CA2037864A1 - Apparatus for the combustion of pollutants carried in a waste gas flow - Google Patents
Apparatus for the combustion of pollutants carried in a waste gas flowInfo
- Publication number
- CA2037864A1 CA2037864A1 CA002037864A CA2037864A CA2037864A1 CA 2037864 A1 CA2037864 A1 CA 2037864A1 CA 002037864 A CA002037864 A CA 002037864A CA 2037864 A CA2037864 A CA 2037864A CA 2037864 A1 CA2037864 A1 CA 2037864A1
- Authority
- CA
- Canada
- Prior art keywords
- heat exchanger
- chamber
- gas flow
- exchanger pipes
- gas
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
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
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)
- Fluidized-Bed Combustion And Resonant Combustion (AREA)
- Gasification And Melting Of Waste (AREA)
- Regulation And Control Of Combustion (AREA)
Abstract
TITLE OF THE INVENTION
APPARATUS FOR THE COMBUSTION OF POLLUTANTS CARRIED IN A
WASTE GAS FLOW
ABSTRACT OF THE DISCLOSURE
A device for the combustion of pollutants carried in a waste gas flow is equipped with heat exchanger pipes which lead from a gas inlet chamber to a gas combustion chamber.
The combustion gases after the combustible pollutants have been burned off, are guided to flow around the heat exchanger pipes to a gas exit port. In order to enable the heat exchanger pipes to accommodate or compensate tempera-ture expansions and contractions, each heat exchanger pipe is provided intermediate its ends with a double bend having an approximate Z- or S-configuration so that the pipe ends extend approximately in parallel to one another. The inter-mediate pipe sections or legs between the double bends may extend radially or preferably tangentially to a circle having a center coincident with the central axis of the housing of the device.
APPARATUS FOR THE COMBUSTION OF POLLUTANTS CARRIED IN A
WASTE GAS FLOW
ABSTRACT OF THE DISCLOSURE
A device for the combustion of pollutants carried in a waste gas flow is equipped with heat exchanger pipes which lead from a gas inlet chamber to a gas combustion chamber.
The combustion gases after the combustible pollutants have been burned off, are guided to flow around the heat exchanger pipes to a gas exit port. In order to enable the heat exchanger pipes to accommodate or compensate tempera-ture expansions and contractions, each heat exchanger pipe is provided intermediate its ends with a double bend having an approximate Z- or S-configuration so that the pipe ends extend approximately in parallel to one another. The inter-mediate pipe sections or legs between the double bends may extend radially or preferably tangentially to a circle having a center coincident with the central axis of the housing of the device.
Description
~3~
1 FIELD OF THE INvENrrIoN
The invention relates to an apparatus or device for the com-bustion of pollutants carrled in a waste gas flow, for exa~.ple, in exhaust gases or flue gases.
BACKGROUND INFORMATION
German Patent Publication (DE) 3,532,232 ~Obermueller~, pub-lished on March 19, 1987, describes an appaxatus for burning oxidizable components of a carrier gas. The known apparatus comprises a cylindrical housing having an inlet port and an outlet port for the gas flow. The inlet port leads into a distribution chamber which is connected through heal exchansec tubes to a ring chamber near one end or the housing, whereby these heat exchanger tubes are angled radlally outwardly~at their inlet ends and extend over a substantial portion of the housing. A burner is arranged concentrlcally in the ring chamber and a flue gas mixing pipe formed as z cylindrical chamber section is arranged coaxlally to the burner and facing the burner. The flue gas mixing pipe is surrounded by an inner ring chamber closed toward the ~burner and by a main combus-tion chamber located near the free end of the flue gas mixingpipe. The inner ring space in turn leads into an outer ring space which is connec,ted to the outlet port. The axiaL legs of the heat exchanger pipes are arranged in the outer ring chamber so that the ho~ gases flow over the surfaces of the heat exchanger pipes for preheating the gases to be cleaned.
~37~5~
1 Bending the inlet ends of the heat exchanger pipes radially outwardly has the ~dvantage that a larger surface area is available for the insertion of the pipe inlet ends making it simpler to weld these inlet ends into apertures in an inlet chamber wall. Due to the available larger surface area radially out,~ardly, the welded~in ends can be spaced from one another with larger spacings so that the inlet cham-ber wall does not need to be constructed as a separate compo-nent, such as a drum, Rather, the inner wall of the outer ring space inside the housing forming the inlet chamber can be used as the surface area in which apertures are formed for welding the inlet ends of the heat exchanger pipes into the wall of the inlet chamber. Thus, the gas carrying oxidiz-able components flowing into the inlet chamber, is led into the inlet openings of the heat exchanger pipes near the outer circumference of the housing.
