WO1999036737A1 - Echangeur thermique a tube tournant - Google Patents

Echangeur thermique a tube tournant Download PDF

Info

Publication number
WO1999036737A1
WO1999036737A1 PCT/NO1998/000214 NO9800214W WO9936737A1 WO 1999036737 A1 WO1999036737 A1 WO 1999036737A1 NO 9800214 W NO9800214 W NO 9800214W WO 9936737 A1 WO9936737 A1 WO 9936737A1
Authority
WO
WIPO (PCT)
Prior art keywords
drum
tubular
heat exchanger
tube heat
discs
Prior art date
Application number
PCT/NO1998/000214
Other languages
English (en)
Norwegian (no)
Inventor
Hans Jørgen BRØNLUND
Original Assignee
Kvaerner Technology And Research Limited
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kvaerner Technology And Research Limited filed Critical Kvaerner Technology And Research Limited
Priority to AU92845/98A priority Critical patent/AU9284598A/en
Publication of WO1999036737A1 publication Critical patent/WO1999036737A1/fr

Links

Classifications

    • 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
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B11/00—Machines or apparatus for drying solid materials or objects with movement which is non-progressive
    • F26B11/02—Machines or apparatus for drying solid materials or objects with movement which is non-progressive in moving drums or other mainly-closed receptacles
    • F26B11/04—Machines or apparatus for drying solid materials or objects with movement which is non-progressive in moving drums or other mainly-closed receptacles rotating about a horizontal or slightly-inclined axis
    • F26B11/0445—Machines or apparatus for drying solid materials or objects with movement which is non-progressive in moving drums or other mainly-closed receptacles rotating about a horizontal or slightly-inclined axis having conductive heating arrangements, e.g. heated drum wall
    • F26B11/045—Machines or apparatus for drying solid materials or objects with movement which is non-progressive in moving drums or other mainly-closed receptacles rotating about a horizontal or slightly-inclined axis having conductive heating arrangements, e.g. heated drum wall using heated internal elements, e.g. which move through or convey the materials to be dried

