EP0684428B1 - Device for injecting air into the combustion space of a flare burner and flare burner - Google Patents

Description

The invention relates to an injector for drawing in ambient air and blowing into the combustion chamber of a torch burner the preamble of claim 1. In addition, the invention has a Torch burner according to the preamble of claim 8 Object.

It is already known from EP 0 042 743 A2, ambient air and a Propellant fluid in a generally straight mixing section of a to mix the tubular line section with one another, that of that with significantly higher speed flowing driving fluid the ambient air is sucked in and Mixing takes place on the mixing section.

The aim of the present invention is to provide a Injector and a torch burner of the aforementioned To create genus in which the conveying and mixing performance with comparatively large volume flows of air with comparatively low volume flows of the propellant fluid is optimized that the wall friction in the mixing area as possible reduced and an almost complete pulse output of the propellant fluid to the intake air is achieved. With in other words, the invention wants to be as short as possible Distance optimal and quick mixing of air and propellant fluid with as little loss of impulse transmission as possible reach from the propellant to the air.

To solve this problem, the characteristics of the characteristic Part of claim 1 provided. Particularly advantageous Further developments can be found in claim 2 The idea of the invention is that the expansion of the dead space in the area of the injection openings in particular between injection openings and flow channel wall greater than is the cross section of the injection openings.

A structurally particularly preferred embodiment, which also to a particularly short overall length with optimal mixing performance leads is characterized by the characteristics of the Part of claim 3 defined.

Preferred embodiments of this development are in claims 4 to 7 specified.

A significant reduction in Frictional losses of the ambient air drawn in are thus achieved that the mouth of the inlet is rounded and open flow detachments are largely avoided in this way. The flow dead spaces according to the invention have the advantage that the spray jets have a backflow in the wall area trigger so that an intensive mixing of the Propellant fluids with the incoming air all around Spray jet takes place. The air flow and the Mixing intensity can by the measures according to claim 7 can be improved.

The arrangement of the injection openings for the propellant fluid in A shielded flow dead space also sets the sound radiation to the outside in an advantageous manner.

The embodiments according to claim 4 have the following Benefits:

The intake cross section through the corner areas of the polygon is enlarged and thus increased the throughput of ambient air is, wherein at least one injection opening in the area of Middle of each pipe section should be provided, because there the closest proximity to the center of the ambient air flow. This ensures homogeneous loading and mixing of the propellant fluid with the air significantly favored. As injection openings serve for the driving fluid from the ring tube in simplest case and structurally particularly advantageous cylindrical Holes. The nozzles used can reduce the efficiency the spray jets increase. By using Laval nozzles becomes a maximum implementation of pressure energy of the propellant fluid in the promotion of air serving kinetic energy the spray jets achieved. When the injection openings are arranged in several levels there will be an improvement in homogeneous Mixing and impulse transmission of the spray jets on the Air achieved. Correspondingly, the invention Ring tube a second ring tube may be arranged, which also two axially spaced rings of injection openings for the propellant fluid can be made available. In particular with several superimposed injection opening levels can change the direction of the axes of the injection openings from the perpendicular to the tangent to the cross section of the Ring pipe at the location of the relevant injection opening more in Deviate towards the wall so that the spray jets do not include a too large angle with the central axis.

By largely avoiding wall contact, a Minimization of the wall friction generated by the propellant fluid Spray jets can be achieved. In a particularly advantageous way Way is in the area where the wall contact of the spray jets is avoided in the sense of a backflow of air in the essentially sucked in against the main flow direction and absorbed by the driving fluid from the wall side.

The ring tube is preferably on the mixing area of the flow channel put on, whereby not only an optimal mixing on a short distance, but also an unhindered, Low-loss intake of air from a large part of the environment is made possible. However, it is preferred if which preferably run parallel to the main flow direction Walls of the mixing area at an angle of 90 ° on the tangent to the cross section of the ring tube on the Hit the point of contact between the wall and the ring pipe.

The embodiments according to FIGS Claims 5 and 6. So neither in the mixing area an increase in flow velocity due to convergence of the flow channel still by divergence of the flow channel a flow velocity reduction. Thereby becomes an optimal and particularly low-loss mixing effect achieved.

