WO2011113732A1 - Installation d'épuration thermique de gaz d'évacuation - Google Patents

Installation d'épuration thermique de gaz d'évacuation Download PDF

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Publication number
WO2011113732A1
WO2011113732A1 PCT/EP2011/053551 EP2011053551W WO2011113732A1 WO 2011113732 A1 WO2011113732 A1 WO 2011113732A1 EP 2011053551 W EP2011053551 W EP 2011053551W WO 2011113732 A1 WO2011113732 A1 WO 2011113732A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
bypass
exhaust air
fluid flow
thermal exhaust
Prior art date
Application number
PCT/EP2011/053551
Other languages
German (de)
English (en)
Inventor
Thorsten Gysin
Erhard Rieder
Original Assignee
Dürr Systems 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 Dürr Systems GmbH filed Critical Dürr Systems GmbH
Priority to EP11708792.4A priority Critical patent/EP2547960B1/fr
Priority to DK11708792.4T priority patent/DK2547960T3/da
Priority to CN201180014368.8A priority patent/CN102803853B/zh
Priority to RU2012143690/03A priority patent/RU2554965C2/ru
Priority to PL11708792T priority patent/PL2547960T3/pl
Publication of WO2011113732A1 publication Critical patent/WO2011113732A1/fr
Priority to HK13100505.3A priority patent/HK1173206A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G7/00—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals
    • F23G7/06—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of waste gases or noxious gases, e.g. exhaust gases
    • F23G7/061—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of waste gases or noxious gases, e.g. exhaust gases with supplementary heating
    • F23G7/065—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of waste gases or noxious gases, e.g. exhaust gases with supplementary heating using gaseous or liquid fuel
    • F23G7/066—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of waste gases or noxious gases, e.g. exhaust gases with supplementary heating using gaseous or liquid fuel preheating the waste gas by the heat of the combustion, e.g. recuperation type incinerator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/50—Control or safety arrangements

Definitions

  • the present invention relates to a thermal exhaust air purification system comprising a combustion chamber and a heat exchanger for transferring heat from a pure gas generated in the combustion chamber to a raw gas to be supplied to the combustion chamber, the heat exchanger having an inner heat exchange space permeable by an inner fluid medium and an outer heat exchange space fluid medium permeable outer heat exchanger chamber comprises.
  • the clean gas emerging from such a thermal exhaust air purification system is often used for further thermodynamic processes, which is why the clean gas outlet temperature must be regulated at the exit from the thermal exhaust air purification system.
  • an internal hot gas bypass valve is used according to the prior art. By opening or partially opening this flap is achieved that very hot clean gas, passed directly from the combustion chamber to the internal clean gas raw gas heat exchanger of the thermal exhaust air purification system and mixed directly to the clean gas exiting the clean gas raw gas heat exchanger exiting clean gas.
  • the mixed stream from the hot clean gas, which originates directly from the combustion chamber, and the pure gas cooled in the clean gas raw gas heat exchanger then assumes a mixing temperature which corresponds to the desired clean gas outlet temperature.
  • the residence time of a gas molecule in the so-called reaction space is calculated as residence time, which is composed of the combustion chamber and a reaction chamber surrounding the combustion chamber.
  • the residence time begins with the entry of the raw gas through the burner into the combustion chamber and ends with the entry of the clean gas into the clean gas raw gas heat exchanger, in which the clean gas is cooled by heat transfer to the raw gas.
  • a known remedy for this problem is to introduce a further deflection in the reaction chamber, which at least partially compensates for the shortening of the residence time for the withdrawn through the hot gas bypass valve partial flow of the exhaust air.
  • the disadvantage of such a deflection chamber is that due to its design, this reduces the residence time for the partial flow not drawn by the hot gas bypass flap.
  • the thermal exhaust air purification system must be built longer and increased in volume, which increases the space requirement of the thermal exhaust air purification system.
  • the present invention has for its object to provide a thermal exhaust air purification system of the type mentioned, which allows a regulation of the clean gas outlet temperature, without reducing the clean gas quality.
  • thermal exhaust air purification system having the features of the preamble of claim 1 according to the invention that the thermal exhaust air purification system a bypass device with a separation device, by means of which a part of the outer fluid flow is separable as a bypass fluid flow of an outer residual fluid flow, and with an admixing device, by means of which the bypass fluid flow can be mixed again into the residual fluid flow after the residual fluid flow has passed through a section of the outer heat exchanger chamber.
  • the present invention is based on the concept of regulating the clean gas exit temperature of the thermal exhaust air purification system by bypassing a portion of the clean gas raw gas heat exchanger of the thermal exhaust air purification system, whereby the efficiency of the heat exchanger can be reduced in a controlled manner.
  • the external fluid flow may be the raw gas supplied to the heat exchanger or the clean gas supplied to the heat exchanger.
  • the residence time of the exhaust air at the reaction temperature in the reaction space is in no case shortened by this division of the external fluid flow.
  • the clean gas outlet temperature T A can be regulated by means of the controllable pure gas raw gas heat exchanger according to the invention simply by varying the proportion of the bypass fluid flow to the total external fluid flow.
  • the admixing device by means of which the bypass fluid flow is again immiscible into the residual fluid flow, comprises at least one admixing point which extends over at least half of the circumference of the flow path of the residual fluid flow. In this way, the most homogeneous admixture of the cold bypass fluid flow is achieved in the heated in the already passed portion of the outer heat exchanger space residual fluid flow.
  • the admixing device comprises at least one admixing point which extends over at least two-thirds, in particular over at least 90%, of the circumference of the residual fluid flow.
  • the admixing point extends substantially over the entire circumference of the residual fluid flow.
  • the admixing point extends annularly around the flow path of the residual fluid flow around.
  • the high homogeneity of the total fluid flow mixed from the bypass fluid flow and the residual fluid flow improves the thermodynamic properties of the exhaust air purification system.