Definitions

  • the invention concerns a rotating shell and tube heat exchanger for use as a reactor, or for heating, cooling or evaporation, alone or in combination, of bulk materials, granules or pellets, comprising a drum with intake and outlet for the bulk material, and relative to the drum internal, parallel, coaxial tubular discs which form energy transfer surfaces, where the energy medium flows into the tubes, and the bulk material is located on the outside of the tubular discs, where the tubular discs are arranged for rotation about a longitudinal axis which is common for the drum and the tubular discs, where each tubular disc comprises concentric tubular rings and at least one manifold to conduct the energy medium to and from each tubular ring, where the shell and tube heat exchanger further comprises distribution pipes and collecting pipes to conduct the energy medium between the tubular discs' manifolds and between the manifolds and rotating couplings which are connected to an external pipe system.
  • Rotating shell and tube heat exchangers of the above-mentioned type are employed in various types of processing plants, for example within the mineral industry, the food industry, the petrochemical industry or sludge treatment plants. Apart from being used for heating or cooling, rotating shell and tube heat exchangers of the above type may also be employed for evaporation, especially of water, but also of other volatile liquids. Rotating shell and tube heat exchangers of the above type may also be employed as reactors during chemical reactions at approximately atmospheric pressure, such as the calcination of soda, where amongst other processes a reaction and a degassing of carbon dioxide take place.
  • the processing medium may be composed of any kind of liquid or dry bulk material, for example sludge, powder, granules or pellets, hereinafter designated bulk material.
  • the drum may either be stationary or rotate together with the tubular discs.
  • the tubular discs are securely connected to a central shaft which is rotatably mounted in the centre of the stationary drum's gable ends.
  • the drum is also securely connected to this shaft, and this shaft is externally supported. In both cases this entails practical limitations to the size of the rotating shell and tube heat exchanger, since bending moments in the drum and the shaft and stresses on the bearings become excessive in large rotating shell and tube heat exchangers.
  • the object of the invention is to provide a rotating shell and tube heat exchanger which can be built on a large scale without being encumbered by the above-mentioned problems or limitations.
  • the invention therefore consists in a rotating shell and tube heat exchanger of the type mentioned in the introduction where the outside of the drum in the circumferential direction is provided with at least two external circular paths or flanges, where the drum is rotatably mounted via each of the paths or flanges on two rollers or bogies arranged under the drum on each side of the longitudinal axis's horizontal projection, where the drum is connected to a drive unit for rotation of the drum, and where the shell and tube heat exchanger includes means for rotation of the tubular discs together with the drum.
  • the rotating shell and tube heat exchanger according to the invention has no load-bearing central shaft, thereby providing a rotating shell and tube heat exchanger which can be built on a large scale without being encumbered with the said problem connected with bending moments in the drum and the shaft and stresses on the bearings which affects large rotating shell and tube heat exchangers which have a load-bearing central shaft.
  • a rotating shell and tube heat exchanger is thereby provided which can be built on a larger scale than known rotating shell and tube heat exchangers, and calculations show that it will be possible to build without difficulty the shell and tube heat exchanger according to the invention with a capacity of 250 tons of mineral concentrate per hour, which at present is considered to be an upper practical capacity limit for those processing plants where installation of the shell and tube heat exchanger may be envisaged.
  • a lower practical capacity limit for the shell and tube heat exchanger according to the invention appears to be 50 tons per hour for mineral concentrate, since the shell and tube heat exchanger will be too expensive to design for a lower capacity.
  • the rotating shell and tube heat exchanger's means for rotation of the tubular discs together with the drum can be composed of welded or bolted connections, or of different types of fit connections.
  • the means for rotation of the tubular discs comprise releasable, load-bearing connections between the drum and the tubular discs for transferring the tubular discs' weight to the drum and transferring the drum's rotary motion to the tubular discs.
  • FIG. 2 is a cross section through the shell and tube heat exchanger in fig. 1, viewed along the intersecting line II-II
  • fig. 3 illustrates an alternative embodiment of the shell and tube heat exchanger's distribution pipes and collecting pipes
  • fig. 4 illustrates a second alternative embodiment of the shell and tube heat exchanger's distribution pipes and collecting pipes
  • fig. 5 illustrates releasable, load-bearing connections between the drum and the tubular discs
  • fig. 6 is a cross section viewed along the intersecting line VI- VI in fig. 5.
  • Figs. 1 and 2 illustrate a rotating shell and tube heat exchanger 1 according to the invention
  • fig. 2 illustrates a cross section through the shell and tube heat exchanger viewed along the intersecting line II-II in fig. 1.
  • the shell and tube heat exchanger 1 comprises a drum 3 which in fig. 1 is shown substantially cut away.
  • An intake 4 and an outlet 5 for the bulk material is provided in gable ends 28.
  • Parallel, coaxial tubular discs 6 for energy transfer to or from the bulk material are located inside the drum and in the illustrated embodiment are releasably connected thereto in a manner which will be explained further below.
  • tubular discs 6 rotate together with the drum 3 about a common longitudinal axis 7, as illustrated by the arrow R, while the drum's gable ends 28 with the intake 4 and the outlet 5 are stationary.
  • the bulk material is fed in through the intake 4, as illustrated by the arrow PI, and is transferred by means of gravity and the drum's and the tubular discs' rotation towards the outlet 5, where it leaves the shell and tube heat exchanger, as illustrated by the arrow P2.
  • the tubular discs 6 rotate through the bulk material, with the result that it is stirred and energy is transferred to or from the energy medium which flows through the tubes in the tubular discs.
  • the outside 15 of the drum is provided in the circumferential direction with two external circular paths or flanges 17, each of which runs over two rollers 18 which are provided under the drum 3 on each side of the longitudinal axis's 7 horizontal projection, which is best illustrated in fig. 2. In this manner a rotatable mounting of the drum 3 is obtained.
  • bogies may be employed for mounting of the drum.
  • the drum's rotation is generated by a drive unit 20, for example an electric gear motor, which via a drive 39 drives a gear rim 40 which is provided on the outside 15 of the drum.
  • the drum's axial forces are absorbed by a wheel 52 which rolls against the side of one of the paths 17.
  • Each tubular disc 6 includes concentric tubular rings 8 and a manifold 9 to guide the energy medium to and from each tubular ring 8, which is most clearly illustrated in figs. 2-4, which illustrate tubular discs each consisting of 6 tubular rings.
  • the energy medium is led from an external pipe system, through a rotating coupling 13 and into distribution pipes 10. From here the energy medium flows into the manifolds 9 in each individual tubular disc 6, and on into each individual tubular ring 8. From the tubular ring the energy medium flows back to the manifold and on into collecting pipes 11, whereupon the energy medium leaves the shell and tube heat exchanger through the rotating coupling 13.