To increase the throughput of air with constant throughput of the driving fluid turns out to be a downstream of the mixing area Diffuser area as advantageous. This will continues to increase the vacuum in the mixing area and the Insensitivity to air pressure fluctuations increased. In an arrangement with a downstream diffuser are ratios of the throughput of ambient air to propellant fluid between 10 and 25 possible.

The subdivision of the diffuser area is also particularly advantageous in at least two sections with the help of in Direction of flow arranged baffles, as a result of which flow-delaying and pressure-building effect of the diffuser area is improved, which in particular the expansion angle of the diffuser increases and the diffuser length can be reduced.

The application of the invention is particularly advantageous for a torch burner according to claim 8. In this application the cross wind sensitivity of the torch burner becomes essential reduced. Furthermore, light weight and ease small dimensions of the injector according to the invention and reduce the attacking wind forces and weight forces in the area of high altitude at the end of the fireplace Exhaust pipe arranged combustion chamber, in which the actual combustion only takes place at minimum load, while flaring larger amounts of flare gas there only intensive mixing of flare gas and air / propellant fluid mixture takes place while the combustion is above the outlet opening takes place. A windshield can reduce cross wind sensitivity still improve especially in the partial load range. Through optimized air intake from the environment the throughput is also when a large number of injectors are arranged improved in a confined space. The noise emission of the Torch burner is due to the low-noise design of the injectors significantly reduced. It also completeness encourages combustion and thus reduces soot formation.

Advantageous embodiments of the torch burner according to the invention are characterized by claims 9 and 10.

The use of steam as is advantageous Propellant fluid because e.g. in ethylene plants anyway Is available and another about the water gas reaction has some influence on the soot suppression process. By the staggered arrangement of the injectors act out of them mixture jets entering the combustion chamber as Barrier grille for the flare gas fed through the exhaust pipe. They are therefore mixture-promoting and there is one Improvement of combustion processes with regard to freedom from soot and burnout.

Basically, the injectors according to the invention can cylindrical part of the torch burner. However, their arrangement in a top of the exhaust pipe is preferred provided, flared combustion chamber.

If the injectors are at least perpendicular to the lateral surface of the conical combustion chamber and up to an angle of 30 ° upwards to the central axis of the combustion chamber are arranged, this helps to improve the homogeneous Mixing the combustion air into the flare gas suitable setting of the injector angle.

The swirl improves the combustion in that cold torch gas layers in the centrifugal field due to their higher density are carried outwards into the peripheral zone, where they are intensely mixed with the combustion air supplied there Can come in contact. With alternating twist pro with Injectors provided the homogeneous mixing the combustion air with the flare gas further favored.

Fig. 1

eine schematische axiale Schnittansicht durch eine erste Ausführungsform eines Injektors gemäß der Erfindung,

Fig. 2

eine entsprechende, noch stärker schematisierte Schnittansicht einer weiteren Ausführungsform eines erfindungsgemäßen Injektors,

Fig. 3

einen stark schematisierten Schnitt nur durch den Mischbereich einer weiteren Ausführungsform eines erfindungsgemäßen Injektors,

Fig. 4

eine schematische Schnittansicht des mit einem polygonalen Ringrohr versehenen Mischbereiches einer weiteren Ausführungsform eines erfindungsgemäßen Injektors,

Fig. 5

einen vergrößerten Schnitt nach Linie V-V in Fig.4,

Fig. 6

einen Axialschnitt einer weiteren Ausführungsform eines erfindungsgemäßen Injektors mit zwei Ringanordnungen von Einblasöffnungen,

Fig. 7

eine Teildraufsicht des Gegenstandes der Fig. 6 bei teilweise aufgebrochenem Ringrohr,

Fig. 8

eine Schnittansicht einer weiteren Ausführungsform zur Erläuterung der Wirkungen eines erfindungsgemäßen Injektors, wobei links und rechts der Mittelachse verschiedene Ausführungsformen dargestellt sind, die

Fig. 8a, 8b und 8c

verschiedene weitere Ausführungsformen für die Ausbildung und Anordnung der Zusatzluftansaugöffnungen, und

Fig. 9

einen Axialschnitt durch den oberen Bereich eines Fackelbrenners, an welchem Injektoren nach einem der vorangehenden Ausführungsbeispiele angeordnet sind.