  • the admixing device can also comprise a plurality of admixing points, wherein these admixing points are distributed over an admixing area which extends over at least half of the circumference of the remainder Fluid stream extends.
  • the admixing region extends over at least two-thirds, preferably over at least 90%, of the circumference of the residual fluid stream.
  • the admixing region extends substantially over the entire circumference of the residual fluid flow.
  • the mixture of the bypass fluid flow with the residual fluid flow preferably takes place at least partially, in particular predominantly, in a mixing space which does not contain a heat exchanger tube of the heat exchanger. This avoids that the cold bypass fluid flow directly applied to a heat exchanger tube, which could lead to high thermal stresses.
  • the mixing chamber can be arranged radially outside a heat exchanger tube bundle of the heat exchanger.
  • the bypass device may comprise a bypass channel, which the
  • bypass fluid flow from the separation device to the admixing device.
  • the bypass channel preferably extends over part of the length of the heat exchanger, preferably over at least one third of the length of the heat exchanger, in particular over at least half the length of the heat exchanger.
  • the bypass device preferably comprises at least one
  • Throttling element in the flow path of the bypass fluid flow.
  • Such a throttle element may in particular be designed as a flow barrier with passage openings.
  • the bypass channel may in particular be formed substantially hollow cylindrical. A particularly good distribution of the bypass fluid flow over the passage cross section of the bypass channel is achieved if the total passage area of the passage openings in the flow barrier is 150% or less, in particular 125% or less, of an inlet cross-sectional area of the bypass device.
  • the total passage area of the passage openings in the flow barrier is 50% or more, in particular 75% or more, of an inlet cross-sectional area of the bypass device.
  • the admixing device is arranged upstream of an outlet of the outer fluid medium from the outer heat exchanger space. In this way, the mixing of the bypass fluid flow in the residual fluid flow is still within the clean gas raw gas heat exchanger, whereby it is achieved that the two partial flows are well mixed together before the outer fluid flow exits the heat exchanger (namely in the combustion chamber, if the raw gas is used as the external fluid, or in a clean gas passage when the clean gas is used as the external fluid).
  • the separating device has a bypass flap for controlling the entry of the bypass fluid flow into the bypass device and a heat exchanger flap for controlling the entry of the residual fluid flow in the Includes heat exchanger.
  • bypass flap and the heat exchanger flap are preferably coupled to one another mechanically and / or by control technology (that is to say by coordinated activation by means of a control device of the thermal exhaust air purification system).
  • This coupling is achieved, for example, by an adaptive flap mechanism.
  • the coupling of the two flaps is preferably carried out so that an opening movement of the bypass flap, through which the inlet cross section of the bypass device is increased, takes place simultaneously with a closing movement of the heat exchanger flap, through which the inlet cross section is reduced in the heat exchanger, and vice versa.
  • the division of the entire outer fluid flow onto the bypass fluid flow and the residual fluid flow can preferably be carried out substantially continuously, whereby the efficiency of the heat exchanger and thus the clean gas discharge temperature can be controlled in a simple manner ,
  • the separation device is preferably arranged upstream of an inlet of the residual fluid flow in the outer heat exchanger space.
  • the outer fluid flow is divided into the bypass fluid flow and the residual fluid flow before the residual fluid flow enters the heat exchanger and is heated or cooled therein.
  • the outer heat exchanger space can be flowed through by the raw gas zu Strukturdem the combustion chamber. In this case, the raw gas is used as the external fluid.
  • the outer heat exchanger space can be flowed through by clean gas generated in the combustion chamber.
  • the clean gas is used as the external fluid.
  • the present invention further relates to a method for purifying a crude gas stream containing oxidizable constituents by means of a thermal exhaust air purification system, which comprises the following method steps: Supplying the raw gas stream to a combustion chamber;
  • the heat exchanger comprises an inner heat exchanger chamber through which an inner fluid medium flows and an outer heat exchanger chamber through which an external fluid medium flows.
  • the present invention is based on the further object of providing a method of the type mentioned above, which allows a control of the pure gas outlet temperature without impairing the quality of the clean gas.
  • the inventive thermal exhaust air purification system is preferably designed as a recuperative exhaust air purification system with a recuperative clean gas Rohgas- heat exchanger. Since the clean gas outlet temperature can be increased if necessary by the controllable heat exchanger used in the thermal exhaust air cleaning system according to the invention when using the bypass device, it is useful, the operating point of the thermal exhaust air purification system not to the target outlet temperature of the clean gas, but to a slightly lower temperature, preferably to a lower by at least 10 ° C lower temperature, in particular to a lower by about 20 ° C temperature to interpret.
  • a ⁇ can then be controlled by controlling the heat exchanger by means of the bypass flap and the heat exchanger cover the actually required clean gas outlet temperature T A.
  • the clean gas outlet temperature can be regulated without the use of a hot gas bypass flap.
  • thermo exhaust air cleaning system may be provided with such a hot gas bypass door in addition to the bypass device.
  • the residence time of the exhaust air to be cleaned in the combustion chamber and a reaction chamber following the combustion chamber or a clean gas channel following the combustion chamber always remains the same regardless of the control setting of the bypass device.
  • the primary energy demand of the thermal exhaust air purification system during break time is significantly reduced.
  • these two partial streams are homogeneously mixed with each other before the entry of the raw gas into the burner, whereby a stable cleaning performance of the exhaust air purification system is achieved.
  • the uniform admixture of the bypass fluid flow over a considerable proportion of the circumference, preferably over the entire circumference, of the residual Fluid flow reduces the thermal stresses caused by temperature gradients to a minimum.
  • the thermal exhaust air purification system is designed so that the design temperature at the operating point of the thermal exhaust air purification system is lower than the target outlet temperature of the clean gas, by means of the variable heat exchanger, the actual clean gas outlet temperature during operation of the thermal exhaust air purification system both to a temperature above the target outlet temperature as well as adjusted to a temperature below the target outlet temperature.