  • Fig. 2 which corresponds to fig. 1, illustrates an embodiment of the distribution pipes and the collecting pipes which is well-suited to heating with steam, where the steam is condensed into water in the tubular rings.
  • the steam flows in through an inlet 31 , and on into the centrally located distribution pipe 10, where the steam flows in the space above the water which flows in the opposite direction.
  • Short pipes 51 extend from each manifold 9 into the centrally located distribution pipe 10, passing the steam into the manifold.
  • the manifolds 9 are composed of pipes which have a common through-flow space for the steam and the water.
  • the steam's circulation is generated by condensation of the steam, resulting in a weak underpressure inside the tubular rings, while the water's circulation is generated by gravity, which causes the water to run out of the tubular ring 8 into the manifold 9. From here the water runs into the distribution pipe 10, which in this embodiment therefore also acts as a collecting pipe. By means of the steam pressure the water is forced via a syphon 53 out through the rotating coupling 13 and out through an outlet 32.
  • Fig. 3 illustrates an embodiment of the rotating shell and tube heat exchanger where the distribution pipes 10 and the collecting pipes 1 1 are located on the outside of the drum 3 and connected to the manifolds 9 with releasable couplings 16, while fig. 4 illustrates an embodiment where the distribution pipes 10 and the collecting pipes 11 are located immediately inside the innermost tubular ring 8.
  • the distribution pipes and the collecting pipes constitute separate pipe systems for supply and removal of the energy medium.
  • liquid energy media for example hot oil or a cooling mixture of water and glycol.
  • the steam flows through the tubular discs in parallel, while the energy medium which is employed in the embodiments in figs.
  • the distribution pipes and the collecting pipes can be provided in such a manner that the energy medium flows through the tubular discs in a combination of series and parallel connection, since the energy medium, for example, can be distributed in parallel to groups of tubular discs, whereupon it flows in series through the tubular discs in each group.
  • the distribution pipes 10 and the collecting pipes 1 1 also include couplings and fittings and may be held in place by pipe clamps.
  • the embodiments illustrated in figs. 3 and 4 have the advantage that the tubular discs 6 have an opening 27 in their central areas, thus providing in the shell and tube heat exchanger's central area an access area for maintenance.
  • the illustrated embodiment of the rotating shell and tube heat exchanger according to the invention also includes releasable, load-bearing connections 21 between the drum 3 and the tubular discs 6 for transferring the tubular discs' weight to the drum and transferring the drum's rotary motion to the tubular discs.
  • Figs. 5 and 6 illustrate the releasable, load-bearing connections 21 in more detail, and also illustrate in more detail how the tubular discs 6 are constructed.
  • Fig. 5 is an enlarged view of the area of the releasable, load- bearing connections 21 which are shown in the bottom part of fig. 2, viewed in the drum's longitudinal direction, while fig. 6 is a cross section viewed along the intersecting line VI- VI in fig. 5, showing the outer section of three tubular discs 6. It can be seen how the releasable, load-bearing connection 21 includes longitudinal guide elements 22 on the inside of the drum 3, and corresponding longitudinal guide elements 23 on the tubular discs.
  • the drum's and the tubular discs' guide elements 22 and 23 respectively have opposite, co-operating, radially directed surfaces or sections indicated by reference numerals 24 and 25 respectively, permitting radial movement relative to one another between the drum's and the tubular discs' guide elements.
  • the drum's longitudinal guide elements 22 are welded into the inside of the drum 3, while the tubular discs' guide elements 23 are welded to a number of spacers 33, one for each tubular disc 6, which in turn are each welded to a doubling plate 34 which is welded to the outermost tubular ring 8 in each tubular disc 6.
  • the outermost tubular ring 8 is welded to a spacer 37 in the form of a flattened tube, which is located with its longitudinal direction in the tubular rings' circumferential direction.
  • the spacer 37 is welded in turn to the second outermost tubular ring 8, which in turn is welded to a spacer 36 which is composed of a short radial tube.
  • the spacer 36 is welded in turn to the tubular ring inside, with the result that between the four innermost and the second outermost tubular ring 8 in each tubular disc 6 spacers 36 are employed in the form of radial tubes, while between the second outermost and the outermost tubular ring 8 in the illustrated embodiment a spacer 37 is employed in the form of a flattened tube which is located with its longitudinal direction in the tubular rings' circumferential direction.
  • the reason for this difference is that the bulk material, which on account of the force of gravity collects at the outermost tubular ring, would be apt to accumulate at the circular tubular spacers if they were also employed between the second outermost and the outermost tubular ring.
  • the manifold 9, which is composed of a flattened tube, is in itself capable of keeping the tubular rings 8 in place, thus fulfilling in its position the function of the spacers.
  • the longitudinal guide elements 22 are preferably evenly distributed along the drum's 3 circumference, as illustrated in figs. 2-4, where the longitudinal guide elements 22 are located at three points along the drum's circumference, thus having an angular distance of 120°.
  • a plurality of tubular discs 6 may preferably be combined to form a tubular disc section, as illustrated in fig. 1, where a tubular disc section is indicated by reference numeral 26 and is composed of a number of tubular discs which are located between two tubular disc section connections 38. This is advantageous for maintenance, since it means that several tubular discs can be removed from the drum together.
  • the tubular discs in a tubular disc section may be interconnected, for example with spacers and bolts.
  • the tubular disc section connections 38 preferably comprise bolted connections, and may, for example, be composed of flanges.
  • the manifolds will carry along more bulk material than the rest of the tubular discs.
  • the manifolds 9 in adjacent tubular discs 6 or tubular disc sections 26 respectively are preferably displaced relative to one another in the direction of rotation.
  • the manifolds 9 will thereby form a helix or be in the form of a spoked wheel, as illustrated in figs. 2-4.
  • this displacement between the manifolds 9 constitutes a relative angular distance which, calculated about the longitudinal axis, corresponds to a fraction or a multiple of the angular distance between the drum's longitudinal guide elements 22.
  • the rotating shell and tube heat exchanger comprises arms which are pivotably attached to the inside of the drum 3 for free movement between the tubular discs 6, in order to eradicate bridge formation and accumulation of the bulk material.
  • arms which are pivotably attached to the inside of the drum 3 for free movement between the tubular discs 6, in order to eradicate bridge formation and accumulation of the bulk material.
  • chains may be employed which are pivotably attached to the inside of the drum 3 for free movement between the tubular discs 6, as illustrated in fig. 1 with reference numeral 30.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Drying Of Solid Materials (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