From ~uropean Patent Publication ~PO) 0,040 f 690 (Betz et al.) it is known to bend the outlet ends of the heat exchanger pipes radially inwardly to reach toward the burner. For this purpose it is neGessery to provlde a separate drum that surrounds the burner concentrically with apertures into which the radially inwardly bent outlet ends of the heat ex-changer pipes are weld`ed.
In both instances, namely bending the inlet ends of the heat exchanger pipes radially outwardly and bending the outlet ends of the heat exchanger pipes radially inwardly, there i5 the disadvantage that the radially extending legs or sections 1 of the heat exchanger pipes must have differing lengths deper.d-ing on the particu]ar radius at which the heat exchanger pipe is mounted within the apparatus. This is necessary because either the radially inner wall of the inlet chamber or the drum around the burner are cylindrical so that the length of the radially bent legs of the heat exchanyer pipes will depend on the posit~ion of the respective pipe away from the correspond-ing cylindrical wall. Due to these different rzdial lengths it is difficult to provide a uniform heat expansion and con-traction chacteristic for the heat exchanger pipes. Dueto the mentioned different radial length, each pipe has a different elasticity, whereby the stresses in the heat exchanger pipes are larger in the short legs than in the longer legs, because the longer legs have a larger elasticity than the shorter legs. However, for an effective compensation or accommodation of heat expansions and contractions, it is essential that all heat exchanger pipes are exposed to the same forces which can only be achieved if all the heat exchanger pipes have the same elastic yielding ability.
Another disadvantage of the known structures is seen in that the welding of the radially outwardly bent pipe inlet ends into the inner wall of the cylindrical inle~ chamber removes a substantial proportion of the pipe leg from any ability to yield elastically, because a substantial proportion of the pipe leg is rigidly clamped, so to speak, by the welding seam so that this portion cannot participate in the compensa-tion or yielding to heat expansions and contractions. Since ~7~
1 these pipes are arranged in groups so that each group occupies another cylinder, so to speak., each cylinder having a differ-ent diameter, the radially outermost group will have the shortest radially outwardly bent legs in the case with the pipe inlet ends being bent radially outwardly. Similarly, in the case in which the pipe outlet ends are bent radially inwardly, the innermost group will have the shortest radially extendlng legs. In both instances the pipe group with the shortest radial legs will have the least flexible yieldability so that its ability to compensate for heat expansions and contractions will differ substantlally from the respective abilities of the other pipe groups.
OBJECTS OF THE INVENTION
In view of the ~oresoing, it is the aim of the invention : to achieve the following objects singly or in combination:
: ~ .
to construct an apparatus for the combustion of oxidizable components in waste gases, wherein all heat ex-changer pipes have substantially the same abilities to com-: : pensate for heat expansions and contractions so that each heat exchange pipe can elastically bend in the same way as : all the other heat exchange pipes;
to minimize the forces and hence the stress thatis effective on each of the heat exchanger pipes;
% ~
1 to make sure that the heat exchanger pipes are not exposed to adverse vibrations during operation of the apparatus; and -to shape and mount all heat exchanger pipes in such a way that their flexibility or elastic yielding is substantially increased.
SUM~RY OF THE INVENTION
The above objects have been achieved according to the invention by providing each heat exchanger pipe intermediate its ends with a Z-bent configuration or with an S-bent configuration, and to mount the heat exchanger pipes so that their straight legs extend in parallel to one another. Preferably, the :: :
Z- or S-bent configuration is located cLoser to the lnlet : ends of the heat exchanger pipes than to their outlet:ends.
:
The construction according to~the invention has the advantase that all radii of the bent configurations can have the same dimensions. Similarly, the pipe length between the two.bent portions may all have the same length. Preferably, the pipe sections between neighboring bends in the same pipe are arranged : :
along tangential lines to a circle that has its center in ~ : the longitudinal central axis of the cylindrical housing ;~ ~ of the apparatus. By arranging the intermediate pipe sections along tangential lines, as just mentioned, it is possible to make these intermediate sections longer than when~these sec-tions extend radially, without changing the other dimensions 1 of the apparatus. Due to the longer intermediate sections, the flexibility of the heat exchanger pipes is substantially increased so that an excellent compensation ~or heat expan-sions and contractions is obtained.