  • FIG. 1 is a schematic block diagram of a thermal exhaust air purification system with a controllable clean gas Rohgas-Wärmetau- shear, in which a bypass fluid stream of the raw gas before entering the heat exchanger of a residual fluid stream of the raw gas is separated and the bypass fluid stream the rest - Fluid flow is reusable before exiting the heat exchanger;
  • FIG. 2 shows a schematic longitudinal section through a combustion chamber, a clean gas raw gas heat exchanger surrounding the combustion chamber and a bypass device with separation device and admixing device of the thermal exhaust air purification system from FIG. 1; a schematic longitudinal section through a second embodiment of a combustion chamber, surrounding the combustion chamber clean gas raw gas heat exchanger and a bypass device with separation device and admixing device; an enlarged view of the area I of FIG. 3; an enlarged view of the area II of Fig. 3; a schematic plan view from above of the thermal exhaust air purification system of Figure 3 in the region of a raw gas inlet into the heat exchanger and a Rohgaseintritts in the bypass device, with the viewing direction in the direction of arrow 6 in Fig. 3.
  • FIG. 3 a schematic cross section through the thermal exhaust air purification system of Figure 3, taken along the line 7-7 in Fig. 3.
  • Fig. 13 is a schematic plan view of a drive device of
  • Fig. 14 is a schematic side view of the drive device for the
  • Fig. 15 is a schematic block diagram of a third embodiment of a thermal exhaust air purification system with a controllable clean gas raw gas heat exchanger, wherein a bypass fluid stream of the clean gas from a residual fluid stream of the clean gas before the entry of pure gas in the clean gas raw gas heat exchanger can be separated and the Bypass fluid flow of the clean gas to the residual fluid flow of the clean gas before emerging from the clean gas raw gas heat exchanger is again mixed.
  • thermal exhaust air purification system includes, as can be seen from the schematic diagram of Fig. 1, a combustion chamber 102, at the combustion chamber inlet a burner 104 is disposed, via a fuel line 106 with a fuel valve 108 a suitable fuel, such as natural gas, and via a cooling air line 110 with a cooling air valve 112 cooling air for an ignition electrode, a sight glass and flame monitoring can be fed.
  • the exhaust air to be cleaned is a gas mixture containing oxidizable components, such as volatile organic compounds.
  • the oxidizable components of the exhaust air are oxidized in the combustion chamber 102, together with the added fuel, and thus made harmless.
  • the gas mixture supplied to the combustion chamber 102 which contains the combustible components, is referred to below as raw gas.
  • the gas mixture produced in the combustion chamber 102 by oxidation of the oxidizable components of the raw gas is referred to below as clean gas.
  • the raw gas comes from a in Fig. 1 purely schematically illustrated and denoted by 114 raw gas source.
  • the raw gas volume flow supplied from the raw gas source 114 to the thermal exhaust air purification system 100 is preferably at least
  • the raw gas from the raw gas source 114 is supplied to a raw gas inlet 116 of the thermal exhaust air purification system 100 via a Rohgaszu111 Gustav 118, in which a Rohgasgebläse 120 is arranged, which promotes the raw gas from the Rohgasario 114 to the combustion chamber 102.
  • the Rohgaszu111 Arthur 118 may be provided with a differential pressure gauge 122, by means of which the differential pressure ⁇ between the pressure side and the suction side of the Rohgasgebläses 120 can be determined.
  • a separation device 124 of a bypass device 126 Downstream of the raw gas inlet 116 into the thermal exhaust air purification system 100 is a separation device 124 of a bypass device 126 arranged, by means of which a part of the crude gas stream as a bypass fluid stream of a residual fluid stream of the raw gas can be separated and fed through a bypass inlet opening 128 a bypass channel 130 of the bypass device 126.
  • the residual fluid flow enters through a raw gas inlet 132 into the secondary side of a recuperative clean gas raw gas heat exchanger 134, which is flowed through on the primary side by the clean gas escaping from the combustion chamber.
  • the pure gas raw gas heat exchanger 134 comprises, as will be explained in more detail later, a heat exchanger tube bundle 136 of a plurality of heat exchanger tubes 138, the interiors together form a permeable by the clean gas inner heat exchanger chamber 140, while limited by a heat exchanger housing 142 outside the Heat exchanger tubes 138 forms a flowing through of the raw gas outer heat exchanger chamber 144.
  • the raw gas in this embodiment of a thermal exhaust air purification system 100 flows through the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134, the raw gas is used in this embodiment as an outer fluid medium.
  • the clean gas which in this embodiment of a thermal exhaust air purification system 100 flows through the inner heat exchanger chamber 140 of the clean gas raw gas heat exchanger 134, serves in this embodiment as an inner fluid medium.
  • An admixing device 148 of the bypass device 126 by means of which the bypass fluid flow of the raw gas can be mixed again into the residual fluid flow of the raw gas, is arranged at a point located between the raw gas inlet 132 and a crude gas outlet 146 of the clean gas raw gas heat exchanger 134 the residual fluid flow of the raw gas between the separating device 124 and the admixing 148 lying portion 150 of the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134 has passed.
  • the admixing device 148 is designed such that the mixing of the bypass fluid flow into the residual fluid flow takes place over a considerable part of the circumference of the residual fluid flow, preferably over the entire circumference of the residual fluid flow, whereby a very good mixing of the two Partial flows (bypass fluid flow and residual fluid flow) to a combined total raw gas flow still within the clean gas raw gas heat exchanger 134 takes place.
  • the residual fluid flow Upon reaching the admixing device 148, the residual fluid flow has a higher temperature than the bypass fluid flow, since the residual fluid flow in the section 150 of the outer heat exchanger chamber 144 has already been heated by heat transfer from the clean gas flowing through the inner heat exchanger chamber 140.
