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WO2020229435A1 - Cyclone échangeur de chaleur - Google Patents

Cyclone échangeur de chaleur Download PDF

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Publication number
WO2020229435A1
WO2020229435A1 PCT/EP2020/063108 EP2020063108W WO2020229435A1 WO 2020229435 A1 WO2020229435 A1 WO 2020229435A1 EP 2020063108 W EP2020063108 W EP 2020063108W WO 2020229435 A1 WO2020229435 A1 WO 2020229435A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
gas
inlet
granular material
cyclone
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/EP2020/063108
Other languages
German (de)
English (en)
Inventor
Francois GREPINET
Hubertus Winkelhorst
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.)
KHD Humboldt Wedag AG
Original Assignee
KHD Humboldt Wedag AG
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 KHD Humboldt Wedag AG filed Critical KHD Humboldt Wedag AG
Publication of WO2020229435A1 publication Critical patent/WO2020229435A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories or equipment specially adapted for rotary-drum furnaces
    • F27B7/2016—Arrangements of preheating devices for the charge
    • F27B7/2025—Arrangements of preheating devices for the charge consisting of a single string of cyclones
    • C—CHEMISTRY; METALLURGY
    • C04—CEMENTS; CONCRETE; ARTIFICIAL STONE; CERAMICS; REFRACTORIES
    • C04B—LIME, MAGNESIA; SLAG; CEMENTS; COMPOSITIONS THEREOF, e.g. MORTARS, CONCRETE OR LIKE BUILDING MATERIALS; ARTIFICIAL STONE; CERAMICS; REFRACTORIES; TREATMENT OF NATURAL STONE
    • C04B7/00—Hydraulic cements
    • C04B7/36—Manufacture of hydraulic cements in general
    • C04B7/43—Heat treatment, e.g. precalcining, burning, melting; Cooling
    • C04B7/432—Preheating without addition of fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B15/00—Fluidised-bed furnaces; Other furnaces using or treating finely-divided materials in dispersion
    • F27B15/003—Cyclones or chain of cyclones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories or equipment specially adapted for rotary-drum furnaces
    • F27B7/2016—Arrangements of preheating devices for the charge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories or equipment specially adapted for rotary-drum furnaces
    • F27B7/2016—Arrangements of preheating devices for the charge
    • F27B7/2041—Arrangements of preheating devices for the charge consisting of at least two strings of cyclones with two different admissions of raw material
    • 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
    • F27D13/00—Apparatus for preheating charges; Arrangements for preheating charges
    • 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
    • F27D17/10—Arrangements for using waste heat
    • 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
    • F27D17/20—Arrangements for treatment or cleaning of waste gases
    • F27D17/22—Arrangements for treatment or cleaning of waste gases for removing solid constituents
    • F27D17/25—Arrangements for treatment or cleaning of waste gases for removing solid constituents using cyclones