According to a further feature of the invention the inlet ends of the heat exchanger pipes extend axially into a ring disk which forms a wall of a gas inlet distribution chamber to which the inlet port is connected. For this purpose the gas distribution inlet chamber and a portion of the outer heat exchange chamber have an enlarged diameter.
BRIEF DESCRIPTION OF THE DRAWINGS
In order that the invention may be clearly understood, it will now be described, by way of example, with reference to the accompanying drawings, wherein:
Fig. 1 is an axial sectional view through a combus-tion apparatus according to the invention, and Fis. 2 illustrates schematically the arrangement of the intermediate heat exchanger pipe sections along tangential lines relative to a central circle, whereby only a few plpe sections are shown.
~37~
1 DETAILED DESCRIPTION OF A PREFERRED EXAMPLE EMBODIME~T AND
OF THE BEST MODE OF THE INVENTION
Referring to Fig. 1, the present apparatus comprises a hous-ing 1 with a central axis A. The housing 1 has an inner casing 2a surrounded by heat insulation 2. The right-hand end of the housing 1 is closed by an end wall 3 covering a radially outer ring chamber 5 connected to an inlet port 4 for the inlet flow 4a of waste gas. The central portion of the end wall 3 also covers a flow eddying chamber 15 which forms a main combustion chamber. The inlet ring chamber 5 is provided with a metal liner which includes a ring disk 6 with apertures into which the axially extending inlet ends 8b OL heat exchanger pipes 7 are welded or brazed.
According to the invention the heat exchange pipes 7 are provided intermediate their inlet ends 8b and their exit ends 7a with a double bend section having approximately a Z- or S-configuration. A first bend 8 is formed between the longer axially extending legs of the heat exchanger pipes 7 and an intermediate leg 9. A second bend 8a is formed between the intermediate leg 9 and the shorter also axially extending inlet ends 8b of the heat exchanger pipes. The open ends of the pipe sections 8b pass through the apertures in the ring disk 6. The longer legs of the heat exchanger pipes 7 extend axially and are arranged in groups, each forming a cylinder of pipe sections. These longer pipe sections extend through an outer ring chamber 18 within the housing. The bends 8, the ~37~
1 intermediate legs 9, and the bends 8a as well as the short in-let ends 8b of the pipes are located in a flow exit r~ng cham-ber 19 which has an enlarged outer diameter compared to the above mentioned outer ring space or chamber 18. An exit port 20 is connected to the exlt ring chamber 19 for the e~it flow 20a. The exit ends 7a of the heat exchanger pipes are passing through holes in a separation wall 10 at the left-hand end of the housing 1 which is closed by a further end wall 11.
The pipe ends 7a which pass through holes or apertures in the separation wall lO,are all welded or brazed into these holes.
The separation wall 10 is axially spaced from the inwardly facin~ surface of the end wall 11 to form a ring chamber lZ
surrounding a burner 13 receiving fuel through a fuel pipe 13a.
The gases to be cleaned thus enter out of the exit ends 7a into the ring chamber 12 and pass thxough holes in the jacket of the burner 13 into the burner. Some of the gases to be cleaned pass through a gap between the burner jacket and a funnel portion 14a of a high speed flow pipe 14 arranged concentrically in the housing 1 and coaxially relative to the burner 13.
Although the inlet ends 8b of the heat exchanger pipes 7 are rigidly connected to the ring disk 6 and although the exit ends 7a of the pipes 7 are rigidly connected to the separa-tion wall 10, heat expansions and contractions are elastically taken up and thus compensated by the ability of the pipes 7 to deform with the help of the double bends 8, 8a. A complete compensation of temperature dependent length changes of the pipes 7 is thus possible. The deformation ability of the double _ g _ 1 bends 8, 8a is the larger, the longer the intermediate pipe legs 9 are~ Therefore, it is preferable to arrange the pipe legs 8 along tangential lines, rather than radially.
Referring to Fig. 2, which is a view in the direction of the central housing axis A from right to left in Fig. 1, two lm-aginary clrcles B and C are shown within the metal casing 2a of the housing 1. The circles B and C have their center in the central housing axis A. The intermediate pipe legs 9 extend approximately tangentially to the circles B and C.