  • the uniform admixture by means of the admixing device 148 it is achieved that from the bypass fluid stream and the residual fluid stream of the raw gas, a combined total raw gas stream is formed, which has a substantially homogeneous temperature distribution, so that the boundary walls of the downstream of the admixing 148th lying and up to the raw gas outlet 146 extending end portion 152 of the outer heat exchanger chamber 144 are all acted upon by raw gas without large temperature gradient.
  • the pure gas raw gas heat exchanger 134 is shown purely schematically as if the outer heat exchanger space 144 is embedded in the inner heat exchanger space 140; However, this type of presentation was chosen only because so the bypass device 126 easier let represent. In fact, the inner heat exchanger space 140 is embedded in the same surrounding outer heat exchanger space 144.
  • the raw gas outlet 146 of the clean gas raw gas heat exchanger 134 is connected to a raw gas inlet 154 of the burner 104, through which the raw gas enters the combustion chamber 102.
  • the thermal exhaust air purification system 100 may be provided with a differential pressure gauge 156, by means of which the differential pressure ⁇ between the combustion chamber 102 on the one hand and the Rohgasaustritt 146 from the pure gas raw gas heat exchanger 134 or the Rohgaseintritt 154 in the burner 104 on the other hand can be determined.
  • a clean gas inlet 160 of the clean gas raw gas heat exchanger 134 is connected, via which the clean gas which has been produced in the combustion chamber 102 enters the inner heat exchanger space 140 of the clean gas raw gas heat exchanger 134.
  • a clean gas line 164 is connected, which leads up to a (not shown) exhaust stack through which the clean gas is discharged into the environment.
  • the clean gas line 164 can be guided by one or more downstream heat exchangers, which are flowed through by the clean gas on the primary side.
  • Such downstream of the clean gas raw gas heat exchanger 134 further heat exchangers can be used to heat a fluid medium or to generate a vapor from a liquid medium.
  • such downstream heat exchangers can be used for steam generation, thermal oil heating, hot water or hot water production or for circulating air or fresh air heating.
  • the thermal exhaust air purification system 100 may include a differential pressure gauge 166, by means of which a pressure difference ⁇ between the clean gas line 164 and the Rohgaseintritt 116 can be determined in the thermal exhaust air purification system 100.
  • a clean gas outlet 158 of the combustion chamber 102 connects, a bypass line 170 can branch off, which opens downstream of the clean gas outlet 162 of the clean gas raw gas heat exchanger 134 in the clean gas line 164.
  • this hot-side bypass line 170 By means of this hot-side bypass line 170, at least part of the clean gas from the combustion chamber 102 can be fed directly to the exhaust gas chimney or the downstream heat exchangers, bypassing the clean gas raw gas heat exchanger 134, in particular if the heat requirement at one of the downstream heat exchangers is particularly high.
  • bypass flow through the hot-side bypass line 170 can be controlled or regulated by means of a bypass flap 172 arranged in the bypass line 170.
  • the combustion chamber 102 and the clean gas raw gas heat exchanger 134 associated therewith of the thermal exhaust air purification system 100 with the bypass device 126 from FIG. 1 are shown in detail in FIG. 2.
  • the combustion chamber 102 is formed substantially cylindrical, along a central longitudinal axis 174 from a burner-side end face 176 facing away from the burner 104 a End face 178 extends and is bounded by a hollow cylindrical combustion chamber wall 180.
  • the combustion chamber 104 is surrounded by the in this embodiment substantially hollow cylindrical clean gas raw gas heat exchanger 134, which on its combustion chamber 104 facing away from the radial outer side by a cylindrical outer heat exchanger housing 182 and at its combustion chamber 102 facing radially inside by a likewise in Substantially cylindrical heat exchanger inner housing 184 is limited.
  • the heat exchanger inner housing 184 is supported on the combustion chamber wall 180 via support rings 186.
  • the heat exchanger tube bundle 136 of the plurality of heat exchanger tubes 138 is arranged.
  • the heat exchanger tubes 138 all extend substantially parallel to the longitudinal axis 174 and form one or more, for example two, cylindrical heat exchanger tube layers 188, in which the heat exchanger tubes 138 each with the same radial distance from the longitudinal axis 174 and along the circumference are arranged substantially equidistantly distributed.
  • Each heat exchanger tube 138 is held on a plurality of, in the direction of the longitudinal axis 174 successive and preferably substantially equidistant from each other arranged holding elements 190 which are formed, for example, as a substantially annular retaining plates 192.
  • the heat exchanger tubes 138 penetrate passage openings in the holding elements and lie with their outer sides 194 in a fluid-tight manner on the holding elements 190, so that substantially no fluid can pass through the holding elements 190 in the regions lying outside of the heat exchanger tubes 138.
  • the heat exchanger tubes 138 are integrally connected to one of the holding elements 190, for example, welded.
  • inner holding elements 190a with a smaller inner radius and a smaller outer radius and outer holding elements 190b with a larger outer radius and a larger inner radius than the inner holding elements 190a follow one another alternately.
  • the inner support members 190a have an inner radius substantially equal to the radius of the outer side of the peripheral wall of the heat exchanger inner housing 184 so that substantially no fluid can pass between the radially inner edge of the inner support members 190a and the heat exchanger inner housing 184.
  • the inner support members 190 a are based on sliding shoes 196 on the heat exchanger inner housing 183, but are not fixed to the
  • Heat exchanger inner housing 184 connected so that the inner Holding members 190a to compensate for different thermal strains due to temperature gradients or due to differences in the thermal expansion coefficients relative to the heat exchanger inner housing 184 in the direction of the longitudinal axis 174 can move.
  • the outer radius of the inner support members 190a is only slightly larger than the outer radius of the heat exchanger tube bundle 136, so that between the outer edge 198 of the inner support members 190a on the one hand and the inside of the heat exchanger outer housing 182 on the other hand, an outer passage gap 200a remains, through which a fluid can happen.