Definitions

  • the invention relates to a heat exchanger cyclone for exchanging heat between a dusty to granular material and a gas, having an inlet for gas, an outlet for gas, an inlet for the powdery to granular material, an outlet for the powdery to granular material, wherein the heat exchanger cyclone furthermore has a cylindrical separating space which is adjoined at the bottom by a conical separating space, the cylindrical separating space and the conical separating space merging into one another, and a dip tube for the gas protruding into the common separating space.
  • a typical plant for the production of cement clinker produces between 1,000 t and 10,000 l of cement clinker per day, the cement clinker being transported within the plant suspended in gas through a cyclone heat exchanger.
  • Dust separators are designed to separate dust particles of less than 100 ⁇ m or granular substances with a diameter of up to 500 ⁇ m suspended in the gas flow from the gas flow, dust separators, which work according to the cyclone principle, carry a common gas and dust and particle flow to the cyclone and separate the common dust / particle and gas flow into an isolated dust / particle flow and a gas flow.
  • the separation principle is used in a cyclone heat exchanger for heat exchange. The dust / particle flow, which is always divided into individual flows, is always reunited with the gas flow and separated again.
  • the first cyclone in the direction of the material flow also works according to this principle.
  • the feeding of the raw meal in the aforementioned quantities of 1,000 to 10,000 t per day into the first cyclone in the cyclone heat exchanger leads to a considerable pressure loss, which has to be compensated for by appropriate fans, whereby the compensation of the pressure loss involves considerable amounts of non-recoverable electrical energy consumed.
  • the object of the invention is therefore to provide a heat exchanger cyclone for a Zyk ion heat exchanger, the pressure loss index of which is reduced compared to heat exchanger cyclones from the prior art.
  • the heat exchanger cyclone has a total of at least four inputs and outputs. It is provided that the inlet for the powdery to granular material as the second inlet is separate from the inlet for the gas as the first inlet. In contrast to what is provided in the prior art, namely cyclones which have been installed for over 100 years, the invention provides for the inlet for the gas flow and the dust / particle flow to be separated into two different inlet flows.
  • the first inlet for the gas into the heat exchanger cyclone is designed as a tangential opening in the part of the wall of the cylindrical part of the common separation space.
  • the tangential opening creates an annular flow in the heat exchanger cyclone, which helps to separate gas and dusty to granular material despite good heat transfer.
  • the second inlet for the dust-like to granular material is arranged on the roof of the cylindrical separation space, a cone and / or a convex body being arranged below the second inlet for the dust-like to granular material, over which the powdery to granular material slides into the common separation space.
  • the cone and / or the convex body helps to distribute the dust-like to granular material evenly in the cylindrical part of the common separation space.
  • the cone and / or the convex body is advantageously designed as the roof of the dip tube.
  • the cone or the convex body can be held in position by the immersion tube.
  • the cone and / or the convex body are designed as a double roof surface, wherein the two roof surfaces are spaced apart and form a conical annular gap nozzle between them as the upper roof surface and the lower roof surface, and a feed line opening into the annular gap nozzle from the outside leads conveying gas into the conical annular gap nozzle, the upper roof surface as a slide for the dusty up granular material acts, and the annular gap nozzle distributes the compressed gas exiting it evenly in the common separation space, whereby the compressed gas carries along the dusty to granular material with it and also distributes it in the common separation space.
  • the nozzle created by the two spaced roof surfaces distributes gas flowing through evenly on all sides in the cylindrical separating space, so that the entrained dusty to granular material is evenly distributed in the separating space and the best possible heat transfer takes place.
  • an advantageous embodiment of the invention provides that at least one spiral-shaped baffle is arranged between the two roof surfaces, which guides the compressed gas with a radial directional component into the common separation space.
  • the escaping gas thus enters the cylindrical separating space of the common separating space with a radial directional component and thus creates a circular path for the gas and the dusty to granular material.
  • the circular path supports an optimal separating effect of the cyclone.
  • the outlet for gas for discharging the gas from the heat exchanger cyclone is arranged as the first outlet at the lower end of the immersion tube, the immersion tube leading out of the wall of the conical separation space from the common separation space.
