EP2547960B1 - Installation d'épuration thermique de gaz d'évacuation - Google Patents

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

Info

Publication number
EP2547960B1
EP2547960B1 EP11708792.4A EP11708792A EP2547960B1 EP 2547960 B1 EP2547960 B1 EP 2547960B1 EP 11708792 A EP11708792 A EP 11708792A EP 2547960 B1 EP2547960 B1 EP 2547960B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
bypass
fluid flow
exhaust air
air purification
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.)
Not-in-force
Application number
EP11708792.4A
Other languages
German (de)
English (en)
Other versions
EP2547960A1 (fr
Inventor
Thorsten Gysin
Erhard Rieder
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.)
Duerr Systems AG
Original Assignee
Duerr Systems 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 Duerr Systems AG filed Critical Duerr Systems AG
Priority to PL11708792T priority Critical patent/PL2547960T3/pl
Publication of EP2547960A1 publication Critical patent/EP2547960A1/fr
Application granted granted Critical
Publication of EP2547960B1 publication Critical patent/EP2547960B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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.
  • Such a hot gas bypass damper is arranged in thermal exhaust air purification systems in compact design due to the design of the combustion chamber and at the beginning of a reaction chamber, which is flowed through with closed bypass valve from the exhaust air from the combustion chamber.
  • the residence time of the exhaust air to be cleaned is extended to the reaction temperature required for a complete conversion of the pollutants contained therein.
  • 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 US 5 643 544 A discloses 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, wherein the heat exchanger can flow through an inner heat exchange space through which an inner fluid medium and through an outer fluid medium outer heat exchanger space, and wherein the thermal exhaust air purification system comprises 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 from an outer residual fluid flow, and with an admixing device, by means of which the bypass fluid flow back into the rest Fluid flow is admixed after the residual fluid flow has passed through a portion of the outer heat exchanger space comprises.
  • the US 4 255 132 A discloses a thermal exhaust air purification system comprising a combustion chamber and a heat exchanger for transferring heat from a clean gas generated in the combustion chamber to a raw gas to be supplied to the combustion chamber, wherein the thermal exhaust air purification system comprises a bypass device with a separation device, by means of which a part of the raw gas stream as a bypass raw gas stream from a residual crude gas stream is separable comprises.
  • the bypass raw gas stream is only combined in the combustion chamber with the rest of the crude gas stream.
  • the US 4,650,414 A discloses a regenerative thermal exhaust air purification system having a combustion chamber and a plurality of regenerative heat exchangers, which are successively flowed through by clean gas generated in the combustion chamber and by the raw gas to be supplied to the combustion chamber.
  • the transfer of heat from the clean gas to the raw gas takes place indirectly via the Heat storage in a heat storage mass of the respective regenerative heat exchanger.
  • the DE 36 05 415 A1 discloses 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 thermal exhaust air purification system comprising a bypass device having a separator by means of which a portion of the raw gas fluid flow bypasses -Rohgasstrom can be separated from a residual crude gas stream, and with a mixing device, by means of which the bypass crude gas stream is again mixed into the residual crude gas stream after the residual raw gas stream has passed through the heat exchanger comprises.
  • the US 4,460,331 A discloses 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, wherein the heat exchanger can flow through an inner heat exchange space through which an inner fluid medium and through an outer fluid medium outer heat exchanger space, and wherein the thermal exhaust air purification system comprises a bypass device with a separation device, by means of which a part of the inner fluid flow is separable as a bypass fluid flow from an inner residual fluid flow, and with an admixing device, by means of which the bypass fluid flow back into the rest Fluid flow is immiscible after the residual fluid flow has passed through the inner heat exchanger space includes.
  • 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.
  • the present invention has the further object to provide a method of the aforementioned type, which allows a regulation of the clean gas outlet temperature, without affecting the quality of the clean gas.
  • the present invention is based on the concept to regulate the clean gas outlet temperature of the thermal exhaust air purification system in that a portion of the outer fluid flow bypasses 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, these admixing points being distributed over an admixing area extending over at least half of the circumference of the residual fluid flow 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 area 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 of a heat exchanger tube bundle of the heat exchanger.