The invention is described below, for example with reference to the drawing; in this shows:

Fig. 1

2 shows a schematic axial sectional view through a first embodiment of an injector according to the invention,

Fig. 2

a corresponding, even more schematic sectional view of a further embodiment of an injector according to the invention,

Fig. 3

2 shows a highly schematic section only through the mixing area of a further embodiment of an injector according to the invention,

Fig. 4

2 shows a schematic sectional view of the mixing area provided with a polygonal ring tube of a further embodiment of an injector according to the invention

Fig. 5

an enlarged section along line VV in Figure 4,

Fig. 6

3 shows an axial section of a further embodiment of an injector according to the invention with two ring arrangements of injection openings,

Fig. 7

6 with a partially broken ring tube,

Fig. 8

a sectional view of a further embodiment to explain the effects of an injector according to the invention, different embodiments are shown to the left and right of the central axis, the

8a, 8b and 8c

various other embodiments for the formation and arrangement of the additional air intake openings, and

Fig. 9

an axial section through the upper region of a torch burner, on which injectors are arranged according to one of the preceding embodiments.

9 shows the upper end of a torch burner 11 its vertically arranged outdoors, a vertical one Exhaust pipe 32 having flare gas in central axis 34 Direction of arrows 38 flows upward. In the upper end area the exhaust pipe 32 is an expanding upward frustoconical peripheral wall 33 on the circular cylindrical below Part set, the lower cross section with the adjacent upper cross section of the circular cylindrical Part of the exhaust pipe 32 is congruent. In the area of The largest upper cross section 39 opens the exhaust pipe 32 in the surrounding atmosphere 40.

Along the circumference of the circumferential wall 33 are in two in Distance between horizontal planes 41, 42 in uniform peripheral distances injectors according to the invention 12 arranged with an interior 49, as follows will be described in detail with reference to FIGS. 1 to 8.

The injectors 12 are filled with motive steam through pipelines 43 charged, for example, a pressure of 9 bar and has a temperature of 450 ° C. This will suck the Injectors in the direction of the curved arrows in FIG. 9 Ambient air and blow it perpendicular to the peripheral wall 33 in the interior of the exhaust pipe 32, where they are with crosses the torch gas 38. By an ignition device, not shown can thus the flammable mixture of flare gas and ignited combustion air supplied by the injectors 12 and the torch gas in the desired manner through the outlet cross-sectional area 39 into the Atmosphere 40 are flared.

The inside of the flared peripheral wall 33 thus represents from the lowest level 41, where combustion air is supplied, a combustion chamber 13.

The same reference numbers are used in the following figures corresponding components as in FIG. 9.

1 comprises a first embodiment of an injector 12 an annular tube 21 with a circular cross section and interior 49, which on the upper circular Input end face 29 of the wall 26 of a flow channel 16 put on and fastened there, for example by welding is. The annular entrance end face 29 is located somewhat radially within the parallel to the central axis 44 of the Injector 12 extending diameter 45 of the circular Cross-section of the ring tube 21. At about an angle of 45 ° to the diameter 45 based on the circular central axis 46 of the ring tube 21 are around the central axis 44 Injection openings 17 are provided in the annular tube 21, through which in the direction of the arrows shown in the injection openings 17 the motive steam supplied through the pipe 43 into the Flow channel 16 can be initiated.

Starting from the front face 29, the Flow channel wall 26 initially nozzle-like until finally in the cross-sectional plane 47 parallel to the generatrix of the wall to the central axis 44, which at the same time the through corresponds to an arrow indicated main flow direction 36. So an area with a circular cylindrical, to the central axis 44 concentric wall 26 'is formed. The Wall 26 'extends further in the main flow direction 36 up to a connection end face 37, to which a diffuser 48 is scheduled. The part tapering like a nozzle could also be designed as a truncated cone against which the wall 26 'connects. The diffuser area 18 could also be the same in the manner of a truncated cone, i.e. with linear generators be trained.