  • the gas leaves the cyclone downwards and is not directed upwards through a dip tube.
  • the immersion tube has at least one radial confluence opening, which leads the gas from the separation space in a tangential direction into the immersion tube via an optional, at least one corresponding baffle, the radial confluence opening in the cylindrical Separation space of the common separation space is arranged.
  • the upper cylindrical separation space offers more space so that a larger opening can be provided for the gas.
  • the heat exchanger cyclone is designed as a twin cyclone with the opposite direction of rotation of the inflowing gas.
  • Fig. 1 is a perspective external view of a heat exchanger cyclone according to the invention
  • FIG. 2 the heat exchanger cyclone from FIG. 1 in a broken view
  • FIG. 3 is an isometric side view of the heat exchanger cyclone from FIG.
  • FIG. 5 shows the heat exchanger cyclone from FIG. 4 in a broken view
  • FIG. 6 shows a detailed representation from FIG. 5,
  • FIG. 7 shows the detailed illustration from FIG. 6 in a view from above
  • FIG. 8 shows a heat exchanger cyclone according to the invention in a first configuration of the material task with three inlets for the material
  • FIG. 9 shows a heat exchanger cyclone according to the invention in a second configuration of the material task with four inlets for the material
  • 10 shows a heat exchanger cyclone according to the invention in a third embodiment of the material feed with an annular inlet for the material
  • FIG. 11 shows an inventive heat exchanger cyclone as a double or twin cyclone in a broken view
  • FIG. 12 shows the heat exchanger cyclone according to the invention from FIG. 11,
  • FIG. 6 shows a sketch of the dust separator from FIG. 14 in a broken view from the PRIOR ART.
  • FIG. 1 shows a perspective external view of a heat exchanger cyclone 1 according to the invention.
  • dust-like (grain size up to a maximum of 100 ⁇ m) particulate or granular (grain size up to 500 ⁇ m) material 2 and hot gas 3 flows into different inlets 5 and 6.
  • the cooled gas 3 leaves the heat exchanger cyclone 1 via an outlet 4 for gas, whereas the dusty, particulate or granular material 2 leaves the heat exchanger cyclone 1 via an outlet 7 downwards.
  • the heat exchanger cyclone 1 itself has a cylindrical separation space 8 and a conical separation space 9, which merge into one another.
  • the inlet 5 for the gas is located in the part of the wall 19 of the cylindrical separating space 8 as a tan gential opening 18. If the gas 3 flows tangentially into the cylindrical separating space 8, a vortex is formed in the cylindrical separating space along the outer wall , also called cyclone. This vortex or cyclone-like flow helps to separate good 2 and gas 3 from each other again.
  • the roof 11 of the heat exchanger cyclone presented here is conical, but can also be designed as a flat roof. In the drawing it can be seen that a submerged tube 10 emerges from the conical separation space 9, which extends into the cylindrical separation space of the heat exchanger cyclone 1 and through which the gas 3 leaves the heat exchanger cyclone again.
  • FIG 2 of the heat exchanger cyclone 1 from Figure 1 is shown in a Wegbroche NEN view, from which the inner components of the heat exchanger cyclone 1 can be seen.
  • the dust-like, particulate or granular material 2 entering the heat exchanger cyclone 1 falls through the inlet 6 onto a cone 12 which, in this embodiment, is formed directly below the roof 11 of the heat exchanger cyclone 1 as the roof of the immersion pipe 10.
  • the dusty, particulate or granular material 2 entering the heat exchanger cyclone 1 slides evenly in different radial directions and is guided in a ring into the cylindrical separating space 8, where it is filled by the hot gas 3, which via the tangential opening 18 of the inlet 5 for gas in the heat exchanger cyclone 1 enters, carried into the cylindrical separating space 8 and directed on a spiral path which is generated by the sum of the annular flow of the Ga ses and the earth's gravity.
  • the spiral path is outlined in Fi gur 3 as the path of the property 2.
  • the hot gas 3 enters the immersion tube 10 from the cylindrical separating space 8 through a confluence opening 15 as an inlet 15.
  • Optionally existing tangential baffles 17 help guide the gas 3 into the immersion tube 10.
  • the dusty to granular material 2 located on the circular path cannot flow inwards due to the centrifugal force that arises in the spiral path, so that a separation between dusty, particulate or granular material 2 and gas 3 occurs. Due to the shear force, the material 2 falls down, where due to the conical shape of the conical separating space 9 with its narrowing circular path, an acceleration tion of its angular velocity experiences and down, at bottom 20 of the ko African separation space 9 fails.
  • the gas 3, leaves the heat exchanger cyclone 1 via the outlet 4 in the immersion tube 10, which can be seen in the sectional drawing in FIGS. 2 and 3.
  • FIG. 3 shows an isometric view of the perforated heat exchanger cyclone 1 in FIG. 2, but with material 2 falling in from above through the inlet 6 being shown.
