WO2014166533A1 - Échangeur thermique à lamelles de gaz - Google Patents

Échangeur thermique à lamelles de gaz Download PDF

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Publication number
WO2014166533A1
WO2014166533A1 PCT/EP2013/057491 EP2013057491W WO2014166533A1 WO 2014166533 A1 WO2014166533 A1 WO 2014166533A1 EP 2013057491 W EP2013057491 W EP 2013057491W WO 2014166533 A1 WO2014166533 A1 WO 2014166533A1
Authority
WO
WIPO (PCT)
Prior art keywords
pipe
heat exchanger
bulk material
nozzles
exchanger according
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.)
Ceased
Application number
PCT/EP2013/057491
Other languages
English (en)
Inventor
Dirk Lohrberg
Andreas Orth
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.)
Outotec Finland Oy
Original Assignee
Outotec Finland Oy
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 Outotec Finland Oy filed Critical Outotec Finland Oy
Priority to KR1020157030972A priority Critical patent/KR20150139551A/ko
Priority to EP13715969.5A priority patent/EP2984432B1/fr
Priority to CN201380076049.9A priority patent/CN105164485B/zh
Priority to US14/782,842 priority patent/US20160054064A1/en
Priority to EA201591777A priority patent/EA029071B1/ru
Priority to PCT/EP2013/057491 priority patent/WO2014166533A1/fr
Priority to RS20170843A priority patent/RS56234B1/sr
Publication of WO2014166533A1 publication Critical patent/WO2014166533A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C3/00—Other direct-contact heat-exchange apparatus
    • F28C3/10—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material
    • F28C3/12—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material the heat-exchange medium being a particulate material and a gas, vapour, or liquid
    • F28C3/14—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material the heat-exchange medium being a particulate material and a gas, vapour, or liquid the particulate material moving by gravity, e.g. down a tube
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C3/00—Other direct-contact heat-exchange apparatus
    • F28C3/10—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material
    • F28C3/12—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material the heat-exchange medium being a particulate material and a gas, vapour, or liquid
    • F28C3/16—Other direct-contact heat-exchange apparatus one heat-exchange medium at least being a fluent solid, e.g. a particulate material the heat-exchange medium being a particulate material and a gas, vapour, or liquid the particulate material forming a bed, e.g. fluidised, on vibratory sieves
    • 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
    • F28D13/00—Heat-exchange apparatus using a fluidised bed
    • 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
    • F28D7/16—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 arranged in parallel spaced relation
    • 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
    • F28D7/0041—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 for only one medium being tubes having parts touching each other or tubes assembled in panel form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • F28D7/106—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 arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits

Definitions

  • the invention relates to a gas slide heat exchanger for treating bulk material comprising an elongated pipe having an inlet for introducing the bulk material at one end and an outlet for withdrawing the bulk material at the other end.
  • Such a heat exchanger comprises a stationary elongated housing having an inlet for the material to be treated at one end and an outlet at the other end as well as one or more screw rotors provided in the housing and extending along the length thereof.
  • the rotor comprises a central shaft and a worm gear provided on the outer surface of the shaft.
  • Within the shaft a conduit is provided which is connected to a steam supply.
  • the bulk material is introduced through the inlet into the housing and conveyed therethrough by the rotating movement of the screw conveyor. At the same time the bulk material is heated by the steam flowing in the central conduit of the shaft as well as by steam flowing in the double wall of the housing.
  • Another heat exchanger comprising a screw conveyor is known from document DE 534 988, wherein a heating or cooling medium flows through the hollow screw conveyor to heat or cool the bulk material transported through the hous- ing.
  • Other screw conveying heat exchangers are known from documents DE 17 51 961 or DD 288 663 A5.
  • Document DE 10 201 1 078 954 A1 describes another bulk heat exchange apparatus having a feed section, a heat exchanger section and a bulk material dis- charge section.
  • the bulk material feed section is divided by a bulk partition in a conveyor flow supply chamber and a counter flow supply chamber.
  • the bulk material partition continues to the bulk heat exchanger section. Thereby, a conveyor flow region and a counter flow region are formed of the heat exchanger section.
  • the heated parti- cles After passing through the heat exchanging section, the heated parti- cles are circulated within an upper chamber of the apparatus and fall back into an annular bed to be withdrawn.
  • This system also is quite complex and requires a specific regulation of the fluidization air.
  • fluidizing gas is injected via nozzles or membranes at the lower part of the gas slide.
  • the amount of injected gas is kept in a range that the bulk material is flowing but not expanding or circulating as it is desired for example in a fluidized bed cooler. It is the object of the present invention to provide a gas slide heat exchanger with improved heat exchange capabilities and an easy structure.
  • a heat exchanger comprising the features of claim 1 .
  • a plurality of heat exchange tubes extends along the longi- tudinal direction of the pipe, wherein a plurality of fluidization nozzles for intro- ducing a fluidizing gas is provided at the bottom of the pipe.
  • the bulk material is fluidized and slowly flows along the elongated pipe.
  • heat is exchanged with the heat exchange medium flowing through the heat exchanging tubes.
  • the heat exchanger elements of the gas slide heat exchanger according to the present invention can be designed with a greater surface/volume ratio.
  • Multiple single heat exchange tubes can be integrated to a bundle with a much greater surface than the cylindrical surface of the screw shaft and the screw conveyor casing used in the prior art. Simultaneously, the heat exchange is promoted by the expanded surface of the bulk mate- rial fluidized by the fluidizing gas. This is not possible in the standard screw conveyor.
  • the fluidization nozzles are directed perpendicular to the conveying direction of the bulk material.
  • Perpendicular in the context of the present invention refers to an orientation of the fluidization nozzles within a range of 85 to 95°, in particular about 90°, relative to the major conveying direction of the bulk material along the pipe. If some of the fluidization nozzles extend from the bottom of the pipe into the upper region of the pipe, it is possible to ensure the expansion and conveying of the material also in cases of bulk material that tends to generate holes rather than expand when fluidized. This happens in particular if the bulk material is very fine.
  • the pipe is tilted downwards in the conveying direction of the bulk material, preferably at an angle of 5 to 10 degrees or more preferably at an angle of 6 to 8 degrees.
  • the fluidized bulk material automatically flows down the pipe towards the outlet.
  • the pipe preferably comprises a double wall for receiving a heat exchange medium. Accordingly, heat is exchanged not only between the longitudinal heat exchange tubes within the fluidized material but also from the outer wall.
  • the pipe wall may be formed from a plurality of smaller pipes for receiving a heat exchange medium.
  • the heat exchange surface is increased.
  • a plurality of smaller pipes may be provided within the pipe for receiving the heat exchange medium.
  • the openings of the transport nozzles are locat- ed in a region extending between about 25 and 75% of the height of the pipe.
  • the transport nozzles are inclined downwards at an angle of 30 to 60°, preferably 40 to 50° and in particular about 45°.
  • the invention provides that the transport nozzles are inclined in the conveying direction of the bulk material in order to promote the conveyance of the material.
  • the transport nozzles are inclined at an angle of 30 to 60°, preferably 40 to 50° and in particular about 45°.
  • the fluidization and/or transport nozzles are located in respective rows along the longitudinal direction of the pipe, wherein preferably common supply pipes are provided for supplying fluidiz- ing gas to each row of nozzles.
  • the flow rate of the fluidization and/or transport nozzles can be regulated, wherein preferably the fluidizing gas is injected through the transport nozzles with a low velocity in conveying direction to ensure just a proper bulk material flow.
  • the other part of the fluidizing gas can instead be injected perpendicular to the conveying direction through the fluidization nozzles with a comparatively higher velocity obtaining an expansion of the bulk material and hence a great material surface and improved heat exchange.
  • the heat exchange medium may be directed counter-currently or co-currently to the conveying direction of the bulk material depending on the specific needs of the process and material.
  • Fig. 1 is a cross section of a heat exchanger according to the present invention
  • Fig. 2 is a cross section of a first embodiment taken along line A-A in
  • Fig. 3 is a cross section of the first embodiment of the invention wherein the heat exchange tubes are not shown, while the distribution of the bulk material within the pipe cross section is shown;
  • Fig.4 is a cross section similar to Fig. 3 of a second embodiment of the invention taken along line A-A in Fig. 1 ;
  • Fig. 5 is a cross section similar to Fig. 3 of an alternative embodiment of the present invention taken along line A-A in Fig. 1 .
  • a gas slide heat exchanger 1 according to the present invention as shown in Fig. 1 includes a pipe 2 having an inlet 3 for introducing a bulk material at a first end, and an outlet 4 for withdrawing the bulk material at the other end of pipe 2.
  • the pipe 2 is slightly downwards tilted at an angle of 6 to 8 degrees in the direction of the outlet 4.
  • a plurality of heat exchange tubes 5 (Fig. 2) extends along the longitudinal direction of pipe 2.
  • a heating medium is introduced into the heat exchange tubes 5 via a supply port 6 and withdrawn through outlet port 7 at the other end of pipe 2.
  • the wall 2a of pipe 2 is designed as a double wall to receive additional heat exchange medium.
  • the heat exchanging medium preferably water, boiler feed water or thermo oil
  • the heat exchange medium can just as well be directed co-currently to the conveying direction of the bulk material in accordance with the specific requirements of the heat exchange process and the material to be treated.
  • a supply pipe 8 for fluidizing gas is provided below the pipe 2 .
  • a plurality of fluidization nozzles 9 extends in an upward direction towards pipe 2.
  • the fluidization nozzles 9 enter the pipe 2 at its bottom 10 at approximately the center of the bottom region of pipe 2.
  • supply pipes 1 1 , 12 extend along the major part of the length of pipe 2 and comprise transport nozzles 13, 14 which enter into pipe 2 in a region located at 25 to 75%, in particular 30 to 40% of the height of pipe 2.
  • the transport nozzles 13, 14 are inclined downwards at an angle of ap- proximately 45°:
  • the transport nozzles 13, 14 further are inclined in the conveying direction of the bulk material at an angle of also about 45°.
  • the fluidization gas in particular air, that is introduced (continuously or as a pulsed stream) into the pipe 2 through the fluidization nozzles 9 and the transport nozzles 13, 14 fluidizes the bulk material within pipe 2 and flows to- gether with the bulk material along pipe 2 until it exits through a gas outlet 15 provided at the end of pipe 2.
  • the heat exchanger according to the first embodiment of the present invention as shown in Fig. 1 and 2 is basically constructed as described above. Next, its operation and advantages shall be described.
  • Bulk material such as ore fines, aluminium hydrate, ash or the like, is introduced into pipe 2 through inlet 3.
  • the bulk material is fluidized within pipe 2 by fluidization gas introduced through the fluidization nozzles 9 and the transport nozzles 13, 14 and flows along pipe 2 until it is withdrawn from pipe 2 through outlet 4.
  • a part of the fluidizing gas is injected with a low velocity in conveying direction through the transport nozzles 13, 14, while the other part of the fluidizing gas is injected with a comparatively higher velocity through the fluidization nozzles 9 in a direction perpendicular to the conveying direction of the bulk material.
  • the bulk material is fluidized and expanded to obtain a great material surface and an improved heat exchange.
  • Fig. 3 The concept of the fluidization is illustrated in Fig. 3 wherein the bulk material is primarily transported in transport zone 20 while zone 21 indicates an area with enlarged material surface due to the expansion of the bulk material.
  • zone 21 indicates an area with enlarged material surface due to the expansion of the bulk material.
  • the heat exchanging tubes 5 are not illustrated in Fig. 3 to 5.
  • FIG. 4 shows an embodiment, wherein the transport nozzles 13, 14 are arranged at a higher region of the pipe 2 so that an increased zone 21 with enlarged material surface is created.
  • a similar effect is achieved in the embodiment shown in Fig. 5 if some of the fluidization nozzles 9a do not open at the bottom 10 of pipe 2 but extend into the upper region of the pipe 2 to create a zone 21 with enlarged material surface.
  • the transport nozzles 13, 14 and the extended fluidization nozzles 9a may be combined in a heat exchanger 1 .
  • the flow rate of the fluidization air supplied through fluidization nozzles 9, 9a and transport nozzles 13, 14 can be regulated in order to provide for adequate fluidization and transport conditions of the bulk material within pipe 2.
  • a gas slide heat exchanger according to the present invention is less complex to manufacture, provides a greater heat exchange surface at approximately same main dimensions and provides for an improved heat transfer due to an expanded bulk material surface.
  • the present invention is suitable for heating the bulk material by employing heated heat exchange media, but may also be used for cooling the bulk material with cold heat exchange media.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices And Processes Conducted In The Presence Of Fluids And Solid Particles (AREA)
  • Nozzles (AREA)