This closes in the main flow direction 36 a mixing area concentrically to the central axis 34 on the ring tube 21 19, which consists of a convexly converging region 19 ' and a wall 26 'parallel to the central axis 44 Area 19 "exists, and a diffuser area 18. The injector 12 becomes the outlet end face 20 in suitable bores 50 in the peripheral wall 33 according to FIG. 9 used and fixed there by welding. The in Fig. 1st upper horizontal plane of the ring tube 21 forms an air intake opening 15, by the in accordance with the curved arrows in Fig. 9 after installation in the torch burner 11 ambient air is sucked in.

1 extends between the radially outer edge 27 of the injection openings 17 and the input end face 29 of the Flow channel wall 26 still a wall piece 25, the length of in Circumferential direction slightly larger than the diameter of the injection openings 17 should be.

Due to the arrangement described arises to the outside, a flow dead space adjoining the injection openings 17 22, so that the exiting from the injection openings 17 Propellant steam first in the dead space 22 and only from this from in through the air intake opening 15 from above Air flow indicated in the direction of the arrows.

Particularly important for a flawless transmission of the Impulse of the high speed through the inlet openings 17 driving steam is not only the Flow dead space 22, but also with parallel to Part 19 "provided with central axis 44 running walls 26 ' the mixing area 19.

In the diffuser 48 four baffles are distributed over the circumference 30 arranged with their planes parallel to Main flow direction 36 and all around radially inside on a streamlined body arranged concentrically to the central axis 44 31 can be attached.

The initial speed of the spray jets 23 in the The order of magnitude of 600 m / s drops to 200 in the mixing area 19 m / s and is approximately 70 at the outlet end face 20 m / s.

Preferred values for the parameters shown in FIG. 1 and their ratios are as follows: D _o / D _M 1.7 to 2.0 D ₁ / D _M 1.2 to 1.4 D ₂ / D _M 1.7 to 2.2 R _O / D _M 0.12 to 0.25. D _M 100 to 200 mm; R _O 10 to 20 mm; d 3 to 8 mm; L _M 60 to 180 mm; Total opening angle of the diffuser area 18 4 ° to 14 °; Length of the diffuser area 18 approx. 100 mm to 200 mm.

Fig. 2 shows an embodiment in which compared to Fig.1 a mixing area 19 with a continuous circular cylindrical, to the circular ring tube 21 and to the central axis 44 concentric wall 26 'is arranged. According to Fig. 2 encounter the walls 26 'of the preferred mixing area 19 approximately perpendicular to the lower tangent of the circular Cross section of the ring tube 21st

What is important in this embodiment is not only the clear one Distance a of the injection openings 17 from the wall 26 ', but also the angle δ at which the through the the blowing vents 17 generated motive steam Spray jets 23 relative to the central axis 44 or the generators of the wall 26 '. In the embodiment according to Fig. 2 shows the angle δ exaggerated; he has preferably a size between 5 and 20 °.

Another important feature of the embodiment according to Fig.2 is that the central axis 44 'of the diffuser area 18 not with the central axis 44 of the mixing area 19 is aligned, but by a small angle of 15 is angled at up to 20 °. To one if possible maintaining continuous flow transition is the Connection end face 37 of the mixing area 19 not perpendicular, but about half the angle δ to the central axis 44 arranged. The corresponding entry end face also points of the diffuser area 18 half the angle δ to its central axis 44 '.

The bending of the diffuser area 18 according to FIG. 2 has the Meaning that when attaching this injector 12 to a torch burner 9, the mixing area 19 is then approximately horizontal can be aligned when the diffuser region 18 into a peripheral wall 33 that widens conically according to FIG. 9 is inserted.

Fig. 3 shows that the ring tube 21 also a semicircular Can have cross-section, which is parallel to the to the central axis 44 wall 26 'of the circular cylindrical Mixing area 19 is placed that the flat Circumferential wall region 21 "of the ring tube 21 with the wall 26 'in of the way shown in Fig. 3 is aligned. In the embodiment 3 is a radial projection of the Ring tube 21 to the outside through the mixing area 19 avoided.