  • the material 2 falls onto the cone 12, which in this embodiment of the heat exchanger cyclone 1 is formed directly below the roof 11 of the heat exchanger cyclone 1 as the roof of the immersion tube 10 entering the heat exchanger cyclone 1 from below.
  • the material 2 slides over the cone 12 in different directions into the cylindrical separating space 8, where it is carried along by the gas 3 on a circular path, as described.
  • the path of the goods 2 is shown by the obliquely running band that seems to encircle the immersion tube 10.
  • At the bottom of the bottom 20 of the conical separating space 9 it is shown how the material 2 leaves the heat exchanger cyclone 1 again.
  • the immersion tube 10 penetrates the wall 14 of the conical separating space 9.
  • FIG. 1 In order to show at which point within a plant of raw meal the heat exchanger cyclone 1 could be used, a principle sketch of such a plant is shown in FIG.
  • Raw meal from calcareous rock and from siliceous rock is fed via a deduster 301 to a cyclone heat exchanger 302, where the raw meal is heated by hot exhaust gases flowing in the opposite direction.
  • the heated raw meal flows into the calciner 304 via a line not shown here and is entrained there in the rising hot exhaust gas of the rotary kiln 306 and fed to the lowest cyclone of the cyclone heat exchanger 302 via a vortex chamber.
  • the inventive Heat exchanger cyclone 1 is to be used as a replacement for the deduster 301 of this system.
  • the deduster 301 is sketched in greater detail as a heat exchanger cyclone from the PRIOR ART.
  • the raw meal is fed into the gas supply to the deduster in the raw meal feed 311 in the gas line 310.
  • the raw meal enters the two dust extractors 301 via the common inlet 312 for dust and gas and is there again separated from the gas, with the raw meal heating up for the first time.
  • the gas emerges from the dust extractor 314 via the exhaust air output 314.
  • FIG. 15 shows a basic sketch to illustrate the mode of operation of a deduster 301 as a first heat exchanger cyclone in a cyclone heat exchanger 302.
  • the gas and dust enter the cyclone via a common inlet for gas and dust and are guided there on a circular path through the tangential inlet.
  • the cyclone tapers and the gas / dust mixture circulating around the immersion tube 320 increases in its angular velocity, as a result of which the dust accumulates with a higher density on the wall of the cone and emerges as raw meal downwards.
  • the gas flows upward out of the cyclone through the central immersion tube 320.
  • the heat exchanger cyclone according to the invention is intended to replace this first cyclone of the cyclone heat exchanger 302. It is provided that the raw meal does not enter the heat exchanger cyclone together with the gas, but rather enters the heat exchanger cyclone 1 separately from one another via different inlets. The other design means that the pressure loss in this first stage is considerably reduced.
  • FIG. 4 an embodiment of the heat exchanger according to the invention is presented.
  • gas is withdrawn via a bypass 140, which is promoted by a fan 141 shown here only as a sketched element.
  • the proportions are here to preserve the sketch function not uniform.
  • the gas 166 conveyed by the fan 141 flows through the supply line 115 into an annular nozzle 114 of the double roof area 111, which consists of two roof areas 112 and 113 that are spaced apart.
  • the material 2 falls through an annular opening that surrounds the supply line 115 onto the upper roof surface
  • baffles 117 are arranged, which guide the incoming, compressed gas 116 on a tangential path and thus support the formation of a cyclone in the heat exchanger cyclone.
  • the compressed gas emerging from the double roof surface 111 from the annular nozzle 114 helps to distribute the material 2 as quickly as possible in the heat exchanger cyclone and to suspend it in the gas 116, as is sketched in the broken view in FIG.
  • the path of the compressed gas 116 is shown, which enters the cylindrical separating space in a ring shape with a tangential component.
  • the double roof surface that rests on the dip tube 10 is shown enlarged and isolated in FIG. In FIG.
  • the compressed gas 116 enters the supply line 115 and exits in a ring between the upper roof surface and the lower roof surface 113, shown by the arrows 116.
  • At least one baffle 117 ensures a flow deflection in a tangential circumferential direction of the compressed gas 116.
  • the double roof area is sketched with a view of the upper roof area 112.
  • the spiral lines correspond to the course of the guide plates 117, which are here arranged in a plurality.
  • FIG. 8 shows a special embodiment of the heat exchanger cyclone according to the invention, in which two heat exchanger cyclones as described above are interconnected as twins and have a common central gas supply.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Ceramic Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Materials Engineering (AREA)
  • Structural Engineering (AREA)
  • Organic Chemistry (AREA)
  • Dispersion Chemistry (AREA)
  • Cyclones (AREA)