  • the outer radius of the outer retaining elements 190b substantially corresponds to the radius of the inner side of the peripheral wall of the heat exchanger outer housing 182, so that the outer retaining elements 190b bear with their outer edge on the inside of the heat exchanger outer housing 182 and substantially no fluid between the outer retaining elements 190b and the heat exchanger outer housing 182 can pass.
  • the inner radius of the outer support members 190a is only slightly smaller than the inner radius of the heat exchanger tube bundle 136, so that between the inner edge 202 of the outer support members 190b and the heat exchanger inner housing 184, an inner passage gap 200b remains, through which a fluid can pass.
  • the inner support members 190a and the outer support members 190b which are offset from each other in the radial direction of the longitudinal axis 174, a mechanical deflection and a labyrinth-shaped subdivision of the outer heat exchanger chamber 144 of the clean gas Rohgas heat exchanger 134, so that in the outer heat exchanger space 144, a tortuous flow path for a fluid medium is formed.
  • This outer heat exchanger space 144 of the clean gas raw gas heat exchanger 134 is flowed through by the same in the operation of the preheated raw gas, which serves as an outer fluid medium in this embodiment.
  • the raw gas Since the raw gas is forced by the holding members 190, a tortuous flow path, the raw gas flows around the heat exchanger tubes 138, in which the serving as an inner fluid medium clean gas flows, mostly transverse to the longitudinal direction of the heat exchanger tubes 138th
  • the clean gas raw gas heat exchanger 134 operates in this embodiment substantially according to the cross-countercurrent principle.
  • the entry of the raw gas into the clean gas raw gas heat exchanger 134 via the radially projecting from the heat exchanger outer housing 182 separating device 124 of the bypass device 126, which at the burner 104 remote from the end of the clean gas raw gas heat exchanger 134 and preferably at the upper tip is arranged.
  • the separating device 124 comprises an inlet shaft 206, which is connected upstream to the Rohgaszu111 Gustav 118, downstream of the raw gas inlet 132 into the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134 opens and by means of a heat exchanger flap 208 is completely or partially closed.
  • the separation device 124 comprises a bypass shaft 210, which is also connected to the raw gas supply line 118 upstream, downstream flows into the bypass channel 130 of the bypass device 126 and by means of a bypass flap 212 is completely or partially closed.
  • bypass flap 212 in the bypass shaft 210 and the heat exchanger flap 208 in the inlet shaft 206 of the clean gas raw gas heat exchanger 134 are mechanically and / or control technology (ie by means of coordinated control of the flaps by a control device of the thermal exhaust air cleaning system 100) coupled to each other such that they always be opened or closed in opposite directions.
  • bypass door 212 when the bypass door 212 is brought into a position in which it releases a larger inlet cross section for the passage of the raw gas through the bypass shaft 210, by a coupled with the movement of the bypass flap 212 movement of the heat exchanger flap 208, the heat exchanger flap 208 simultaneously in a position brought in which it reduces the inlet cross section for the passage of the raw gas through the entrance shaft 206, and vice versa.
  • the volume fraction of the bypass fluid flow (measured in standard cubic meters) in the total supplied raw gas stream in particular substantially continuously, at least in a range of about 20% to 80% controlled or regulated.
  • the bypass channel 130 is formed in this embodiment of a thermal exhaust air purification system 100 is substantially hollow cylindrical and surrounds a portion of the clean gas raw gas heat exchanger 134 annular.
  • the bypass channel 130 is bounded on its radial inner side facing the clean gas raw gas heat exchanger 134 by the outer heat exchanger housing 182 and on its radial outer side facing away from the clean gas raw gas heat exchanger 134 by a cylindrical bypass outer housing 214.
  • the bypass channel 130 extends along the longitudinal axis 174 of the bypass shaft 210, where the bypass fluid flow into the bypass channel 130, over a portion of the length of the clean gas raw gas heat exchanger 134, preferably over at least one third of the length of the clean gas raw gas Heat exchanger 134, to the admixing device 148 of the bypass device 126, in which the bypass fluid flow is remixed to the residual fluid flow in the outer heat exchanger chamber 144.
  • the admixing device 148 comprises a bypass duct end wall 216, which closes off the hollow cylindrical bypass duct 130 at the end, and an annular passage gap 218 in the heat exchanger outer housing 182, through which the bypass fluid flow from the hollow cylindrical bypass duct 130 into the also hollow cylindrical outer heat exchanger chamber 144 of the clean gas Crude gas heat exchanger 134 may occur.
  • the passage gap 218 thus forms an admixing point 220 which extends over the entire circumference of the outer heat exchanger space 144 and thus over the entire circumference of the flow path of the residual fluid flow flowing through the outer heat exchanger space 144.
  • one or more throttle elements 222 are provided, each as a flow barrier with along the circumference of the throttle element 222, preferably substantially equidistantly, distributed passage openings 224 for the passage of the bypass fluid flow through the throttle element 222 are formed.
  • the total passage area of the passage openings 224 in such a flow barrier is preferably 150% or less of the maximum inlet cross-sectional area, which the bypass flap 212 in the
  • the entire passage area of the passage openings 224 in such a flow barrier is 125% or less, for example approximately 100%, of the maximum inlet cross-sectional area which the bypass flap 212 releases in the bypass shaft 210.
  • the total passage area of the passage openings 224 in such a flow barrier is preferably at least approximately 50%, in particular at least approximately 75%, of the maximum inlet cross-sectional area which the bypass flap 212 releases in the bypass shaft 210.
  • the throttle elements 222 may in particular be formed as a throttle plate with through openings 224, which may be integrally formed with one of the outer holding elements 190 b in the form of a holding plate 192.