On décrit un échangeur thermique à calandre et tube tournants, qui s'utilise comme réacteur, ou pour le chauffage, le refroidissement ou l'évaporation, seul ou associé à des matériaux en vrac, des granulés ou des billes. L'échangeur thermique comprend un tambour (3) muni d'un orifice d'admission (4) et d'un orifice d'évacuation (5) des matériaux en vrac et, parallèlement au tambour (3), des disques tubulaires coaxiaux (6) constituant des surfaces de transfert d'énergie. La partie externe (15) du tambour est munie, dans le sens de sa circonférence, d'au moins deux parcours ou brides circulaires (17). Le tambour est soutenu de manière rotative par chaque élément des parcours ou brides (17) et repose sur deux rouleaux (18) ou bogies de roulement disposés sous le tambour (3) de chaque côté de la projection horizontale de l'axe longitudinal (7). L'échangeur thermique à calandre et tube inclut un moyen pour tourner les disques tubulaires (6) en association avec le tambour (3).
PCT/NO1998/000214 1998-01-15 1998-07-14 Echangeur thermique a tube tournant WO1999036737A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU92845/98A AU9284598A (en) 1998-01-15 1998-07-14 Rotating tube heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO980201 1998-01-15
NO980201A NO306837B1 (no) 1998-01-15 1998-01-15 Rörvarmeveksler for oppvarming, törking eller kjöling av flytende eller törre bulkformede materialer

Publications (1)

