat exchanger in a process for liquefying a tube side stream
US9562718B2 (en) * 2010-03-31 2017-02-07 Linde Aktiengesellschaft Rebalancing a main heat exchanger in a process for liquefying a tube side stream
EP2561294A4 (de) * 2010-03-31 2018-03-21 Linde Aktiengesellschaft Neuausgleich eines hauptwärmetauschers in einem verfahren zur verflüssigung eines röhrenseitenstroms
WO2012028494A3 (de) * 2010-09-03 2012-06-21 Siemens Aktiengesellschaft Solarthermische durchlaufverdampfer-heizfläche mit lokaler querschnittsverengung an ihrem eintritt
US20140090827A1 (en) * 2012-09-29 2014-04-03 Nortiz Corporation Heat exchanger and production method thereof
US9970716B2 (en) * 2012-09-29 2018-05-15 Noritz Corporation Heat exchanger and production method thereof
US20180292141A1 (en) * 2012-10-18 2018-10-11 Linde Aktiengesellschaft Heat exchanger
CN104697378A (zh) * 2015-03-10 2015-06-10 苏州道众机械制造有限公司 一种螺栓固定管板
CN107702557A (zh) * 2017-11-07 2018-02-16 国电科学技术研究院 冷却柱及其防冻结构、冷却三角
US20210231383A1 (en) * 2020-01-24 2021-07-29 Hamilton Sundstrand Corporation Fractal heat exchanger

Also Published As

Publication number Publication date
AT278863B (de) 1970-02-10
CH496225A (de) 1970-09-15
DE1811596A1 (de) 1969-08-07
DE1811596B2 (de) 1972-04-06
GB1239854A (en) 1971-07-21

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