  • 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 throttle 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 mechanically and / or control technology (ie, by coordinated control by means of a control device of the thermal exhaust air purification system) coupled together.
  • 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 coupling of the bypass flap and the heat exchanger flap By the coupling of the bypass flap and the heat exchanger flap, the division of the entire outer fluid flow to the bypass fluid flow and the residual fluid flow can be carried out preferably substantially continuously, whereby the efficiency of the heat exchanger and thus the clean gas outlet 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 thermal exhaust air purification system according to the invention is preferably designed as a recuperative exhaust air purification system with a recuperative clean gas raw gas heat exchanger.
  • 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.
  • thermal exhaust air purification system can then be regulated by regulating the heat exchanger by means of the bypass flap and the heat exchanger flap 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.
  • thermal 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.
  • the uniform admixture of the bypass fluid flow over a substantial 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.
  • thermal exhaust air purification system comprises, as shown in the schematic diagram of Fig. 1 can be seen, a combustion chamber 102, at the combustion chamber inlet a burner 104 is arranged, via a fuel line 106 with a fuel valve 108, a suitable fuel, such as natural gas, and a cooling air line 110 with a cooling air valve 112 cooling air for an ignition electrode, a sight glass and a 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 designated 114 raw gas source.
  • 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 Ap 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 is arranged at a location between the raw gas inlet 132 and a raw gas outlet 146 of the clean gas raw gas heat exchanger 134, 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 after the remainder -Fluidstrom of the raw gas one 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.
  • Fig. 1 the clean gas raw gas heat exchanger 134 is shown purely schematically as if the outer heat exchanger chamber 144 is embedded in the inner heat exchanger chamber 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 Ap between the combustion chamber 102 on the one hand and the Rohgasaustritt 146 from the clean 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.
  • 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 .DELTA.p between the clean gas line 164 and the Rohgaseintritt 116 can be determined in the thermal exhaust air purification system 100.
  • a bypass line 170 can branch off downstream of the clean gas outlet 162 of the clean gas raw gas heat exchanger 134 into the clean gas line 164 opens.
  • 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 current 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 associated clean gas raw gas heat exchanger 134 of the thermal exhaust air purification system 100 with the bypass device 126 from Fig. 1 are in Fig. 2 shown in detail.
  • 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 190a are supported by sliding shoes 196 on the heat exchanger inner housing 183, but are not firmly connected to the heat exchanger inner housing 184, 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 holding members 190 a and the outer holding members 190 b 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 raw gas heat exchanger 134, so that in the outer heat exchanger chamber 144 a convoluted flow path is formed for a fluid medium.
  • 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 coordinated control of the flaps by a control device of the thermal exhaust air cleaning system 100) coupled together such that they always open in opposite directions or closed.
  • 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% controllable 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, up 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.
  • the throttle elements 222 are provided, which in each case 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 is formed are.
  • 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 releases in the bypass shaft 210.
  • 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, faces away from the burner 104 End of the combustion chamber 102 and on the other hand in fluid communication with the clean gas collecting chamber 228.
  • compensator 230 which, for example, has the shape of a hollow cylinder and, on the one hand, faces away from the burner 104 End of the combustion chamber 102 and on the other hand in fluid communication with the clean gas collecting chamber 228.
  • the compensator 230 for example, at its collecting chamber 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 the clean gas Crude gas heat exchanger 134 to pass.
