EP3123092A2 - Échangeur de chaleur à contre-courant pour effluents gazeux chargés de poussières d'installations métallurgiques - Google Patents

Échangeur de chaleur à contre-courant pour effluents gazeux chargés de poussières d'installations métallurgiques

Info

Publication number
EP3123092A2
EP3123092A2 EP15741781.7A EP15741781A EP3123092A2 EP 3123092 A2 EP3123092 A2 EP 3123092A2 EP 15741781 A EP15741781 A EP 15741781A EP 3123092 A2 EP3123092 A2 EP 3123092A2
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
cooling
countercurrent
pocket
gas
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.)
Granted
Application number
EP15741781.7A
Other languages
German (de)
English (en)
Other versions
EP3123092B1 (fr
Inventor
Manfred Schmiedberger
Dietmar Steiner
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.)
Primetals Technologies Austria GmbH
Original Assignee
Primetals Technologies Austria GmbH
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 Primetals Technologies Austria GmbH filed Critical Primetals Technologies Austria GmbH
Publication of EP3123092A2 publication Critical patent/EP3123092A2/fr
Application granted granted Critical
Publication of EP3123092B1 publication Critical patent/EP3123092B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D17/00—Arrangements for using waste heat; Arrangements for using, or disposing of, waste gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • 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
    • F28D7/06—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 having a single U-bend
    • 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
    • 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
    • F28D7/1607—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 with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G7/00—Cleaning by vibration or pressure waves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/104—Particular pattern of flow of the heat exchange media with parallel flow