4 and 5 is a fully circular cross-section provided ring tube 21 made of straight tube sections 21 'assembled into a polygonal arrangement. All in all are eight pipe sections 21 'to an octagon arrangement composed. In the embodiment according to FIGS. 4 and 5, each pipe section 21 'has an injection opening only in the middle 17 on.

The angle δ of this embodiment to the wall 26 'or Center axis 44 is also in the embodiment Fig. 5 between 5 and 20 °. The distance a from the central axis of the Injection opening 17 from the wall 26 'corresponds to the thickness b the wall 26 '.

In the embodiment according to FIGS. 6 and 7 have that ring tube 21 provided with a circular cross section, the mixing area 19 and the diffuser area 18 are the same Central axis 44. In contrast to those described above However, exemplary embodiments are in the lower interior Quadrants of the circular tube 21 two ring arrangements of injection openings 17 in axially one above the other Planes 24, 24 'are provided which are perpendicular to the central axis 44 run and thus at different angles to the central axis 44 spray jets entering the mixing area 19 define.

The axes of the injection openings 17 can in the simplest Fall perpendicular to the tangent to the cross section of the ring tube 21 where the opening in question is located, run. However, it is preferred if these axes are slightly inclined towards the wall 26 such that the Spray jets 23 at a smaller angle to the central axis 44 than when exiting vertically. The one in question However, the angle must remain different from zero.

Another embodiment is shown on the right of the central axis 44 in FIG illustrated in the immediately below the Ring tube 21 in the circular cylindrical wall to the outside atmosphere leading holes 53 are provided, which over the entire Circumference are evenly distributed.

Instead of these holes, according to FIGS. 8a, 8b and 8, 8c also recesses 53 ', 53 "or 53"' 'in the upper end face 29 of the flow channel wall 26 can be provided, which either in FIG. 8a in a radial view approximately semicircular, 8b triangular or Fig. 8, 8c are trapezoidal.

The mode of operation of the injector 12 according to the invention is described in following described with reference to FIG. 8.

8 that forms, for example, through 13 to 16 injection openings 17 at a speed of, for example 600 m / s inflowing motive steam spray 23, the first in the flow dead spaces provided according to the invention 22 enter and from this into the actual mixing area 19 arrive. Due to the clear distance of the Injection openings 17 from the peripheral wall 26 'of the mixing area 19 there is a slight backflow in the wall area, because the static pressure of the total flow in the main flow direction 36 along the mixing area 19 to the diffuser area 18 goes up. Due to high turbulent friction large differential speeds already occur here first effective mixing of propellant steam and air, and not just on the side of the Spray jets 23, but also on the central axis 44 pointing side of the spray jets 23.

So the extremely fast steam jets become fast mixed with the intake air. The air gets higher Speed accelerates towards the main flow and the spray jets 23 due to the interaction accordingly delayed. The delay due to pulse delivery from the spray jets to the air succeeds on the comparatively short mixing section 19.

If additional air intake openings 53, 53 ', 53 "are arranged and / or 53 '' 'as shown to the right of the central axis 44 in Fig. 8 (where an embodiment of the auxiliary air intake openings 53 in solid lines and another Embodiment (53 ') shown in dashed lines is) or in FIGS. 8a, 8b and 8c there is additional outside air sucked in, which flows back in the flow channel 16 Air-propellant mixture mixed and the total air flow elevated.

In level 51, this is not quite schematic there balanced speed profile indicated. At the Connection end face 37 for the diffuser area 18 is then located but already a largely even speed profile 52 over the entire cross section of the flow channel 16 before. In the diffuser area 13 then only the Velocity of the air flow mixed with motive steam reduced to such a value as for blowing into the combustion chamber 13 according to FIG. 9 is desired.

Preferred dimensions of the individual components are as follows with reference to FIG. 8: Inner diameter ID of the ring tube 21 115 mm Length LM of the mixing area 19 150 mm Length LD of the diffuser area 18 150 mm Diameter DM of the mixing area 130 mm Diameter DD of the outlet end face 20 of the diffuser area 18 160 mm.

All components of the injector 12 with the exception of the angled one Diffuser area 18 according to FIG. 2 are concentric its central axis 44. The ring tube 21 can be circular or polygonal his.