  • the heat exchanger tubes 138 may be provided on the inside and on the outside of its wall with a turbulence generating surface structure.
  • the heat exchanger tubes 138 are formed as swirl tubes.
  • the heat exchanger tubes 138 may also be designed as smooth tubes.
  • 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 supplied from the admixing device 148 very evenly to the residual fluid flow 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 mixing point 220 over the entire Extending the circumference of the outer heat exchanger chamber 144 at the mixing 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 with a temperature of for example about 750 ° C is generated, which faces away from the burner end face 178 of 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 the through the interiors of 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 clean gas is discharged through the exhaust chimney to the environment.
  • 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 operating point of the thermal exhaust air purification system 100 is not useful when using the bypass device 126 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 interpreted.
  • thermal exhaust air cleaning system 100 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, the actual clean gas outlet temperature T A required.
  • FIG. 3 to 14 illustrated second embodiment of a thermal exhaust air purification system 100 agrees with respect to their basic structure and operation with the in the Fig. 1 and 2 illustrated first embodiment.
  • the basic block diagram is correct Fig. 1 Also to the second embodiment of a thermal exhaust air purification system 100 to.
  • 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 are arranged in the region of the mixing point 220 of the mixing device 148, so that the remaining Fluid flow is forced to pass by the radially outer side of the holding member 190 a.
  • the 4 to 14 show details of the second embodiment of a thermal exhaust air purification system 100, which are the same in the first embodiment or may be the same, but from the single sectional view ( Fig. 2 ) of the first embodiment are not so clearly visible.
  • FIG. 4 a vertical section through the radially inner region of an inner support member 190 a with a shoe 196 attached 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 to a holding element 190 of the clean gas raw gas heat exchanger 134, in particular welded, are.
  • Fig. 6 shows a top view from the top of the burner 104 remote from the end portion of the thermal exhaust air purification system 100, from which in particular the separation device 124 with the bypass shaft 210 and the adjacent entrance 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 148th
  • 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 portion 150 of the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134.
  • Fig. 9 and Fig. 10 showing 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.
  • FIG. 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 208th
  • bypass flap 212 and the heat exchanger flap 208 are pivotally mounted on the bypass shaft 210 and the inlet shaft 206 respectively about a rotary 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 208th 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 over a in Fig. 14 illustrated parallelogram linkage 246 coupled together so that the bypass flap 212 and the heat exchanger flap 208 perform opposite equal pivotal movements when the rotary shaft of the bypass valve 242 is driven to pivotal movement.
  • 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 another 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 illustrated in a schematic block diagram third embodiment of a thermal exhaust air purification system 100 differs from that in the Fig. 1 and 2 illustrated first embodiment in that the inner heat exchanger chamber 140 of the clean gas raw gas heat exchanger 134 in the third embodiment is not flowed through by the clean gas, but by the raw gas, while the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134 in this embodiment of the Clean gas is flowed through.
  • the clean gas serves as the outer fluid medium and the raw gas as the inner fluid medium.
  • 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 separation 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 an admixing 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 section 150 of the outer heat exchanger chamber 144 of the clean gas raw gas heat exchanger 134.
  • the efficiency of the clean gas raw gas heat exchanger 134 can be reduced by passing an adjustable proportion of the total clean gas flow at the portion 150 of the outer heat exchanger space 144 of the clean gas raw gas heat exchanger 134 in a controlled manner, in this embodiment as well Control of the clean gas raw gas heat exchanger 134, a regulation of the clean gas outlet temperature T A possible.
  • Fig. 15 illustrated third embodiment of a thermal exhaust air purification system 100 in terms of structure and function with in the Fig. 1 and 2 shown first embodiment and also with in the Fig. 3 to 14 illustrated second embodiment, to the above description in this respect reference is made.