The illustration is merely schematical and the extens:ion of the intermedlate pipe legs 9 may be actually more radially than is actually shown in Fig. 2. Under certain circumstances, a radial arrangement may also be desirable, depending on how many pipes need to be mounted in a given available space.
Fig. 2 is not drawn to any scale. For example, the diameter of the circles B and C may correspond approximately to one half of the outer diameter of the housing. This type of ar-rangement permits the intermediate pipe legs 9 to have a maxi-mal length between the bends 8 and 8a, whereby the pipes 7 can make use of their maximum elasticity for an unhindered length change compensation.
Referring again to Fig. 1, the jacket of the burner 13 reaches into the funnel portion 14a of a high 10w speed flue gas mix-ing pipe 14 which merges into the funnel section 14a through a diverging section 14b. In other words, as viewed in the flow direction, the pipe section 14b is diverging. However, it converges toward the funnel section 14a. The right-hand end 1 of the pipe section 14 ope~s into the above mentioned flow eddying main combustion chamber 15 enclosed by the end wall 3.
The pipe section 14 is surrounded by an inner ring space 16 enclosed by a second pipe section 16a haviny an inner metal wall surrounded by heat insulation 16b which in turn is sur- :
rounded by a further metal wall 16c. The second pipe section with its elements 16a, 16b, and 16c preferably forms an ex-tension of the chamber 15. The just mentioned extension, 16a, 16b, 16c, surrounds the pipe section 14 for a substan-tial proportion of its length to form the inner rins chamberor space 16 which meryes into a flow detour chamber 17 formed between the separation wall 10, the funnel section 14a, the pipe section 14b, the inner casing 2a, and a flange 16d form-ing the left-hand end of the second pipe section 16a. The : flange lea~es a flow gap between its outer circumference and the inner casing 2a for the cleaned gases to pass around the heat exchanger pipes 7 mounted in the outer ring space or chamber 18. Additional baffle plates may be arranged as shown to cause a meandering flow of the hot gases around the heat exchanger pipes 7 in the chamber 18. The outer ring space merges into the above mentioned larger diameter exit ring chamber 19 and out of the chamber through the exit port 20. The bends 8, 8a and the pipe legs 9 are located in the chamber 19 which partially surrounds the wall of the flow eddying chamber 15.
1 FIELD OF THE INvENrrIoN
The invention relates to an apparatus or device for the com-bustion of pollutants carrled in a waste gas flow, for exa~.ple, in exhaust gases or flue gases.
BACKGROUND INFORMATION
German Patent Publication (DE) 3,532,232 ~Obermueller~, pub-lished on March 19, 1987, describes an appaxatus for burning oxidizable components of a carrier gas. The known apparatus comprises a cylindrical housing having an inlet port and an outlet port for the gas flow. The inlet port leads into a distribution chamber which is connected through heal exchansec tubes to a ring chamber near one end or the housing, whereby these heat exchanger tubes are angled radlally outwardly~at their inlet ends and extend over a substantial portion of the housing. A burner is arranged concentrlcally in the ring chamber and a flue gas mixing pipe formed as z cylindrical chamber section is arranged coaxlally to the burner and facing the burner. The flue gas mixing pipe is surrounded by an inner ring chamber closed toward the ~burner and by a main combus-tion chamber located near the free end of the flue gas mixingpipe. The inner ring space in turn leads into an outer ring space which is connec,ted to the outlet port. The axiaL legs of the heat exchanger pipes are arranged in the outer ring chamber so that the ho~ gases flow over the surfaces of the heat exchanger pipes for preheating the gases to be cleaned.
~37~5~
1 Bending the inlet ends of the heat exchanger pipes radially outwardly has the ~dvantage that a larger surface area is available for the insertion of the pipe inlet ends making it simpler to weld these inlet ends into apertures in an inlet chamber wall. Due to the available larger surface area radially out,~ardly, the welded~in ends can be spaced from one another with larger spacings so that the inlet cham-ber wall does not need to be constructed as a separate compo-nent, such as a drum, Rather, the inner wall of the outer ring space inside the housing forming the inlet chamber can be used as the surface area in which apertures are formed for welding the inlet ends of the heat exchanger pipes into the wall of the inlet chamber. Thus, the gas carrying oxidiz-able components flowing into the inlet chamber, is led into the inlet openings of the heat exchanger pipes near the outer circumference of the housing.