Reference list

11

Torch burner

12th

Injector

13

Combustion chamber

14

Propellant fluid

15

Air intake opening

16

Flow channel

17th

Injection opening

18th

Diffuser area

19th

Mixing area

19 '

tapered part

19 "

parallel part

20th

Exit face

21

Ring tube

21 '

Pipe shot

21 "

flat peripheral wall area

22

Current dead space

23

Spray jets

24th

level

24 '

level

25th

Wall piece

26

Flow channel wall

26 '

Wall of the mixing area

27

edge

28

convex curved wall piece

29

Entrance face

30th

Baffle

31

Streamlined body

32

Exhaust pipe

33

Peripheral wall

34

Central axis

35

direction

36

Main flow direction

37

Connection face

38

Arrows

39

cross-section

40

the atmosphere

41

horizontal plane

42

horizontal plane

43

pipeline

44

Central axis

44 '

Central axis

45

diameter

46

Central axis

47

Cross-sectional level

48

Diffuser

49

inner space

50

drilling

51

level

52

Speed profile

53

Additional air intake openings

Claims (10)

1. An injector (12) for sucking in environmental air and for injection into the combustion chamber (13) of a torch burner (11) by means of a driving fluid (14), in particular a driving vapour, standing under excess pressure, comprising an air induction opening (15), a flow channel (16) which connects to the air induction opening (15) via an interior space (49) and which has an inlet end face (29), driving fluid injection openings (17) which are arranged in the direction of flow after the air induction opening (15) at the periphery of the flow channel (16) and through which the driving fluid (14) is blown substantially in the direction of flow, but with a component of movement towards the interior of the flow channel (16), into a mixing region (19) extending in the direction of flow where it mixes with the induced air, wherein the flow channel (16) has a diffuser region (18) spaced from the injection openings (17) in the direction of flow and extending in the direction of flow, with the diffuser region being followed by an outlet opening (20) for the mixture of air and driving fluid,
   characterised in that
   the injection openings (17) open into a dead flow space (22) provided at the inner periphery of the interior space (49) and of the flow channel (16), with the dead flow space being formed by a wall piece (25) also extending between the radially outer edge (27) of the injection openings (17) and the inlet end face (29) of the flow channel wall (26) in such a way that spray jets are directed into the mixing region (19) from the dead flow space (22).
2. An injector in accordance with claim 1, characterised in that the flow channel wall (26, 26') is offset radially outwardly by a short distance in the direction of flow immediately behind the injection openings (17), and extends from there in the direction of flow preferably at an acute angle (δ) of preferably 5 to 20° to the driving fluid (14) exiting the injection openings (17), with the spacing of the radially outer edge (27) of the injection openings (17) from the flow channel wall (26) preferably being greater than the diameter of the injection openings (17) and/or in that the injection openings (17) are located in a convexly curved wall piece (25) extending from the flow channel wall (26) in the direction of the air induction opening (15).
3. An injector in accordance with claim 1 or claim 2, characterised in that the air induction opening (15) is made at the interior space of a ring tube (21) supplied with the driving fluid (14) and set on the inlet end face (29) of the mixing region (19) of the flow channel (16) and in that the injection openings (17) are provided in or on the ring tube (21) in the direction of flow subsequent to the smallest cross-section of the interior space (49) of the ring tube (21).
4. An injector in accordance with claim 3, characterised in that the ring tube (21) has a circular cross-section and/or in that the ring tube (21) is made up of more than two, preferably at least four, cylindrical tubular elements (21') preferably circular in cross-section and forming a rectangular to polygonal air induction opening (15), with in particular each tubular element (21') having at least one injection opening (17) attached in its region facing the mixing region (19) and/or in that the injection openings (17) are made as cylindrical bores arranged in the wall of the ring tube (21) and/or in that the tangent at the cross-section of the wall piece (25) extending from the inlet end face (29) of the mixing region (19) of the flow channel wall (26) to the interior space of the flow channel (16) forms an angle of 90 to 40° with the generatrix of the flow channel wall (26) in the region of the intersection between the inlet end face (29) and the ring tube (21).