Definitions

  • the invention relates to a method for cooling dust-laden exhaust gas from a metallurgical plant, wherein the exhaust gas by means of a cooling gas by means of indirect
  • Heat transfer is cooled, and a device for carrying out the
  • the dust load of the exhaust gas can be at the cooling surfaces of indirect
  • Heat transfer working cooling units deposit. Such deposits hinder the heat transfer between the exhaust gas and the cooling medium and the gas flow, and must therefore always be removed to maintain a satisfactory cooling performance and an unobstructed gas flow. This happens, for example, by providing scrapers, scrape the dust covering; or by vibrating the parts where the dust settles - for example, by a shock by means of an impact mechanism - so that the
  • a method of cooling dust-laden exhaust gas from a metallurgical plant wherein the exhaust gas is cooled by a cooling gas by means of indirect heat transfer, characterized in that the exhaust gas cooling at a temperature above 650 ° C, preferably above 680 ° C, more preferably above 700 ° C is supplied, and for the cooling gas, the flow direction at least once changed, preferably reversed, is,
  • the dust-laden exhaust gas comes from a metallurgical plant.
  • Metallurgical plants such as converters, electric arc furnace EAF, AOD, ladle furnace, sintering belt, blast furnace and other reduction units. It may also be off
  • Combinations or from several such metallurgical plants originate. Preferably it comes from a steel plant.
  • the exhaust gas has a high temperature
  • dust-laden exhaust gas is to be understood as meaning an exhaust gas which on average carries more than 20 mg / Nm 3 of solids as dust.
  • the average is time-integrated dust concentration divided by time-during the operating life of the dust source for the dust-laden exhaust gas, for example, in practice half-hour averages are given during the operating time of an EAF. Since in the indirect heat transfer, the heat removed during cooling heat is transferred to the cooling medium, which is not mixed with the exhaust gas, their further use by processing the cooling medium is basically easier than cooling by direct heat transfer.
  • the cooling gas may flow first from top to bottom and after the reversal from bottom to top.
  • Chiller is exposed to the entry of the exhaust gas, reduced.
  • Cooling units operated according to the invention for higher exhaust gas temperatures can be used as heat exchangers previously used for dust-laden exhaust gas of metallurgical plants with crossflow of the cooling gas or natural draft radiator with indirect heat transfer. While such conventional cross-flow heat exchangers can be used, for example, only up to about 650.degree. C., the process control according to the invention allows safe operation at inlet temperatures of up to about 750.degree.
  • the exhaust gas is supplied to the cooling according to the invention with a temperature above 650 ° C, preferably above 680 ° C, more preferably above 700 ° C.
  • a temperature above 650 ° C, preferably above 680 ° C, more preferably above 700 ° C are used.
  • temperatures of up to 750 ° C. can be reliably controlled in the long term.
  • a temperature range which is customary for cross-flow cooling for the inlet temperature of exhaust gas to be cooled can be increased from 300 to 600 ° C. to 300 to 750 ° C.
  • the temperature difference between two media determines the efficiency of the
  • Heat transfer Accordingly, can be cooled more efficiently with the countercurrent principle than, for example, in a cross-flow heat exchanger of the cooling gas. Accordingly, the exchange area between exhaust gas and cooling gas required for a specific heat dissipation can be reduced. Reduction of the exchange surface means saving material and weight and can reduce the space requirement of the
  • the cooling according to the invention uses less cooling gas. This is hotter at the exit than at cross-flow cooling. Since less but hotter cooling gas is produced, the cooling gas is also better usable elsewhere.
  • the cooling gas is supplied to the cooling of the exhaust gas use of its heat content.
  • the cooling according to the invention is effective in comparison with cooling with crossflow with less cooling gas. This is hotter at the exit than at
  • the supply of cooling gas is controlled continuously.
  • the supply of cooling gas can be fine-tuned to the actual needs of cooling gas. This reduces the consumption of cooling gas and the consumption of energy for the supply of cooling gas, for example, compared to a common in plate heat exchangers with cross flow of the cooling gas discrete control - overall, the process is more efficient.
  • the supply of cooling gas does not have to be permanent. It is preferably done only when there is a need for cooling.
  • the cooling gas is air. Air is readily available cheaply with reasonable temperatures without effort.
  • the exhaust gas can well follow the change, preferably reverse, of the flow direction of the cooling gas and ensure a large area for heat transfer, which improves the cooling effect.
  • Baffles in the countercurrent cooling gas channel also increase the heat exchange surface and thereby contribute to improved cooling. They also reduce that
  • the exhaust gas flows to
  • Another object of the present application is a
  • cooling gas supply line opens into at least one countercurrent cooling gas channel
  • the exhaust gas supply line opens into at least one counterflow exhaust gas channel, and the counterflow exhaust gas channel opens into the exhaust gas discharge line,
  • countercurrent refrigerant gas channel and countercurrent exhaust gas channel are designed for mutual indirect countercurrent gas-gas heat transfer