From ~uropean Patent Publication ~PO) 0,040 f 690 (Betz et al.) it is known to bend the outlet ends of the heat exchanger pipes radially inwardly to reach toward the burner. For this purpose it is neGessery to provlde a separate drum that surrounds the burner concentrically with apertures into which the radially inwardly bent outlet ends of the heat ex-changer pipes are weld`ed.
In both instances, namely bending the inlet ends of the heat exchanger pipes radially outwardly and bending the outlet ends of the heat exchanger pipes radially inwardly, there i5 the disadvantage that the radially extending legs or sections 1 of the heat exchanger pipes must have differing lengths deper.d-ing on the particu]ar radius at which the heat exchanger pipe is mounted within the apparatus. This is necessary because either the radially inner wall of the inlet chamber or the drum around the burner are cylindrical so that the length of the radially bent legs of the heat exchanyer pipes will depend on the posit~ion of the respective pipe away from the correspond-ing cylindrical wall. Due to these different rzdial lengths it is difficult to provide a uniform heat expansion and con-traction chacteristic for the heat exchanger pipes. Dueto the mentioned different radial length, each pipe has a different elasticity, whereby the stresses in the heat exchanger pipes are larger in the short legs than in the longer legs, because the longer legs have a larger elasticity than the shorter legs. However, for an effective compensation or accommodation of heat expansions and contractions, it is essential that all heat exchanger pipes are exposed to the same forces which can only be achieved if all the heat exchanger pipes have the same elastic yielding ability.
Another disadvantage of the known structures is seen in that the welding of the radially outwardly bent pipe inlet ends into the inner wall of the cylindrical inle~ chamber removes a substantial proportion of the pipe leg from any ability to yield elastically, because a substantial proportion of the pipe leg is rigidly clamped, so to speak, by the welding seam so that this portion cannot participate in the compensa-tion or yielding to heat expansions and contractions. Since ~7~
1 these pipes are arranged in groups so that each group occupies another cylinder, so to speak., each cylinder having a differ-ent diameter, the radially outermost group will have the shortest radially outwardly bent legs in the case with the pipe inlet ends being bent radially outwardly. Similarly, in the case in which the pipe outlet ends are bent radially inwardly, the innermost group will have the shortest radially extendlng legs. In both instances the pipe group with the shortest radial legs will have the least flexible yieldability so that its ability to compensate for heat expansions and contractions will differ substantlally from the respective abilities of the other pipe groups.
OBJECTS OF THE INVENTION
In view of the ~oresoing, it is the aim of the invention : to achieve the following objects singly or in combination:
: ~ .
to construct an apparatus for the combustion of oxidizable components in waste gases, wherein all heat ex-changer pipes have substantially the same abilities to com-: : pensate for heat expansions and contractions so that each heat exchange pipe can elastically bend in the same way as : all the other heat exchange pipes;
to minimize the forces and hence the stress thatis effective on each of the heat exchanger pipes;
% ~
1 to make sure that the heat exchanger pipes are not exposed to adverse vibrations during operation of the apparatus; and -to shape and mount all heat exchanger pipes in such a way that their flexibility or elastic yielding is substantially increased.
SUM~RY OF THE INVENTION
The above objects have been achieved according to the invention by providing each heat exchanger pipe intermediate its ends with a Z-bent configuration or with an S-bent configuration, and to mount the heat exchanger pipes so that their straight legs extend in parallel to one another. Preferably, the :: :
Z- or S-bent configuration is located cLoser to the lnlet : ends of the heat exchanger pipes than to their outlet:ends.
:
The construction according to~the invention has the advantase that all radii of the bent configurations can have the same dimensions. Similarly, the pipe length between the two.bent portions may all have the same length. Preferably, the pipe sections between neighboring bends in the same pipe are arranged : :
along tangential lines to a circle that has its center in ~ : the longitudinal central axis of the cylindrical housing ;~ ~ of the apparatus. By arranging the intermediate pipe sections along tangential lines, as just mentioned, it is possible to make these intermediate sections longer than when~these sec-tions extend radially, without changing the other dimensions 1 of the apparatus. Due to the longer intermediate sections, the flexibility of the heat exchanger pipes is substantially increased so that an excellent compensation ~or heat expan-sions and contractions is obtained.