Publication Number Publication Date
WO1999036737A1 true WO1999036737A1 (fr) 1999-07-22

Family

ID=19901560

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NO1998/000214 WO1999036737A1 (fr) 1998-01-15 1998-07-14 Echangeur thermique a tube tournant

Country Status (3)

Country Link
AU (1) AU9284598A (fr)
NO (1) NO306837B1 (fr)
WO (1) WO1999036737A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000036355A1 (fr) * 1998-12-14 2000-06-22 Kvaerner Technology And Research Limited Echangeur de chaleur a tube tournant
CN108387069A (zh) * 2017-01-24 2018-08-10 李柱先 褐煤干燥系统及褐煤干燥方法
CN111059936A (zh) * 2019-12-26 2020-04-24 无锡华邦智能装备有限公司 换热均匀的列管式换热器
WO2020093369A1 (fr) * 2018-11-06 2020-05-14 金川集团股份有限公司 Échangeur de chaleur pour échange de chaleur de matériau et récupération d'énergie thermique
CZ308768B6 (cs) * 2020-03-17 2021-05-05 Vysoká Škola Báňská - Technická Univerzita Ostrava Rekuperační šnekový výměník tepla, zejména pro sypké materiály

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2724639B2 (de) * 1977-06-01 1979-08-23 Vasily Vasilievitsch Chimki Moskovskoi Oblasti Mamistov Schüttguttrockner, der ein zylindrisches Gehäuse mit Doppelwänden aufweist
DE2531589B2 (de) * 1974-07-15 1980-01-17 Almer Sangyo Kaisha Ltd., Tokio Drehofen
US4260372A (en) * 1979-04-12 1981-04-07 Bayer Aktiengesellschaft Rotary tube
EP0077889A2 (fr) * 1981-09-24 1983-05-04 Asahi Glass Company Ltd. Dispositif pour le séchage ou le chauffage de matière granulaire
US5580242A (en) * 1993-12-11 1996-12-03 Babcock Bsh Aktiengesellschaft Rotary kiln
WO1998002700A1 (fr) * 1996-07-15 1998-01-22 Kumera Corporation Sechoir a vapeur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2531589B2 (de) * 1974-07-15 1980-01-17 Almer Sangyo Kaisha Ltd., Tokio Drehofen
DE2724639B2 (de) * 1977-06-01 1979-08-23 Vasily Vasilievitsch Chimki Moskovskoi Oblasti Mamistov Schüttguttrockner, der ein zylindrisches Gehäuse mit Doppelwänden aufweist
US4260372A (en) * 1979-04-12 1981-04-07 Bayer Aktiengesellschaft Rotary tube
EP0077889A2 (fr) * 1981-09-24 1983-05-04 Asahi Glass Company Ltd. Dispositif pour le séchage ou le chauffage de matière granulaire
US5580242A (en) * 1993-12-11 1996-12-03 Babcock Bsh Aktiengesellschaft Rotary kiln
WO1998002700A1 (fr) * 1996-07-15 1998-01-22 Kumera Corporation Sechoir a vapeur

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000036355A1 (fr) * 1998-12-14 2000-06-22 Kvaerner Technology And Research Limited Echangeur de chaleur a tube tournant
CN108387069A (zh) * 2017-01-24 2018-08-10 李柱先 褐煤干燥系统及褐煤干燥方法
WO2020093369A1 (fr) * 2018-11-06 2020-05-14 金川集团股份有限公司 Échangeur de chaleur pour échange de chaleur de matériau et récupération d'énergie thermique
CN111059936A (zh) * 2019-12-26 2020-04-24 无锡华邦智能装备有限公司 换热均匀的列管式换热器
CN111059936B (zh) * 2019-12-26 2021-06-08 无锡华邦智能装备有限公司 换热均匀的列管式换热器
CZ308768B6 (cs) * 2020-03-17 2021-05-05 Vysoká Škola Báňská - Technická Univerzita Ostrava Rekuperační šnekový výměník tepla, zejména pro sypké materiály

Also Published As

Publication number Publication date
NO306837B1 (no) 1999-12-27
NO980201L (no) 1999-07-16
AU9284598A (en) 1999-08-02
NO980201D0 (no) 1998-01-15

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