Abstract

L'invention concerne un échangeur thermique (1) destiné au traitement d'un matériau en vrac, comprenant un tuyau allongé (2) possédant une entrée (3) pour l'introduction du matériau en vrac à une extrémité et une sortie (4) pour soutirer le matériau en vrac à l'autre extrémité. Une pluralité de tuyaux d'échange thermique (5) s'étend le long de la direction longitudinale du tuyau (2), et une pluralité de buses de fluidisation (9, 9a) pour l'introduction d'un gaz de fluidisation est ménagée au fond (10) du tuyau (2).
PCT/EP2013/057491 2013-04-10 2013-04-10 Échangeur thermique à lamelles de gaz Ceased WO2014166533A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
KR1020157030972A KR20150139551A (ko) 2013-04-10 2013-04-10 가스 슬라이드 열교환기
EP13715969.5A EP2984432B1 (fr) 2013-04-10 2013-04-10 Échangeur de chaleur à glissière pneumatique
CN201380076049.9A CN105164485B (zh) 2013-04-10 2013-04-10 气体滑道换热器
US14/782,842 US20160054064A1 (en) 2013-04-10 2013-04-10 Gas slide heat exchanger
EA201591777A EA029071B1 (ru) 2013-04-10 2013-04-10 Теплообменник с псевдоожиженным слоем
PCT/EP2013/057491 WO2014166533A1 (fr) 2013-04-10 2013-04-10 Échangeur thermique à lamelles de gaz
RS20170843A RS56234B1 (sr) 2013-04-10 2013-04-10 Izmenjivač toplote sa strujanjem gasa