According to a further feature of the invention the inlet ends of the heat exchanger pipes extend axially into a ring disk which forms a wall of a gas inlet distribution chamber to which the inlet port is connected. For this purpose the gas distribution inlet chamber and a portion of the outer heat exchange chamber have an enlarged diameter.
BRIEF DESCRIPTION OF THE DRAWINGS
In order that the invention may be clearly understood, it will now be described, by way of example, with reference to the accompanying drawings, wherein:
Fig. 1 is an axial sectional view through a combus-tion apparatus according to the invention, and Fis. 2 illustrates schematically the arrangement of the intermediate heat exchanger pipe sections along tangential lines relative to a central circle, whereby only a few plpe sections are shown.
~37~
1 DETAILED DESCRIPTION OF A PREFERRED EXAMPLE EMBODIME~T AND
OF THE BEST MODE OF THE INVENTION
Referring to Fig. 1, the present apparatus comprises a hous-ing 1 with a central axis A. The housing 1 has an inner casing 2a surrounded by heat insulation 2. The right-hand end of the housing 1 is closed by an end wall 3 covering a radially outer ring chamber 5 connected to an inlet port 4 for the inlet flow 4a of waste gas. The central portion of the end wall 3 also covers a flow eddying chamber 15 which forms a main combustion chamber. The inlet ring chamber 5 is provided with a metal liner which includes a ring disk 6 with apertures into which the axially extending inlet ends 8b OL heat exchanger pipes 7 are welded or brazed.
According to the invention the heat exchange pipes 7 are provided intermediate their inlet ends 8b and their exit ends 7a with a double bend section having approximately a Z- or S-configuration. A first bend 8 is formed between the longer axially extending legs of the heat exchanger pipes 7 and an intermediate leg 9. A second bend 8a is formed between the intermediate leg 9 and the shorter also axially extending inlet ends 8b of the heat exchanger pipes. The open ends of the pipe sections 8b pass through the apertures in the ring disk 6. The longer legs of the heat exchanger pipes 7 extend axially and are arranged in groups, each forming a cylinder of pipe sections. These longer pipe sections extend through an outer ring chamber 18 within the housing. The bends 8, the ~37~
1 intermediate legs 9, and the bends 8a as well as the short in-let ends 8b of the pipes are located in a flow exit r~ng cham-ber 19 which has an enlarged outer diameter compared to the above mentioned outer ring space or chamber 18. An exit port 20 is connected to the exlt ring chamber 19 for the e~it flow 20a. The exit ends 7a of the heat exchanger pipes are passing through holes in a separation wall 10 at the left-hand end of the housing 1 which is closed by a further end wall 11.
The pipe ends 7a which pass through holes or apertures in the separation wall lO,are all welded or brazed into these holes.
The separation wall 10 is axially spaced from the inwardly facin~ surface of the end wall 11 to form a ring chamber lZ
surrounding a burner 13 receiving fuel through a fuel pipe 13a.
The gases to be cleaned thus enter out of the exit ends 7a into the ring chamber 12 and pass thxough holes in the jacket of the burner 13 into the burner. Some of the gases to be cleaned pass through a gap between the burner jacket and a funnel portion 14a of a high speed flow pipe 14 arranged concentrically in the housing 1 and coaxially relative to the burner 13.
Although the inlet ends 8b of the heat exchanger pipes 7 are rigidly connected to the ring disk 6 and although the exit ends 7a of the pipes 7 are rigidly connected to the separa-tion wall 10, heat expansions and contractions are elastically taken up and thus compensated by the ability of the pipes 7 to deform with the help of the double bends 8, 8a. A complete compensation of temperature dependent length changes of the pipes 7 is thus possible. The deformation ability of the double _ g _ 1 bends 8, 8a is the larger, the longer the intermediate pipe legs 9 are~ Therefore, it is preferable to arrange the pipe legs 8 along tangential lines, rather than radially.
Referring to Fig. 2, which is a view in the direction of the central housing axis A from right to left in Fig. 1, two lm-aginary clrcles B and C are shown within the metal casing 2a of the housing 1. The circles B and C have their center in the central housing axis A. The intermediate pipe legs 9 extend approximately tangentially to the circles B and C.
The illustration is merely schematical and the extens:ion of the intermedlate pipe legs 9 may be actually more radially than is actually shown in Fig. 2. Under certain circumstances, a radial arrangement may also be desirable, depending on how many pipes need to be mounted in a given available space.