  • the countercurrent cooling gas channel having at least two sections with different oriented longitudinal directions, which are preferably parallel, characterized in that the countercurrent exhaust passage has at least one, preferably at least two, flaschenaschenformigen section with at least one inlet opening and at least one outlet opening for the exhaust gas is limited by metal plates, wherein between a pair of opposing metal plates of a flat pocket stiffening elements are present, and wherein
  • At least a flachtaschenformigen section on a pocket surface which is directly adjacent to an outer wall of the countercurrent cooling gas channel, preferably substantially parallel, with a gap between the pocket surface and the outer wall, on the pocket surface and / or attached to the outer wall knocking elements in this Protrude interstice.
  • the longitudinal direction is to be understood as the direction in which the cooling gas flows in operation through these two sections of the countercurrent cooling gas channel, that is to say from the
  • two sections of a straight tube in which the cooling gas flows would have no differently oriented longitudinal directions.
  • flat-pocket-shaped section is to be understood as meaning a section whose extent in two dimensions is significantly greater than in the third dimension, this third dimension being essentially perpendicular to the longitudinal direction of the countercurrent exhaust gas duct In the longitudinal direction to understand the direction in which the exhaust gas flows in operation through the flat-pocket-shaped portion of the counterflow exhaust passage, that is, from the inlet opening toward the outlet opening
  • the flat-pocket-shaped section is thus dimensioned significantly larger in its length and its width than in its thickness.
  • the expansion in length and width is also called pocket area in the episode.
  • the outer contour of a flat pocket substantially corresponds to a plate whose thickness is significantly smaller compared to the length and width.
  • At least the pocket-like portion preferably the entire counterflow exhaust passage, is made of metal to allow good indirect heat exchange
  • the flat-pocket-shaped section is limited by metal plates - made of metal.
  • the metal plates which form the two pocket surfaces of a flat pocket, lie opposite each other and are connected according to the invention by stiffening elements. If there is a pressure difference between the cooling gas and the exhaust gas, there is a risk that the sheet metal plates forming the pocket surfaces buckle in the direction of the lower pressure or bulge out from the region of higher pressure. Changing pressure conditions would be accompanied by changes in the extent of denting or buckling. This stresses the material and changes the flow conditions possibly unfavorably. To avoid such disadvantages, stiffening elements are provided between a pair of opposed sheet metal plates of a flat bag.
  • Stiffening elements can be connected to both metal plates or only one.
  • the stiffening elements prevent the metal sheets from buckling in or out - the flat pockets are thus stiffened.
  • a cooling gas blower that blows cooling gas into the device according to the invention generally builds an overpressure of approximately 300 Pascals.
  • Exhaust gas of a metallurgical plant is usually supplied to the device according to the invention with a negative pressure of about 500 Pascal.
  • When passing through the device according to the invention is usually a pressure drop of about 700 Pascal added.
  • the inventive method is preferably carried out with a pressure difference between exhaust gas in the counterflow exhaust passage and cooling gas in the countercurrent cooling gas passage in a range between 500 and 3000 Pascal. At higher pressure differences, the material is stressed so much that failure in the medium term is expected.
  • the device may be designed such that at least two flat-pocket-shaped sections lie side by side with their pocket surfaces, preferably substantially parallel, with a gap between the two directly adjacent ones
  • cooling gas flows through this intermediate space in countercurrent to the exhaust gas in the flat-pocket-shaped sections, ie it is part of the countercurrent cooling gas channel.
  • the device can also be designed so that at least one
  • the outer wall of the countercurrent refrigerant gas passage is a wall defining the countercurrent refrigerant gas passage against the outside atmosphere.
  • knocking elements protrude into the space.
  • Knocking elements on directly adjacent pocket surfaces or on directly adjacent pocket surface and outer wall are therefore preferably arranged such that they engage in the case of a sufficiently large movement of a pocket surface in the direction of the directly adjacent pocket surface or in the direction of the outer wall
  • Tapping element of this pocket surface or the outer wall can touch. Such an arrangement is referred to as being aligned in the context of this application. There is a gap between aligned knocking elements; usually in the
  • the pocket surfaces are largely prevented by the stiffening elements at a bulge or denting, however, the metal plates of the pocket surfaces can be offset by the gas streams of refrigerant gas and exhaust gas in vibrations - especially by fluctuations in the pressure difference between the exhaust gas and the cooling gas. Due to the vibrations, the knocking elements of a pocket surface in the direction of the knocking elements of the direct
  • Sheet metal plates - and thus a knocking element - are aligned with each other knocking elements or push knocking elements to directly adjacent
  • the detached dust is preferably at least partially in one of the
  • Device according to the invention included dust discharge device transferred - in which he falls into it, for example - and there from the device according to the invention
  • the countercurrent exhaust duct comprises one or more