  • the outlet of the clean gas from the inner heat exchanger chamber 140 of the clean gas raw gas heat exchanger 134 takes place in a clean gas collection chamber 228 at the end facing away from the burner 104 of the clean gas raw gas heat exchanger 134, in which open the downstream gas ends of the heat exchanger tubes 138.
  • the clean gas line 164 begins, through which the clean gas flows to the optionally downstream heat exchangers and finally to the exhaust chimney.
  • the additional hot-side bypass line 170 through which the clean gas can be conducted past the primary side of the clean gas raw gas heat exchanger 134, is formed in this embodiment by a so-called compensator 230 which, for example, has the shape of a hollow cylinder and, on the one hand, the burner 104 opposite end of the combustion chamber 102 and on the other hand with the clean gas collecting chamber 228 is in fluid communication.
  • compensator 230 which, for example, has the shape of a hollow cylinder and, on the one hand, the burner 104 opposite end of the combustion chamber 102 and on the other hand with the clean gas collecting chamber 228 is in fluid communication.
  • the compensator 230 for example, at its Sammelschschsei- term end, provided with the bypass valve 172, which makes it possible to adjust the proportion of clean gas flow from the combustion chamber 102, which enters directly from the combustion chamber 102 in the clean gas collecting chamber 228, without previously to pass the clean gas raw gas heat exchanger 134.
  • the heat exchanger tubes 138 may be provided on the inside and on the outside of its wall with a turbulence generating surface structure. In particular, it may be provided that the heat exchanger tubes 138 are formed as swirl tubes.
  • the heat exchanger tubes 138 may also be designed as smooth tubes.
  • thermal exhaust air purification system 100 functions as follows:
  • the raw gas from the raw gas source 114 passes to the separating device 124 of the bypass device 126 and is there in the bypass fluid flow, which enters the bypass channel 130, and in the residual fluid flow, which directly into the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134 occurs, split.
  • the volume fraction of the bypass fluid flow and the residual fluid flow on the total raw gas flow depends on the respectively set position of the bypass flap 212 and the heat exchanger flap 208.
  • the outlet temperature of the clean gas can thus be adjusted by means of the controllable clean gas raw gas heat exchanger 134 depending on the desired at the downstream heat exchangers clean gas temperature.
  • a further increase in the outlet temperature of the clean gas can be achieved if the bypass flap 172 in the hot-side bypass line 170 is opened, so that clean gas can pass from the combustion chamber 102 directly into the clean gas line 164.
  • the reaction time available for the oxidation of the combustible constituents of the raw gas is shortened because the clean gas entering the bypass line 170 does not pass through the clean gas duct 168.
  • bypass fluid flow is very uniformly returned to the residual fluid flow by the admixing device 148, because the bypass channel 130 is designed as a hollow cylinder, which is arranged concentrically around the clean gas raw gas heat exchanger 134, and because the admixing point 220 extends over the entire circumference of the outer heat exchanger chamber 144 at the admixing point 201.
  • throttle elements 222 arranged in the bypass channel 130 act as damper stages, which uniform the distribution of the bypass fluid flow over the circumference of the bypass channel 130.
  • the raw gas which has been heated in the clean gas raw gas heat exchanger 134 from its initial temperature to a preheating temperature of, for example, about 620 ° C, optionally mixed with fuel from the fuel line 106, passes through the raw gas inlet 154 in the Burner 104 and from there into the combustion chamber 102.
  • the oxidizable constituents of the raw gas and the fuel are oxidized in an exothermic reaction, whereby a clean gas having a temperature of, for example, about 750 ° C is generated, which faces away from the burner end face 178 of the combustion chamber 102 flows through the clean gas duct 168 against the flow direction 204 back to the burner end of the clean gas raw gas heat exchanger 134 where the clean gas enters the burner side ends of the heat exchanger tubes 138 of the clean gas raw gas heat exchanger 134 and in which through the interiors the heat exchanger tubes 138 formed inner heat exchanger chamber 140 along the flow direction 204 to the burner 104 remote from the end of the clean gas raw gas heat exchanger 134 flows.
  • the thermal exhaust air purification system 100 is structurally designed for a specific operating point with a certain clean gas outlet temperature T A.
  • this predetermination (at an input temperature of the raw gas specified by the raw gas source 114) essentially determines the height of the outlet temperature.
  • the outlet temperature of the clean gas can be increased as required by the bypass device 126 which is controllable in the manner described above, but can not be lowered, it makes sense to use the bypass device 126, the operating point of the thermal exhaust air purification system 100 not to the target outlet temperature of the clean gas, but to a slightly lower temperature, preferably to a lower by at least 10 ° C temperature, in particular to a lower by about 20 ° C temperature interpreted.
  • the actually required clean gas outlet temperature T A can then be adjusted by regulating the clean gas raw gas heat exchanger 134 by means of the bypass flap 212 and the heat exchanger flap 208.
  • FIGS. 3 to 14 illustrated second embodiment of a thermal exhaust air purification system 100 agrees with respect to their basic structure and its operation with the first embodiment shown in FIGS. 1 and 2.
  • the principal block diagram of FIG. 1 to the second embodiment of a thermal exhaust air purification system 100 too.
  • a difference of the second embodiment from the first embodiment is that in the second embodiment, the portion 150 between the raw gas inlet 132 at which the residual fluid flow enters the outer heat exchanger space 144 of the clean gas raw gas heat exchanger 134 and the admixing device 148 of the outer heat exchanger space 144 is longer than that between the admixing device 148 and the Rohgasaustritt 146, where the reunited total fluid flow of the raw gas exiting the outer heat exchanger chamber 144, lying end portion 152 of the outer heat exchanger chamber 144th
  • the bypass fluid flow is admixed only when the residual fluid flow already has a higher temperature than in the first embodiment.
  • the extension of the admixing point 220 of the admixing device 148 in the direction of the longitudinal axis 174 in the second embodiment is greater than in the first embodiment.