Landscapes

  • 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)

Claims (14)

  1. Installation d'épuration thermique d'air d'évacuation, comprenant une chambre de combustion (102) et un échangeur de chaleur (134) pour le transfert de chaleur d'un gaz purifié généré dans la chambre de combustion (102) à un gaz brut à transmettre à la chambre de combustion (102),
    l'échangeur de chaleur (134) comportant un espace d'échangeur de chaleur (140) intérieur pouvant être traversé par un agent fluide intérieur et un espace d'échangeur de chaleur (144) extérieur pouvant être traversé par un agent fluide extérieur,
    l'installation d'épuration thermique d'air d'évacuation (100) comportant un dispositif de dérivation (126)
    avec un dispositif de séparation (124), à l'aide duquel une partie du courant fluidique extérieur peut être séparée, comme courant fluidique de dérivation, d'un courant fluidique restant extérieur, et
    avec un dispositif de mélange (148), à l'aide duquel le courant fluidique de dérivation peut être mélangé de nouveau dans le courant fluidique restant, après que le courant fluidique restant a passé une section (150) de l'espace d'échangeur de chaleur (144) extérieur, caractérisée en ce que le dispositif de dérivation (126) comporte un canal de dérivation (130) qui entoure de manière annulaire la voie d'écoulement du courant fluidique restant.
  2. Installation d'épuration thermique d'air d'évacuation selon la revendication 1, caractérisée en ce que le dispositif de mélange (148) comporte au moins un point de mélange (220) qui s'étend sur au moins la moitié de la périphérie du courant fluidique restant.
  3. Installation d'épuration thermique d'air d'évacuation selon la revendication 2, caractérisée en ce que le point de mélange (220) s'étend en forme d'anneau autour de la voie d'écoulement du courant fluidique restant.
  4. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le dispositif de mélange (148) comporte plusieurs points de mélange (220), les points de mélange (220) étant répartis sur une zone de mélange qui s'étend sur au moins la moitié de la périphérie du courant fluidique restant.
  5. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le dispositif de dérivation (126) comporte au moins un élément d'étranglement (222) dans la voie d'écoulement du courant fluidique de dérivation.
  6. Installation d'épuration thermique d'air d'évacuation selon la revendication 5, caractérisée en ce qu'au moins un élément d'étranglement (222) est réalisé comme une barrière d'écoulement avec des ouvertures de passage (224).
  7. Installation d'épuration thermique d'air d'évacuation selon la revendication 6, caractérisée en ce que la surface de passage entière des ouvertures de passage (224) dans la barrière d'écoulement s'élève à 150 % ou moins d'une aire de section d'entrée du dispositif de dérivation (126).
  8. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 7, caractérisée en ce que le dispositif de mélange (148) est disposé en amont d'une sortie (146 ; 162) de l'agent fluide extérieur hors de l'espace d'échangeur de chaleur extérieur (144).
  9. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 8, caractérisée en ce que le dispositif de séparation (124) comporte un clapet de dérivation (212) pour la commande de l'entrée du courant fluidique de dérivation dans le dispositif de dérivation (126) et un clapet d'échangeur de chaleur (208) pour la commande de l'entrée du courant fluidique restant dans l'échangeur de chaleur (134).
  10. Installation d'épuration thermique d'air d'évacuation selon la revendication 9, caractérisée en ce que le clapet de dérivation (212) et le clapet d'échangeur de chaleur (208) sont couplés par voie mécanique et/ou technique de commande.
  11. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 10, caractérisée en ce que le dispositif de séparation (124) est disposé en amont d'une entrée (132 ; 160) du courant fluidique restant dans l'espace d'échangeur de chaleur extérieur (144).
  12. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 11, caractérisée en ce que l'espace d'échangeur de chaleur extérieur (144) peut être traversé par le gaz brut à transmettre de la chambre de combustion (102).
  13. Installation d'épuration thermique d'air d'évacuation selon l'une quelconque des revendications 1 à 11, caractérisée en ce que l'espace d'échangeur de chaleur (14) extérieur peut être traversé par du gaz purifié généré dans la chambre de combustion (102).
  14. Procédé d'épuration d'un courant de gaz brut contenant des éléments oxydables à l'aide d'une installation d'épuration thermique d'air d'évacuation, comportant les étapes de procédé suivantes :
    - amenée du courant de gaz brut à une chambre de combustion (102) ;
    - génération d'un courant de gaz purifié par l'oxydation au moins partielle des éléments oxydables du courant de gaz brut dans la chambre de combustion ;
    - transfert de la chaleur du courant de gaz purifié au courant de gaz brut à l'aide d'un échangeur de chaleur (134), l'échangeur de chaleur (134) comportant un espace d'échangeur de chaleur (140) intérieur traversé par un agent fluide intérieur et un espace d'échangeur de chaleur (144) extérieur traversé par un agent fluide extérieur ;
    - séparation d'une partie du courant fluidique extérieur, comme courant fluidique de dérivation, d'un courant fluidique restant extérieur à l'aide d'un dispositif de séparation (124) d'un dispositif de dérivation (126) ;
    - mélange du courant fluidique de dérivation dans le courant fluidique restant à l'aide d'un dispositif de mélange (148) du dispositif de dérivation (126) après que le courant fluidique restant a passé une section (150) de l'espace d'échangeur de chaleur extérieur (144) ;
    le dispositif de dérivation (126) comportant un canal de dérivation (130) qui entoure de manière annulaire la voie d'écoulement du courant fluidique restant.
EP11708792.4A 2010-03-15 2011-03-09 Installation d'épuration thermique de gaz d'évacuation Not-in-force EP2547960B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11708792T PL2547960T3 (pl) 2010-03-15 2011-03-09 Instalacja termiczna do oczyszczania powietrza odlotowego