  • flat-pocket-shaped sections with at least one inlet opening and at least one outlet opening for exhaust gas - also called flat pockets -, wherein a flat pocket is thus a metallic sheet metal duct, through which the exhaust gas is passed.
  • a flat pocket preferably comprises at least parallel flat pocket surfaces.
  • Embodiment all boundary surfaces of a flat pocket in pairs in parallel. But there may also be non-parallel boundary surfaces, such as boundary surfaces, which make up the thickness of the flat bag - also
  • Called longitudinal side surfaces For example, such longitudinal side surfaces can be executed canted.
  • the walls of the flat pockets made of thin sheet with thicknesses of 2mm to 5mm - as the preferred thickness, 3mm has been found.
  • These thicknesses ensure that economic production, assembly and low-maintenance operation of the device according to the invention is ensured and the necessary properties - good heat transfer, sufficient rigidity, the lowest possible weight and sufficient abrasion resistance in the exhaust duct - the flat bags are given.
  • a typical flat bag is 3,6,9 or 12 meters long, and 1, one and a half, 2 or 3 meters wide, and 50 to 150 mm thick.
  • the at least two sections of the counterflow cooling gas channel with different oriented longitudinal directions are largely vertical. In this way, the savings of required footprint can be maximized.
  • the counterflow cooling gas channel opens into a cooling gas discharge line. This makes it easy to supply the heated cooling gas to use its heat content of other use.
  • the cooling gas supply line comprises devices for the continuous regulation of the flow of cooling gas.
  • Such a multi-generous design reduces the height required for a particular exchange surface.
  • the device is erected standing on a floor, wherein the cooling gas supply line at least one blower, preferably only a blower, has, characterized in that the blower is mounted at the level of the soil.
  • the cooling gas supply line at least one blower, preferably only a blower, has, characterized in that the blower is mounted at the level of the soil.
  • the countercurrent exhaust gas channel also has at least two sections with differently oriented longitudinal directions, which are preferably parallel.
  • the at least two sections of the countercurrent exhaust gas duct with differently oriented longitudinal directions are largely vertical.
  • the device comprises a
  • the Staubaustragsvoriques may be, for example, a rotary valve or a screw or a chain conveyor.
  • transition section between the at least two sections of the countercurrent exhaust gas duct with different oriented longitudinal directions, which comprises the dust discharge device.
  • Dust in the exhaust gas for example coarse particles entrained in the exhaust gas
  • the provision of dust discharge devices in such locations facilitates the removal of this dust from the counterflow exhaust passage;
  • such Staubaustragsvoriquesen lie at the lowest point of the counterflow exhaust passage, for example, where a reversal of the flow direction.
  • Dust removed from the flat pockets by the tapping elements can also be collected in such dust discharge devices and discharged from the device. This is particularly pronounced when a reversal of the flow direction takes place from top to bottom, flowing from bottom to top; especially then, as a result of the reversal below the local area of the countercurrent exhaust gas passage can act as a coarse particle.
  • a forced draft condenser according to the invention can thus also be regarded as a spark arrester.
  • the cooling baffles may be provided in the countercurrent cooling gas duct.
  • the invention may be present. For example, it will be two, three, or more Exhaust gas flows through devices in parallel, it being preferred to supply them with exhaust gas, for example via a common exhaust pipe. From this exhaust pipe then the respective exhaust gas supply lines of the individual devices can go out. Accordingly, it is also preferred in such a case to let the exhaust gas discharge lines of the individual devices lead into a discharge. This reduces the construction costs.
  • a stiffening element may for example be a frame, or non-planar
  • Metal sheets such as trapezoidal sheets, or ribs, or with each other
  • Spacers are designed for example as rods. There may also be several types of stiffening elements in a flat pocket, for example rods between the pocket surfaces, and trapezoidal sheets connecting the sheets of the pocket surfaces.
  • At least one stiffening element and at least one knocking elements consist of a single workpiece; for example, from a rod which passes through at least one metal plate of a pocket surface and is connected to it. It protrudes into the space on at least one side and serves as a knocking element. Between the pocket surfaces of the flat pocket he serves as
  • FIG. 1 shows schematically a method sequence according to the invention.
  • FIG. 2 shows schematically an overall external view of a device according to the invention.
  • FIG. 3 schematically shows a device according to the invention in an oblique view.
  • FIG. 4 shows an oblique view of a flat pocket-shaped section, called a flat pocket.
  • Figure 5a / b shows schematically, aligned arranged knocking elements.
  • FIG. 1 shows schematically the sequence of a method according to the invention.
  • a device 1 for cooling dust-laden exhaust gas from a metallurgical plant with an exhaust gas supply line 2, an exhaust discharge line 3, a
  • Exhaust gas discharge line 3 opens.
  • the countercurrent cooling gas channel 5 and countercurrent exhaust duct 6 to the mutual indirect countercurrent gas gas
  • the countercurrent cooling gas channel 5 here has two sections 7, 8, each of which is vertical and parallel to one another, with different oriented longitudinal directions.
  • the exhaust gas, represented by wavy arrows, is through the