  • the extent of the passage gap 218 forming the admixing point 220 in the direction of the longitudinal axis 174 is greater than the average distance between two holding elements 190 of the clean gas-raw gas heat exchanger 134 which succeed one another in the direction of the longitudinal axis 174.
  • the bypass passage end wall 216 in the second embodiment is not substantially circular-cone-shaped, as in the first embodiment, but is substantially annular.
  • reinforcing elements 232 are provided in the second embodiment, for example in the form of approximately triangular gussets which extend along the circumference of the bypass passage end wall 216, preferably substantially equidistant. are distributed and cohesively connected to both the bypass channel end wall 216 and the bypass outer housing 214.
  • the edge 234 of the heat exchanger outer housing 182 facing the bypass duct end wall 216, which delimits the admixing point 220 on the upstream side, is provided with an annular fold 236 in order to stiffen the edge 234.
  • an inner holding element 190a of the clean gas raw gas heat exchanger 134 and no outer holding element 190b is arranged, so that the Residual fluid flow is forced to pass on the radially outer side of the holding member 190 a.
  • FIGS. 4 to 14 show details of the second embodiment of a thermal exhaust air purification apparatus 100 which are the same in the first embodiment or may be the same, but are not so clear from the single sectional view (FIG. 2) of the first embodiment.
  • FIG. 4 shows a vertical section through the radially inner region of an inner retaining element 190a with a sliding shoe 196 fastened thereto, which can slide on an outer side of the heat exchanger inner housing 184 in the direction of the longitudinal axis 174.
  • FIG. 5 shows a vertical section through the burner-side ends of two heat exchanger tubes 138, which are materially connected, in particular welded, to a holding element 190 of the clean gas raw gas heat exchanger 134.
  • FIG. 6 shows a top view from above of the end region of the thermal exhaust air purification system 100 facing away from the burner 104, from which in particular the separating device 124 with the bypass shaft 210 and the adjacent inlet shaft 206 can be clearly seen.
  • the cross section of the inlet shaft 206 through which the raw gas can flow is preferably larger than the cross section of the bypass shaft 210 through which the raw gas can flow.
  • FIG. 7 shows a vertical cross section through the thermal exhaust air cleaning system 100 in the region of the admixing point 220 of the admixing device 148.
  • the heat exchanger tube bundle 136 includes three heat exchanger tube layers 188, wherein the heat exchanger tubes 138 of different heat exchanger tube layers 188 have different radial distances from the longitudinal axis 174 ,
  • FIG. 9 shows a vertical cross section through the thermal exhaust air purification system 100 in a region in which the bypass channel 130 of the bypass device 126 concentrically surrounds the section 150 of the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134.
  • Fig. 9 and 10 which shows an annular throttle element 222 arranged in the bypass passage 130 alone, it can be seen that the throttle element 222 is provided with a plurality of circular passage openings 224, which follow each other along the circumference of the throttle element 222, preferably equidistantly.
  • the ratio of the total area of the passage openings 224 in the throttle element 222 to the maximum throughflow cross-sectional area of the bypass device 126 can be selected in the same way as in the first embodiment.
  • FIGS. 11 to 14 show details of an embodiment for a separation device 124 of the bypass device 126, with a drive device 240 for driving a coupled adjustment movement of the bypass flap 212 and the heat exchanger flap 208.
  • bypass flap 212 and the heat exchanger flap 208 are pivotably mounted on the bypass shaft 210 and on the inlet shaft 206 respectively about a rotational shaft 242 and 244 between an open position and a closed position.
  • bypass flap 212 is currently in its open position, in which it releases the maximum inlet cross section for the inflow of the bypass fluid flow into the bypass device 126, while at the same time the heat exchanger flap 208 is in its closed position, in which the heat exchanger flap 208 prevents the entry of raw gas into the section 150 of the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134.
  • bypass flap 212 and the heat exchanger flap 208 In this position, the bypass flap 212 and the heat exchanger flap 208 so that the volume fraction of the bypass fluid flow in the entire raw gas stream, which enters the thermal exhaust air purification system 100, 100%.
  • the rotary shafts 242 and 244 are coupled to each other via a parallelogram linkage 246 shown in FIG. 14 so that the bypass damper 212 and the heat exchanger damper 208 perform opposite equal pivotal movements when the rotary shaft of the bypass damper 242 is driven to pivot.
  • Such a pivoting movement is triggered by means of an electric drive motor 248, which generates a displacement of a rectilinear guided free end of a lever 249 via a rotary spindle assembly 250, which is articulated via a hinge 251 to a further lever 252, which in turn is non-rotatably connected to the rotary shaft 242 ,
  • the heat exchanger flap 208 is simultaneously moved by the coupling of the two flaps 212 and 208 via the parallelogram linkage 246 from its closed position to the open position.
  • FIG. 15 shows a schematic block diagram of a third embodiment of a thermal exhaust air purification system 100 differs from that shown in FIGS. 1 and 2 illustrated in that the inner heat exchanger chamber 140 of the clean gas Rohgas-Wärmetau- shear 134 is traversed in the third embodiment not by the clean gas, but by the raw gas, while the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134th in this embodiment, the clean gas flows through it.
  • the clean gas serves as the outer fluid medium and the raw gas as the inner fluid medium. Therefore, in this embodiment, the bypass means 126, by means of which a portion of the outer fluid flow past a portion 150 of the outer heat exchange space 144 of the clean gas raw gas heat exchanger 134 to reduce the efficiency of the clean gas raw gas heat exchanger 134, if necessary, not raw gas side, but arranged on the clean gas side.
  • the bypass device 126 comprises a separating device 124 arranged at the clean gas inlet into the clean gas raw gas heat exchanger 134, by means of which part of the clean gas flow from the combustion chamber 102 can be separated as a bypass fluid flow from a residual fluid flow of the clean gas and via a bypass channel 130 a Zumischvorrich- device 148 can be fed, by means of which the bypass fluid flow is again mixed into the residual fluid stream of the clean gas, after this residual fluid flow has passed the portion 150 of the outer heat exchanger chamber 144 of the clean gas Rohgas heat exchanger 134.