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010012005A DE102010012005A1 (de) 2010-03-15 2010-03-15 Thermische Abluftreinigungsanlage
PCT/EP2011/053551 WO2011113732A1 (fr) 2010-03-15 2011-03-09 Installation d'épuration thermique de gaz d'évacuation

Publications (2)

Publication Number Publication Date
EP2547960A1 EP2547960A1 (fr) 2013-01-23
EP2547960B1 true EP2547960B1 (fr) 2014-06-11

Family

ID=44063755

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11708792.4A Not-in-force EP2547960B1 (fr) 2010-03-15 2011-03-09 Installation d'épuration thermique de gaz d'évacuation

Country Status (8)

Country Link
EP (1) EP2547960B1 (fr)
CN (1) CN102803853B (fr)
DE (1) DE102010012005A1 (fr)
DK (1) DK2547960T3 (fr)
HK (1) HK1173206A1 (fr)
PL (1) PL2547960T3 (fr)
RU (1) RU2554965C2 (fr)
WO (1) WO2011113732A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102013224212A1 (de) 2013-11-27 2015-05-28 Caverion Deutschland GmbH Verfahren zum Betrieb einer Gasoxidationsanlage
DE102013224297A1 (de) 2013-11-27 2015-05-28 Caverion Deutschland GmbH Gasoxidationsanlage sowie Verfahren zu deren Betrieb
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
CN113007729A (zh) * 2021-04-14 2021-06-22 苏州克兰茨环境科技有限公司 适用于高、低浓度VOCs气体的集成化处理系统

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2254848B2 (de) * 1972-11-09 1976-08-05 Böhler-Zenkner GmbH & Co KG Strömungstechnik, 4005 Meerbusch Anordnung zur thermischen nachverbrennung
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
NL8902479A (nl) * 1989-10-05 1991-05-01 Rolfes Operational B V Werkwijze en inrichting voor het beperken van de emissie van milieu belastende, in de druktechniek e.d. vrijkomende organische oplosmiddelen.
ATE161622T1 (de) * 1994-11-24 1998-01-15 Kunz Drytec Ag W Verfahren zum trocknen einer substanz, insbesondere von holzspänen
US5643544A (en) 1995-04-28 1997-07-01 Applied Web Systems, Inc. Apparatus and method for rendering volatile organic compounds harmless

Also Published As

Publication number Publication date
CN102803853B (zh) 2016-04-13
DK2547960T3 (da) 2014-09-01
CN102803853A (zh) 2012-11-28
EP2547960A1 (fr) 2013-01-23
HK1173206A1 (zh) 2013-05-10
RU2012143690A (ru) 2014-04-20
PL2547960T3 (pl) 2014-11-28
RU2554965C2 (ru) 2015-07-10
DE102010012005A1 (de) 2011-09-15
WO2011113732A1 (fr) 2011-09-22