  • Cooling gas - in the present case air is used as cooling gas, ie cooling air - represented by transparent arrows, cooled by indirect heat transfer.
  • cooling air - represented by transparent arrows
  • the transition between sections 7,8 is shown with dashed border da er in the illustration of Figure 1 at a height with a portion of the counterflow exhaust passage 6 extends.
  • the arrow representing the cooling gas is shown surrounded by dashed lines in this transition.
  • the exhaust gas comes from a metallurgical plant, for example from a
  • the counterflow exhaust passage 6 has two vertical, parallel sections with different oriented
  • a transition section 9 between the two vertical sections of the counterflow exhaust passage 6 comprises a dust discharge device 10, shown a
  • the countercurrent cooling gas channel 5 opens into a cooling gas discharge line 1 1.
  • the supply of cooling gas is controlled continuously, including the cooling gas supply line. 4
  • FIG. 2 shows a schematic overall view of a device according to the invention in which three lines of exhaust gas and cooling gas are flowed through next to one another, wherein they are supplied with exhaust gas to be cooled via a common exhaust gas supply line 2.
  • the device is erected standing on a floor 14, wherein the cooling gas supply lines 13a, 13b, 13c each have a fan 15a, 15b, 15c, which are mounted at the level of the floor and are continuously or discretely adjustable.
  • the 3 blowers could be replaced by a single larger one.
  • the cooling air supply to this fan is split to the respective countercurrent refrigerant gas channels. It is also preferable to let the exhaust discharge lines of the individual line trains lead into a discharge. This reduces the construction costs.
  • FIG. 3 shows a device 1 according to the invention for cooling dust-laden exhaust gas from a metallurgical plant, which is operated analogously to FIG.
  • Hot dust-laden exhaust gas 16 enters the right side of the device in the
  • Exhaust gas supply line 2 and left exits chilled dust-laden exhaust gas 17, from the exhaust gas discharge line 3. Cooling cooling gas 18 enters the left in the device into the
  • Cooling gas supply line 4, and heated cooling gas 19 exits the right of the device, from the cooling gas discharge line 1 1.
  • the exhaust gas supply line 2 opens into
  • the cooling gas supply line 4 opens into a countercurrent cooling gas channel 21, which is formed by the space between the flaschenaschenförmigen sections and the outer walls 21 - for clarity, only one of the outer walls of the cooling gas channel is provided with reference numeral 38.
  • Counterflow exhaust passage are designed for mutual indirect countercurrent gas-gas heat transfer.
  • the countercurrent cooling gas duct here has two sections 7, 8, each of which is vertical and parallel to one another, with different oriented longitudinal directions.
  • the exhaust gas is cooled by indirect heat transfer by the cooling gas - in the present case air serves as cooling gas, ie cooling air.
  • Exhaust gas flow and cooling gas flow are schematically represented by lines connecting the arrows 16 and 17 and the arrows 18 and 19, respectively. It is for the cooling gas
  • the exhaust gas comes from a metallurgical plant, for example from a
  • the counterflow exhaust passage has two vertical, parallel sections with different oriented ones
  • a transition section 9 between the two vertical sections of the countercurrent exhaust duct comprises a Staubaustragsvornchtung 10, shown a rotary valve.
  • Figure 4 shows an oblique view of a flat pocket-shaped portion, called flat pocket 23.
  • Exhaust gas represented by an arrow enters the left into the flat pocket and right.
  • the expansion of the flat pocket is significantly larger in 2 dimensions a, b than in the third dimension c, this third dimension c being substantially perpendicular to the longitudinal direction of the counterflow exhaust gas duct.
  • the longitudinal direction is to be understood as the direction in which the exhaust gas flows through the flat-pocket-shaped section during operation, ie from the inlet opening to the left in the direction of the outlet opening on the right.
  • the flat-pocket-shaped portion is bounded on two opposite sides in the first-mentioned 2 dimensions, which are significantly larger in relation to the thickness of the flat pockets in the third dimension c, by metal plates 24, 25 made of metal.
  • the flat-pocket-shaped section is thus dimensioned significantly larger in its length and its width than in its thickness. The expansion in length and width will also be considered.
  • the outer contour of the flat pocket substantially corresponds to a plate whose thickness is significantly smaller compared to the length and width.
  • the flaschenaschenförmige section is limited by metal plates - made of metal - limited; on the longitudinal side surfaces 26, 27 by folded metal sheets.
  • Knocking elements 30,31, 32nd Stiffening element 28 and knocking elements 31, 32 consist of a single workpiece; namely from a rod which passes through both metal plates 24,25 of the pocket surfaces and is connected to them. If a further flat pocket or an outer wall is located directly adjacent to the flat pocket 23, the rod protrudes into the intermediate spaces formed between them and serves as knock elements. Between the pocket surfaces of the flat pocket it serves as a stiffening element.
  • Figure 5a shows schematically how aligned arranged tapping elements 33,34 - as in Figure 4 from a rod, which also serves as a stiffening element formed - in the
  • Figure 5b shows schematically how they collide - represented by a star - when the two flat pockets vibrate corresponding to each other.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Environmental & Geological Engineering (AREA)
  • Waste-Gas Treatment And Other Accessory Devices For Furnaces (AREA)
  • Separating Particles In Gases By Inertia (AREA)