5. An injector in accordance with one of the preceding claims, characterised in that the mixing region (19) comprises a part (19') convexly tapering from its inlet end face (29) in the direction of flow and a part (19") following in the direction of flow and having walls (26') parallel to the main direction of flow (36) towards the central axis and in that preferably the ratio of the diameter (D₀) of the circular air induction opening (15) of the ring tube (21) to the smallest diameter (D_M) of the mixing region (19) is 1.25 to 2.5, preferably 1.7 to 2.0 and/or in that the ratio of the diameter (D₁) of the mixing region (19) at the inlet end face (29) to the smallest diameter (D_M) of the mixing region (19) is 1.10 to 2.0, preferably 1.2 to 1.4 and/or in that the ratio of the largest diameter (D₂) of the diffuser region (18) to the smallest diameter (D_M) of the mixing region (19) is 1.5 to 2.7, preferably 1.7 to 2.2 and/or in that the ratio of the radius (R₀) of the cross-section of the ring tube (21) to the smallest diameter (D_M) of the mixing region (19) is 0.15 to 0.45, preferably 0.12 to 0.25 and/or in that the generatrices of the walls (26') of the mixing region (19) are parallel to the direction of flow (36) or the central axis in the direction of flow from its inlet end face (29) to the connecting end face (37) and in that the diffuser region (18) connects directly to the mixing region (19) in the direction of flow, with in particular the angle (δ) between the generatrices of the walls (26') of the mixing region (19) and the axis of the injection openings (17) being 5 to 20° and/or in that the mixing region (19), and preferably also the diffuser region (28), have circular cross-sections.
6. An injector in accordance with one of the preceding claims, characterised in that the diffuser region (18) is divided into sections by guide vanes (30) directed in the direction of flow and extending preferably in radial planes, with preferably four crossing guide vanes (30), preferably attached to a streamlined body (31), being provided which divide the interior of the diffuser region (18) into four equal flow cross-sections, with the guide vanes (30) extending in particular from the diffuser terminal end face (37) at least to half the diffuser length and/or in that the diffuser region (18) is joined to the mixing region (19) at an angle, preferably at a small angle, and/or in that the ratio of the flow rate of the environmental air to the driving fluid is between 10 and 25.
7. An injector in accordance with one of the preceding claims, characterised in that additional air induction openings (53, 53', 53", 53"') are provided in the flow channel wall (26) around the central axis (44) directly beneath the injection openings (17) or the ring tube (21) which are preferably aligned axially with the injection openings (17).
8. A torch burner (11) having a chimney-like extraction tube (32) which has a preferably expanding combustion chamber (13), in particular expanding conically, at its upper end with injectors (12) in accordance with one of the preceding claims being laterally arranged in the peripheral wall (33) of the combustion chamber.
9. A torch burner in accordance with claim 8, characterised in that at least one group of injectors (12) is provided uniformly distributed in one horizontal plane (41; 42) around a periphery and preferably a plurality of groups of injectors (12) are provided uniformly distributed in a plurality of vertically spaced horizontal planes (41, 42) around a plurality of axially offset peripheries and/or in that the injectors (12) are arranged directed upwards at least perpendicular to the jacket surface of the conical peripheral wall (33) of the combustion chamber up to a maximum of 30° to the central axis (34) and/or in that the axes of the injectors (12) are in a radial plane of the extraction tube (32) or have a peripheral component so that a certain spin of the flare gas and of the combustion air is created, with in particular the spin generated being of alternate direction in sequential horizontal planes (41, 42) with injectors (12), so that practically no total spin remains at the outlet of the combustion chamber (13).
10. A torch burner in accordance with claim 8 or claim 9, characterised in that the expansion angle of the conical combustion chamber (13) is selected such that the flow rate of the total mixture of flare gas, combustion air and driving fluid calculated using the continuity equation is practically constant under the assumption of a homogeneous mixture in each cross-section of the conical combustion chamber (13) and/or in that saturated or over-heated vapour is used as the driving fluid and is utilised preferably in the temperature range from 130°C to 300°C and in the pressure range from 2 bar to 30 bar.

Images