Similar Documents

Publication Publication Date Title
EP2547960B1 (fr) Installation d'épuration thermique de gaz d'évacuation
DE102012107908B4 (de) Abgaswärmetauscher
DE102006055973A1 (de) Wärmetauscher zur Kühlung von Spaltgas
DE3808075A1 (de) Mechanische russfiltervorrichtung
EP2986911A1 (fr) Brûleur central pour système de brûleur multi-lances multi-combustibles
DE102011118164B4 (de) Wärmeübertrager und Verfahren zum Betreiben eines Wärmeübertragers
DE3208467A1 (de) Konvektionserhitzer zum erhitzen von fluida, wie z.b. eine aufschlaemmung oder dergleichen
EP1984673B1 (fr) Dispositif pour la combustion de matières organiques
DD291803A5 (de) Anlage und verfahren zur regelung der temperatur von zwischenueberhitzungsdampf bei dampfkesseln mit zirkulierender wirbelschicht
WO2011045152A2 (fr) Échangeur thermique à plaques
DE102010042674A1 (de) Wärmeübertragungsvorrichtung, thermoelektrische Generatorvorrichtung und Verfahren zur Steuerung und/oder Regelung einer Wärmeübertragungsvorrichtung
WO2013156139A1 (fr) Refroidisseur de gaz de processus comportant des clapets de refroidisseur de gaz de processus commandés par leviers
DE10019414C2 (de) Vorrichtung zum Einleiten von Gas in einen Rohrabschnitt
DE102004018037A1 (de) Verfahren zum Kühlen von Abgas eines Verbrennungsmotors eines Fahrzeugs sowie Wärmeübertrager
EP1771683B1 (fr) Dispositif de postcombustion thermique et procede d'exploitation correspondant
EP2622276B1 (fr) Brûleur à mazout à prémélange
DE102010012006A1 (de) Wärmetauscher für eine thermische Abluftreinigungsanlage und Verfahren zum Reinigen eines Abluftstroms
DE102015203001B3 (de) Wärmetauscheranordnung sowie Abgassystem für eine Brennkraftmaschine eines Kraftfahrzeugs
DE3117596A1 (de) "verfahren zum ofenbetrieb mittels gasverschluss und vorrichtung zur durchfuehrung des verfahrens"
EP1221571B1 (fr) Appareil de combustion avec refroidissement
EP3931491B1 (fr) Dispositif de postcombustion régénératrice, système de revêtement et procédé de revêtement d'objets
DE102013206014A1 (de) Energiewandler-System und Baugruppen hierfür
WO2018002309A1 (fr) Four à haute température à récupération de chaleur
WO2020025163A1 (fr) Système de récupération de chaleur pour un four pourvu d'un ou de plusieurs brûleurs
DE102011012493A1 (de) Ölvormischbrenner

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20120816

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140108

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: CH

Ref legal event code: NV

Representative=s name: ISLER AND PEDRAZZINI AG, CH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: T3

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 672453

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140715

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011003364

Country of ref document: DE

Effective date: 20140724

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20140825

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140912

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140911

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

REG Reference to a national code

Ref country code: PL

Ref legal event code: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141013

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141011

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011003364

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20150312

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011003364

Country of ref document: DE

Effective date: 20150312

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011003364

Country of ref document: DE

Representative=s name: HOEGER, STELLRECHT & PARTNER PATENTANWAELTE MB, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150309

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502011003364

Country of ref document: DE

Owner name: DUERR SYSTEMS AG, DE

Free format text: FORMER OWNER: DUERR SYSTEMS GMBH, 74321 BIETIGHEIM-BISSINGEN, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011003364

Country of ref document: DE

Representative=s name: HOEGER, STELLRECHT & PARTNER PATENTANWAELTE MB, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140611

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502011003364

Country of ref document: DE

Representative=s name: HOEGER, STELLRECHT & PARTNER PATENTANWAELTE MB, DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IE

Payment date: 20220322

Year of fee payment: 12

Ref country code: GB

Payment date: 20220321

Year of fee payment: 12

Ref country code: DK

Payment date: 20220323

Year of fee payment: 12

Ref country code: DE

Payment date: 20220322

Year of fee payment: 12

Ref country code: CH

Payment date: 20220321

Year of fee payment: 12

Ref country code: AT

Payment date: 20220322

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20220321

Year of fee payment: 12

Ref country code: PL

Payment date: 20220228

Year of fee payment: 12

Ref country code: NL

Payment date: 20220321

Year of fee payment: 12

Ref country code: IT

Payment date: 20220323

Year of fee payment: 12

Ref country code: FR

Payment date: 20220322

Year of fee payment: 12

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230628

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011003364

Country of ref document: DE

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20230331

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20230401

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 672453

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230309

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20230309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230401

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230310

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230331

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230331

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20231003

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230331

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230309