Abstract

L'invention concerne un cyclone échangeur de chaleur (1) servant à échanger de la chaleur entre un produit (2) de pulvérulent à granulaire et un gaz (3). Le cyclone échangeur de chaleur comporte une entrée (4) pour du gaz (3), une sortie (5) pour du gaz (3), une entrée (6) pour le produit (2) pulvérulent à granulaire, une sortie (7) pour le produit (2) pulvérulent à granulaire. Le cyclone échangeur de chaleur comporte par ailleurs une chambre de séparation cylindrique (8), à laquelle se raccorde vers le bas une chambre de séparation conique (9). La chambre de séparation cylindrique (8) et la chambre de séparation conique (9) se confondent. Un tuyau plongeur (10) pour le gaz (3) dépasse dans la chambre de séparation (8, 9) commune. L'invention prévoit que l'entrée (6) pour le produit (2) pulvérulent à granulaire est séparée en tant que deuxième entrée de l'entrée (4) pour le gaz en tant que première entrée.
PCT/EP2020/063108 2019-05-13 2020-05-12 Cyclone échangeur de chaleur Ceased WO2020229435A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019112376.3A DE102019112376B4 (de) 2019-05-13 2019-05-13 Wärmetauscherzyklon
DE102019112376.3 2019-05-13

Publications (1)

Publication Number Publication Date
WO2020229435A1 true WO2020229435A1 (fr) 2020-11-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2020/063108 Ceased WO2020229435A1 (fr) 2019-05-13 2020-05-12 Cyclone échangeur de chaleur

Country Status (2)

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DE (1) DE102019112376B4 (fr)
WO (1) WO2020229435A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115215052A (zh) * 2022-06-21 2022-10-21 立达超微科技(安徽青阳)有限公司 一种颗粒料输送转运装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020112554B4 (de) 2020-05-08 2022-08-18 TenneT TSO GmbH Vorrichtung zur Kühlung elektrischer Elemente sowie ein mit einer solchen Vorrichtung ausgestattetes elektrisches Element

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3305940A (en) * 1963-10-14 1967-02-28 Isler Walter Heat exchange between granular material and gas
FR1557177A (fr) * 1967-02-02 1969-02-14
US5131462A (en) * 1988-03-08 1992-07-21 F. L. Smidth & Co. A/S Heat exchanger
CN106440843A (zh) * 2016-12-20 2017-02-22 北京建筑材料科学研究总院有限公司 一种从回转窑取风取热协同除氯的方法及其系统
WO2017060369A1 (fr) * 2015-10-08 2017-04-13 Flsmidth A/S Préchauffeur de suspension d'usine de calcination de ciment à niveaux multiples

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB300841A (en) * 1928-02-25 1928-11-22 William Alexander Improvements in apparatus for purifying steam, vapours and gases centrifugally
DE68902919T2 (de) * 1988-03-08 1993-02-18 Smidth & Co As F L Waermetauscher.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3305940A (en) * 1963-10-14 1967-02-28 Isler Walter Heat exchange between granular material and gas
FR1557177A (fr) * 1967-02-02 1969-02-14
US5131462A (en) * 1988-03-08 1992-07-21 F. L. Smidth & Co. A/S Heat exchanger
WO2017060369A1 (fr) * 2015-10-08 2017-04-13 Flsmidth A/S Préchauffeur de suspension d'usine de calcination de ciment à niveaux multiples
CN106440843A (zh) * 2016-12-20 2017-02-22 北京建筑材料科学研究总院有限公司 一种从回转窑取风取热协同除氯的方法及其系统

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115215052A (zh) * 2022-06-21 2022-10-21 立达超微科技(安徽青阳)有限公司 一种颗粒料输送转运装置
CN115215052B (zh) * 2022-06-21 2023-11-03 立达超微科技(安徽青阳)有限公司 一种颗粒料输送转运装置

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DE102019112376A1 (de) 2020-11-19
DE102019112376B4 (de) 2022-01-05

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