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2013/057491 WO2014166533A1 (fr) 2013-04-10 2013-04-10 Échangeur thermique à lamelles de gaz

Publications (1)

Publication Number Publication Date
WO2014166533A1 true WO2014166533A1 (fr) 2014-10-16

Family

ID=48092957

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/057491 Ceased WO2014166533A1 (fr) 2013-04-10 2013-04-10 Échangeur thermique à lamelles de gaz

Country Status (7)

Country Link
US (1) US20160054064A1 (fr)
EP (1) EP2984432B1 (fr)
KR (1) KR20150139551A (fr)
CN (1) CN105164485B (fr)
EA (1) EA029071B1 (fr)
RS (1) RS56234B1 (fr)
WO (1) WO2014166533A1 (fr)

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CN105698561A (zh) * 2016-01-18 2016-06-22 巢湖瑞丰油脂有限公司 一种烘炒芝麻冷却设备及使用方法

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DE534988C (de) 1929-06-23 1931-10-05 Otto Hardung Umlaufender Waermeaustauscher mit in einem Gehaeuse angeordneter doppelwandiger Hohlschnecke
DE1551441A1 (de) 1966-07-20 1971-04-29 Balfour & Co Ltd Henry Waermeaustauscher
DE1751961A1 (de) 1968-08-24 1971-06-16 Werner & Pfleiderer Schneckenwaermeaustauscher mit hohlen Schenckengaengen
US3851406A (en) * 1972-04-24 1974-12-03 Ipran Inst Proiectari Pentru I Fluidized-bed apparatus
US4509463A (en) * 1982-12-24 1985-04-09 M.A.N. Maschinenfabrik Ausburg-Nurnberg Aktiengesellschaft Upright apparatus for cooling high pressure gases containing a high dust content
DE3320595A1 (de) * 1983-06-08 1984-12-13 Rheinische Braunkohlenwerke AG, 5000 Köln Schneckenfoerderer zum austragen von festen rueckstaenden aus unter hoher temperatur und ueberdruck betriebenen einrichtungen
DE3345235A1 (de) * 1983-12-14 1985-06-20 Sulzer-Escher Wyss GmbH, 7980 Ravensburg Fliessbett mit einer waermetauscher-anordnung
DD288663A5 (de) 1989-10-18 1991-04-04 Veb Volkswerft Stralsund,De Waermetauschende foerderschnecke
US5190415A (en) * 1991-09-03 1993-03-02 Ingersoll-Rand Company Flow induced feed collector and transporter apparatus
EP0694749A1 (fr) * 1994-07-28 1996-01-31 GEC ALSTHOM Stein Industrie Dispositif de refroidissement de particules solides en sortie d'un agencement de traitement
US6253715B1 (en) * 1999-04-30 2001-07-03 Miura Co., Ltd. Water-tube boiler
US20070183854A1 (en) * 2006-02-07 2007-08-09 Ibau Hamburg Ingenieurgesellschaft Industriebau Mbh Device for the pneumatic conveying of particulate and powdery bulk material
AT507100B1 (de) 2008-07-23 2010-02-15 Andritz Tech & Asset Man Gmbh Vorrichtung und verfahren zur wärmeübertragung
DE102009020437A1 (de) * 2009-05-08 2010-11-11 Outotec Oyj Vorrichtung zum Transportieren von Schüttgütern
WO2010147771A1 (fr) 2009-06-17 2010-12-23 Motorola Mobility, Inc. Dispositif électronique portable et procédé de gestion d'énergie pour celui-ci afin de s'adapter à un fonctionnement de projecteur
US20110240269A1 (en) * 2010-04-01 2011-10-06 Mac-Dan Innovations Llc Waste water heat recovery system
WO2012131236A1 (fr) * 2011-03-31 2012-10-04 Mersen France Py Sas Installation et reacteur pour la synthese directe d'acide chlorhydrique a partir d'hydrogene et de chlore avec recuperation de chaleur
DE102011078954A1 (de) 2011-07-11 2013-01-17 Coperion Gmbh Schüttgut-Wärmetauschervorrichtung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105698561A (zh) * 2016-01-18 2016-06-22 巢湖瑞丰油脂有限公司 一种烘炒芝麻冷却设备及使用方法

Also Published As

Publication number Publication date
EP2984432B1 (fr) 2017-08-02
CN105164485A (zh) 2015-12-16
US20160054064A1 (en) 2016-02-25
EP2984432A1 (fr) 2016-02-17
EA029071B1 (ru) 2018-02-28
CN105164485B (zh) 2017-08-08
EA201591777A1 (ru) 2016-03-31
KR20150139551A (ko) 2015-12-11
RS56234B1 (sr) 2017-11-30

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