Fig. 2 is not drawn to any scale. For example, the diameter of the circles B and C may correspond approximately to one half of the outer diameter of the housing. This type of ar-rangement permits the intermediate pipe legs 9 to have a maxi-mal length between the bends 8 and 8a, whereby the pipes 7 can make use of their maximum elasticity for an unhindered length change compensation.
Referring again to Fig. 1, the jacket of the burner 13 reaches into the funnel portion 14a of a high 10w speed flue gas mix-ing pipe 14 which merges into the funnel section 14a through a diverging section 14b. In other words, as viewed in the flow direction, the pipe section 14b is diverging. However, it converges toward the funnel section 14a. The right-hand end 1 of the pipe section 14 ope~s into the above mentioned flow eddying main combustion chamber 15 enclosed by the end wall 3.
The pipe section 14 is surrounded by an inner ring space 16 enclosed by a second pipe section 16a haviny an inner metal wall surrounded by heat insulation 16b which in turn is sur- :
rounded by a further metal wall 16c. The second pipe section with its elements 16a, 16b, and 16c preferably forms an ex-tension of the chamber 15. The just mentioned extension, 16a, 16b, 16c, surrounds the pipe section 14 for a substan-tial proportion of its length to form the inner rins chamberor space 16 which meryes into a flow detour chamber 17 formed between the separation wall 10, the funnel section 14a, the pipe section 14b, the inner casing 2a, and a flange 16d form-ing the left-hand end of the second pipe section 16a. The : flange lea~es a flow gap between its outer circumference and the inner casing 2a for the cleaned gases to pass around the heat exchanger pipes 7 mounted in the outer ring space or chamber 18. Additional baffle plates may be arranged as shown to cause a meandering flow of the hot gases around the heat exchanger pipes 7 in the chamber 18. The outer ring space merges into the above mentioned larger diameter exit ring chamber 19 and out of the chamber through the exit port 20. The bends 8, 8a and the pipe legs 9 are located in the chamber 19 which partially surrounds the wall of the flow eddying chamber 15.
2~3~
l I desired, the exit port ~0 may be arranyed next -to the inlet port 4 and the inlet flow direc~ion may be parallel to the outlet flow direction as shown by the respective arrows 4a and 20a.
The intermediate pipe legs or sections 9 preferably all have the same length to make the heat e~pansion and contraction characteristics of all the pipes as uniform as possible. In any event, long intermediate legs 9 increase the elastic abil-ity to compensate larger heat expansions and contractions.
The angles enclosed between each intermediate pipe leg or sec tion 9 and the xespective pipe ley 8b or 7 is about 90 more or less, whereby the pipes are easily mountable.
Although the invention has been described with reference to specific example embodiments it will be appreciated that it is intended to cover all modifications and equivalents within the scope of the appended claims.
,
l I desired, the exit port ~0 may be arranyed next -to the inlet port 4 and the inlet flow direc~ion may be parallel to the outlet flow direction as shown by the respective arrows 4a and 20a.
The intermediate pipe legs or sections 9 preferably all have the same length to make the heat e~pansion and contraction characteristics of all the pipes as uniform as possible. In any event, long intermediate legs 9 increase the elastic abil-ity to compensate larger heat expansions and contractions.
The angles enclosed between each intermediate pipe leg or sec tion 9 and the xespective pipe ley 8b or 7 is about 90 more or less, whereby the pipes are easily mountable.
Although the invention has been described with reference to specific example embodiments it will be appreciated that it is intended to cover all modifications and equivalents within the scope of the appended claims.
,
Claims (6)
1. An apparatus for the combustion of pollutants in a waste gas flow, comprising cylindrical housing means for enclosing a combustion chamber, gas inlet means for the entry of polluted gas, gas exit means for the exit of cleaned gas, burner means for burning said pollutants, gas flow means for leading a gas flow from said inlet means through said combus-tion chamber to said outlet means, said gas flow means com-prising heat exchanger pipes for leading polluted gas from said inlet means substantially to said burner means, said gas flow means further including a flow chamber in which said heat exchanger pipes are mounted for preheating polluted gas before it reaches said burner means, each of said heat exchanger pipes having a double bend therein, each bend con-necting an intermediate pipe section to a substantially straight pipe section, so that said straight pipe sections of heat exchanger pipes extend substantially in parallel to one another for accommodating temperature dependent changes-in said heat exchanger pipes.