Abstract

L'invention concerne un procédé de refroidissement d'effluents gazeux chargés de poussières provenant d'une installation métallurgique. Le but de cette invention est de proposer un procédé et un dispositif de refroidissement d'effluents gazeux chauds chargés de poussières provenant d'une installation métallurgique par transfert de chaleur indirect. Le but est atteint par un procédé dans lequel les effluents gazeux sont refroidis par un gaz de refroidissement par transfert de chaleur indirect et les effluents gazeux sont amenés au refroidissement à une température supérieure à 650°C. Le gaz de refroidissement change au moins une fois de sens d'écoulement, de préférence le sens d'écoulement est inversé et les effluents gazeux sont refroidis selon le principe de l'écoulement à contre-courant.
EP15741781.7A 2014-03-24 2015-03-24 Échangeur de chaleur à contre-courant avec guidage forcé du gaz/de l'air Active EP3123092B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14161227.5A EP2924384A1 (fr) 2014-03-24 2014-03-24 Échangeur de chaleur à contre-courant avec guidage forcé du gaz/de l'air
PCT/EP2015/056171 WO2015144651A2 (fr) 2014-03-24 2015-03-24 Échangeur de chaleur à contre-courant pour effluents gazeux chargés de poussières d'installations métallurgiques

Publications (2)

Publication Number Publication Date
EP3123092A2 true EP3123092A2 (fr) 2017-02-01
EP3123092B1 EP3123092B1 (fr) 2019-05-08

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP14161227.5A Withdrawn EP2924384A1 (fr) 2014-03-24 2014-03-24 Échangeur de chaleur à contre-courant avec guidage forcé du gaz/de l'air
EP15741781.7A Active EP3123092B1 (fr) 2014-03-24 2015-03-24 Échangeur de chaleur à contre-courant avec guidage forcé du gaz/de l'air

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Application Number Title Priority Date Filing Date
EP14161227.5A Withdrawn EP2924384A1 (fr) 2014-03-24 2014-03-24 Échangeur de chaleur à contre-courant avec guidage forcé du gaz/de l'air

Country Status (5)

Country Link
EP (2) EP2924384A1 (fr)
CN (1) CN106461358A (fr)
RU (1) RU2677555C2 (fr)
TR (1) TR201909188T4 (fr)
WO (1) WO2015144651A2 (fr)

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Publication number Priority date Publication date Assignee Title
DE102016114710A1 (de) * 2016-08-09 2018-02-15 Thyssenkrupp Ag Plattenwärmetauscher, Synthesevorrichtung und Verfahren zur Herstellung eines Produkts
EP3567329A1 (fr) * 2018-05-09 2019-11-13 Linde Aktiengesellschaft Dispositif d'extraction du condensat et échangeur thermique

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US3842904A (en) * 1972-06-15 1974-10-22 Aronetics Inc Heat exchanger
WO1985002671A1 (fr) * 1983-12-07 1985-06-20 Licencia Találmányokat Értékesito^" Vállalat Procede et installation d'echange thermique recuperateur pour retirer des impuretes d'air chaud pollue, en particulier de gaz de fumees, et pour reduire la corrosion des cheminees
RU2104454C1 (ru) * 1992-10-27 1998-02-10 Акционерное общество открытого типа "Уралэнергоцветмет" Теплоутилизационный агрегат-охладитель отходящих печных газов
FR2706993B1 (fr) * 1993-06-23 1995-08-18 Valeo Thermique Moteur Sa
JP3300192B2 (ja) * 1995-03-27 2002-07-08 サンデン株式会社 熱交換器
DE19801753A1 (de) * 1998-01-20 1999-07-22 Ibb Engineering Gmbh Verfahren zur Kühlung oder Aufheizung nicht-rieselfähiger Schüttgüter
FR2878318B1 (fr) * 2004-11-22 2007-03-30 Air Liquide Echangeur de chaleur indirect
DE502005010654D1 (de) * 2005-09-07 2011-01-20 Modine Mfg Co Wärmetauscher
US7849692B2 (en) * 2006-07-31 2010-12-14 Caterpillar Inc Segmented heat exchanger

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RU2016137902A (ru) 2018-04-26
RU2016137902A3 (fr) 2018-11-13
EP2924384A1 (fr) 2015-09-30
RU2677555C2 (ru) 2019-01-17
CN106461358A (zh) 2017-02-22
WO2015144651A3 (fr) 2015-11-19
TR201909188T4 (tr) 2019-07-22
WO2015144651A2 (fr) 2015-10-01
EP3123092B1 (fr) 2019-05-08

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