  • FIG. 15 the third embodiment of a thermal exhaust air purification system 100 illustrated in FIG. 15 is identical in construction and function to the embodiment shown in FIGS. 1 and 2 illustrated first embodiment and also with the second embodiment shown in FIGS. 3 to 14, to the above description in this respect reference is made.

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  • Engineering & Computer Science (AREA)
  • Environmental & Geological Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Incineration Of Waste (AREA)

Abstract

L'invention concerne une installation d'épuration thermique de gaz d'évacuation, comprenant une chambre de combustion et un échangeur de chaleur pour la transmission de chaleur d'un gaz purifié produit dans la chambre de combustion à un gaz brut à amener dans la chambre de combustion, l'échangeur de chaleur comportant une chambre d'échange de chaleur intérieure pouvant être parcourue par un milieu fluide intérieur et une chambre d'échange de chaleur extérieure pouvant être parcourue par un milieu fluide extérieur, laquelle installation permet une régulation de la température de sortie du gaz purifié, sans diminuer la qualité du gaz purifié. Selon l'invention, il est proposé que l'installation d'épuration thermique de gaz d'évacuation comporte un dispositif de dérivation comprenant un dispositif de séparation au moyen duquel une partie du flux de fluide extérieur peut être séparé en tant que flux de fluide de dérivation d'un flux de fluide résiduel extérieur et un dispositif de mélange au moyen duquel le flux de fluide de dérivation peut être de nouveau mélangé au flux de fluide résiduel après que le flux de fluide résiduel a passé une section de la chambre d'échange de chaleur extérieure.
PCT/EP2011/053551 2010-03-15 2011-03-09 Installation d'épuration thermique de gaz d'évacuation WO2011113732A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP11708792.4A EP2547960B1 (fr) 2010-03-15 2011-03-09 Installation d'épuration thermique de gaz d'évacuation
DK11708792.4T DK2547960T3 (da) 2010-03-15 2011-03-09 Termisk afgangsluftrenseanlæg
CN201180014368.8A CN102803853B (zh) 2010-03-15 2011-03-09 热力的废气净化设施
RU2012143690/03A RU2554965C2 (ru) 2010-03-15 2011-03-09 Установка термической очистки отходящего воздуха
PL11708792T PL2547960T3 (pl) 2010-03-15 2011-03-09 Instalacja termiczna do oczyszczania powietrza odlotowego
HK13100505.3A HK1173206A1 (zh) 2010-03-15 2013-01-11 熱力的廢氣淨化設施

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010012005A DE102010012005A1 (de) 2010-03-15 2010-03-15 Thermische Abluftreinigungsanlage
DE102010012005.7 2010-03-15

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WO2011113732A1 true WO2011113732A1 (fr) 2011-09-22

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CN (1) CN102803853B (fr)
DE (1) DE102010012005A1 (fr)
DK (1) DK2547960T3 (fr)
HK (1) HK1173206A1 (fr)
PL (1) PL2547960T3 (fr)
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JP5370457B2 (ja) * 2011-10-13 2013-12-18 三浦工業株式会社 熱媒ボイラ
ITGO20120001A1 (it) * 2012-03-14 2013-09-15 Eligio Zupin Dispositivo di combustione del combustibile gassificato da combustibili solidi
DE102013203448A1 (de) 2013-02-28 2014-08-28 Dürr Systems GmbH Anlage und Verfahren zum Behandeln und/oder Verwerten von gasförmigemMedium
DE102013224297A1 (de) 2013-11-27 2015-05-28 Caverion Deutschland GmbH Gasoxidationsanlage sowie Verfahren zu deren Betrieb
DE102013224212A1 (de) 2013-11-27 2015-05-28 Caverion Deutschland GmbH Verfahren zum Betrieb einer Gasoxidationsanlage
GB2544520A (en) * 2015-11-19 2017-05-24 Edwards Ltd Effluent gas treatment apparatus and method
DE102016201974A1 (de) * 2016-02-10 2017-08-10 Dürr Systems Ag Verfahren zum Betreiben einer Wärmekraftmaschine und Wärmekraftmaschine
CN107305013A (zh) * 2016-04-21 2017-10-31 沈阳铝镁科技有限公司 一种沥青烟气净化焚烧装置
RU183318U1 (ru) * 2018-07-24 2018-09-18 Константин Владимирович Крайзеров Устройство термической очистки газов

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US4255132A (en) 1979-09-12 1981-03-10 Schweitzer Industrial Corp. Incinerator-heater system
US4460331A (en) 1983-05-12 1984-07-17 Haden Schweitzer Corporation Fume incineration for paint drying oven
US4650414A (en) 1985-11-08 1987-03-17 Somerset Technologies, Inc. Regenerative heat exchanger apparatus and method of operating the same
DE3605415A1 (de) 1986-02-20 1987-08-27 Katec Betz Gmbh & Co Verfahren und vorrichtung zum verbrennen oxidierbarer bestandteile in einem traegergas
US5643544A (en) 1995-04-28 1997-07-01 Applied Web Systems, Inc. Apparatus and method for rendering volatile organic compounds harmless

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EP2547960A1 (fr) 2013-01-23
PL2547960T3 (pl) 2014-11-28
RU2554965C2 (ru) 2015-07-10
DE102010012005A1 (de) 2011-09-15
EP2547960B1 (fr) 2014-06-11
HK1173206A1 (zh) 2013-05-10
CN102803853A (zh) 2012-11-28
RU2012143690A (ru) 2014-04-20
CN102803853B (zh) 2016-04-13
DK2547960T3 (da) 2014-09-01

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