2. The apparatus of claim 1, wherein said double bend is located closer to heat exchange pipe inlet ends than to heat exchange pipe outlet ends.
3. The apparatus of claim 1, wherein said intermediate pipe sections are arranged approximately on tangential lines of a circle having its center on a central longitudinal axis of said cylindrical housing.
4. The apparatus of claim 1, wherein said gas flow means comprise an exit chamber leading into said gas flow exit means, said exit chamber having an enlarged diameter to provide space for said double bends and said intermediate pipe sections located in said exit chamber.
5. The apparatus of claim 1, wherein said intermediate pipe sections of all heat exchanger pipes have the same length between two bends forming said double bends.
6. The apparatus of claim 1, wherein each bend encloses an angle of about 90°.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4007626 | 1990-03-10 | ||
| DEP4007626.1-13 | 1990-03-10 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2037864A1 true CA2037864A1 (en) | 1991-09-11 |
Family
ID=6401879
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002037864A Abandoned CA2037864A1 (en) | 1990-03-10 | 1991-03-08 | Apparatus for the combustion of pollutants carried in a waste gas flow |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0447631B1 (en) |
| AT (1) | ATE102327T1 (en) |
| CA (1) | CA2037864A1 (en) |
| DE (1) | DE59004810D1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5601789A (en) * | 1994-12-15 | 1997-02-11 | W. R. Grace & Co.-Conn. | Raw gas burner and process for burning oxygenic constituents in process gas |
| US5609833A (en) * | 1994-12-15 | 1997-03-11 | W. R. Grace & Co.-Conn. | Process and apparatus for burning oxygenic constituents in process gas |
| US5620668A (en) * | 1994-08-17 | 1997-04-15 | W.R. Grace & Co.-Conn. | Annular air distributor for regenerative thermal oxidizers |
| US5762880A (en) * | 1996-12-16 | 1998-06-09 | Megtec Systems, Inc. | Operational process and its improved control system of a secondary air burner |
| CN110566982A (en) * | 2019-10-10 | 2019-12-13 | 郭志斌 | Combustion device for waste gas environment-friendly treatment |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2218528B1 (en) * | 1973-02-19 | 1977-12-30 | Stein Industrie | |
| DE3532232A1 (en) * | 1985-09-10 | 1987-03-19 | Katec Betz Gmbh & Co | DEVICE FOR BURNING OXIDISABLE COMPONENTS IN A CARRIER GAS |
-
1990
- 1990-12-01 EP EP90123045A patent/EP0447631B1/en not_active Expired - Lifetime
- 1990-12-01 AT AT90123045T patent/ATE102327T1/en not_active IP Right Cessation
- 1990-12-01 DE DE90123045T patent/DE59004810D1/en not_active Expired - Fee Related
-
1991
- 1991-03-08 CA CA002037864A patent/CA2037864A1/en not_active Abandoned
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5620668A (en) * | 1994-08-17 | 1997-04-15 | W.R. Grace & Co.-Conn. | Annular air distributor for regenerative thermal oxidizers |
| US5601789A (en) * | 1994-12-15 | 1997-02-11 | W. R. Grace & Co.-Conn. | Raw gas burner and process for burning oxygenic constituents in process gas |
| US5609833A (en) * | 1994-12-15 | 1997-03-11 | W. R. Grace & Co.-Conn. | Process and apparatus for burning oxygenic constituents in process gas |
| US5618173A (en) * | 1994-12-15 | 1997-04-08 | W.R. Grace & Co.-Conn. | Apparatus for burning oxygenic constituents in process gas |
| US5676536A (en) * | 1994-12-15 | 1997-10-14 | W.R. Grace & Co.-Conn. | Raw gas burner and process for burning oxygenic constituents in process gas |
| US5762880A (en) * | 1996-12-16 | 1998-06-09 | Megtec Systems, Inc. | Operational process and its improved control system of a secondary air burner |
| CN110566982A (en) * | 2019-10-10 | 2019-12-13 | 郭志斌 | Combustion device for waste gas environment-friendly treatment |
Also Published As
| Publication number | Publication date |
|---|---|
| DE59004810D1 (en) | 1994-04-07 |
| EP0447631A3 (en) | 1992-03-11 |
| EP0447631A2 (en) | 1991-09-25 |
| ATE102327T1 (en) | 1994-03-15 |
| EP0447631B1 (en) | 1994-03-02 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |