DE1501922C - Burners for oil, gas or coal dust to fire a boiler room - Google Patents

Description

3 4

Outlet diameter of an air supply pipe 11, in which the combustion accelerating nozzle DJD ₁ - 0.45 flow air in the direction of an arrow A. Behind and

Length of the burner muffle LJD ₁ = about 1.4 at a distance from the inlet end la of the burner muffle 1

Length of the acceleration nozzle _{... LJD 1} = 0.74, the housing 9 is closed by an end wall 12-Thickness of the swirl blades SdID ₁ = 0.03 5 sen, the auxiliary organs of the burner, such as the nozzle diameter of the spray hole d _s / D ₁ = 0.14 system 6, the ignition device and the flame suppression

Diameter of the housing dJD _± = 1.4 wachung (both not shown). Between the

The inlet diameter of the air inlet 13 into the swirl device 3 and the air supply dJD ₁ - 0.6 supply pipe 11 is a homogenization element

lo direction 14 arranged for the flow, which in the

As practical tests have shown, the embodiment is designed as a perforated plate, the soot curve of the burner according to the invention deviates only very little from the ring around the burner muffle 1 in the ideal soot curve. The burner annular space 15 between the burner muffle 1 and the housing 9 thus ensures an extension even with small powers. The swirl vane carrier 7 is so close to optimal combustion. Furthermore, the invention has introduced the housing 9 that only a narrow burner has the great advantage that it remains a stable passage gap for the combustion air, generates a flow pattern which, independently of the reed, forms a throttle point 16 with the dimension s . is nolds number. The burner can therefore be standardized in its ab- Behind the throttle body forms the housing 9 with the measurements, so that different- end wall 12 has an air collection space 17, with which the burner power can be easily scaled by 20 both the inlet 13 of the swirl device 3 and changes in the Dimensions can be achieved- the spray hole 5 are in connection. Between the nen. Inlet 13 and the injection hole 5 are not a throttle

In a preferred embodiment of the invention present, so that the static pressure on these It is provided that the flow comparison points in the air collection space 17 are of the same size. At the Moderating device in the annular space between the 25 front end is the housing 9 by a ringför burner muffle and the housing is arranged, and mige membrane 18 sealed off, that the swirl device has a plate-shaped swirl In the area of the outlet end of the burner muffle 1

Has vane carrier, the outer circumference of which is arranged in this an annular aperture 19, the housing encloses an annular gap forming a throttle point in the illustrated embodiment in the direction with a gap width j which is _{conical to d x} in the 30 of the acceleration nozzle 2. ratio is 0.09. The throttle point 16, which is designed as an annular gap, is located in this embodiment

the equalization device in the annular secured by spacers 20, which are around the Distribute in the channel between the burner muffle and the circumference of the Ge.

housing. At this point, the combustion is running in the burner described.

simple means, for example with a perforated plate 35 as follows: or an annular collar, a flow. The combustion air occurs in the direction of arrow A.

Achieve equalization. The swirl vane carrier through the feed pipe 11 into the housing 9. has the additional function, together with the housing, it flows through it as a flow equalization unit To form throttle point. transmission device 14 acting perforated plate is through

One embodiment of the invention is in FIG. 40 the stowage taking place there evenly over the Drawing shown and is distributed in the following more closely the scope of the burner muffle and comes with described. calmed flow to which a throttle point 16 forms

The burner shown in the illustration has a burning ring gap. There is a further flown muffle 1, which takes place from its inlet end la to calm down. The majority of the combustion air outlet end Ib widens conically. An acceleration nozzle 2 then reaches the outlet 45 from the air collection space 17 through the end. At the swirl device 3 in the inlet end la of the burner inlet end there is a swirl device 3 with a pre-muffle. However, some of the air also flows through gently radial swirl blades 4, which have a thickness sr> in the drawing, through which the fuel is injected in a direction of the burner muffle axis O , also not visible in the drawing Spiral 50 In the burner muffle, the combustion angle β of the air inlet moves against the circumferential direction of air as a result of the swirl in a helical manner to produce the outlet. Ib ends in axis O of the burner. As a result of the expansion of the burner muffle, there is a spray hole 5 at the inlet end la , thereby reducing the circumferential component of the centrifugal force acting on the combustion of a nozzle system 6 in the burner muffle through which fuel, especially oil, by means of flow and thus also the air acting on the combustion of a nozzle system 6. From point R in the exit can be. The swirl vanes 4 are at a plate-shaped point Q in the inlet cross-section, which is attached to part of the swirl vane carrier 7, expediently combustion air against the main flow in one piece with this. On which the swirl sucks back. Between the side opposite the wall close to the flow, the vane carrier 7 is the swirl 60 and the central return flow, a door device is formed by a likewise plate-shaped bulge area in which the fuel cover plate 8 is intensively closed, which in its center is mixed with the combustion air. Which does not contain the spray hole. The recirculating portion passes through the free cross. The burner muffle 1 is cut over part of its length of the aperture 19 in the acceleration nozzle surrounded by a cylindrical housing 9, which at 65 and leaves the burner in the form of a very fast surface 10 on the wall of the to be fired heating flame gas jet. A space (not shown) that can be flange-mounted is formed behind the panel 19. Eddy W from which the boundary layer of the air flow at the front end of the housing opens into the flame jet. From point P to point

R in the exit cross-section of the acceleration nozzle there is also a pressure gradient.

The portion of the combustion air flowing through the spray hole 5 carries the fuel into the interior the burner muffle 1 and keeps the space in front of and around the spray hole free from the effects of the flame.

The burner allows a flame gas jet to be generated at a speed that corresponds to a dynamic pressure which is at least 5 to 10 times the buoyancy forces acting on the flame gas jet in the heating room per unit area, and at the same time a stable flow pattern despite the opposing pressure gradients PQ and To achieve PR and to achieve an optimal soot curve. With a combustion output of 100,000 kcal / h and a pre-pressure of the combustion air of 100 mm WS, the following dimensions are maintained:

Case diameter d ₂ = 250 mm

Width of the gap s = 7.5 mm

Inlet diameter of the combustion

air supply d _z = 100 mm

Distance throttle point: housing front wall b ₂ = 62 mm

The passage area of the perforated sheet corresponds to 364 holes, each 4 mm in diameter.

Entry diameter of the burner muffle

Outlet diameter of the burner muffle

Exit diameter of the acceleration nozzle = passage diameter

the aperture

Length of the burner muffle

Accelerator jet length ....

Axial length of the swirl vanes

Spiral angle of air inlet against

the circumferential direction

Thickness of the guide vanes (not shown)

Diameter of the spray hole

ίο If the burner is to be designed for other capacities, then the specified dimensions, but at least the dimensions d _x , D ₁ , D ₂ , L ₁ , L ₂ , b _x and d _s in the ratio of the square root of the throughputs corresponding to the capacities to change.
It is also possible to use the axial swirl vane length έ _1; to change the smallest burner muffle diameter d ₁ and the helix angle β of the air inlet taking into account the compensation rule of the swirl rate. Every such change in one of the mentioned influencing variables must be compensated for by an essentially linearly proportional change in another of the mentioned influencing variables.

With these values, there is a negative pressure in the center of the inlet end of the burner muffle, the 10th mm is 25 to 20 times greater than the mean dynamic pressure of the mm flow in the burner muffle, measured halfway

mm length L _{1 of} the burner muffle at the place of greatest

mm speed of the local speed profile.

This pressure ratio guarantees the stability of the / 5 = 7-15 ° 30 flame flow.

Instead of a conical diaphragm with a cone: j3 = 5 mm base angle α = 30 °, another conicity can also be used

mm or a flat ring aperture can be selected.

D ₁

D ₂ -L ₁ -

L ₂ ■■

A =

1 sheet of drawings

Claims (5)

Claims- 5. burner according to at least one of claims 1 to 4, characterized in that the second 1. Burner for oil, gas or coal dust to the collecting space (17) between the inlet (13) of the Firing a boiler room, with a main swirl device and the spray hole (5) throttle flow direction the throughput opening 5 is conical. ' widening, elongated burner muffle, a ■, '- fuel feed arranged at the inlet end. tion, a radially extending annulus with The invention relates to a burner for Twist blades for supplying combustion oil, gas or coal dust, for firing heating air, one in the area of the fuel supply in the io space, with a spray hole arranged in the main flow direction of the center of the annular space, throughput flow widening conically, elongated to the outlet end of the burner muffle Burner muffle, an acceleration nozzle connected to the inlet end for the ordered fuel supply, a radial flow of flame gases, an annular space to be supplied for combustion air with swirl vanes for supplying a first collecting space in a combustion air chamber that at least partially surrounds the burner 15 in the area of the combustion muffle, Substance feed arranged in the center of the annular space and an acceleration nozzle connected to the first collecting space via a th spray hole, an acceleration nozzle connected to the outlet end of the flow equalization device, burner muffle and the second collecting space, which is connected to the ring space for the flame gases, a combustion air supply space, thereby identifying the burner muffle to a first collecting space inside the burner muffle, that the spray hole (5) also at least partially surrounds the housing, and a housing that is in flow connection with the second collecting space and the first collecting space a flow space (17) is, and the in the following specified equalization device connected to the second spiral angle β, as well as the dimensions 25 related to the outlet through-collecting space, which is related to the annular space in connection with the _{diameter D 1 of} the burner muffle. conditions of the inlet diameter Ci _{1 of} the In a known burner of this type (revue Burner muffle and the axial length O _{1 of} the Swirl Generale de Thermique, June 1963, p. 128) is based on blades, the device taking into account no flow connection between the entry of the swirl sifting of the compensation rule of the swirl rate device and the spray hole. The combustion air supplied to the spray hole by · di ■ β = const, variable 30 comes from a dedicated Inlet diameter of the new air inlet, from the at the first collecting Burner muffle d / D = 05 is independent of the air inlet connected to the room. In- axial length of the swirl blades' bJO, = 0, '17 ^fol 8 ^{e of this} independent air supply as well as because of the Spiral angle of air inlet "' ⁰ ^ ^m properly coordinated against the circumferential direction β = 7-15 ° ³ S is the dimensional relationships of the known burner With this it is very difficult to generate a stable flow and, furthermore, the following constant dimensional image. Specifically, the flow is not a ratio, again based on the outlet, independent of the Reynolds number, so that the diameter D _{1 is} adhered to, but each time a change is made in the line. Exit diameter of 40 must be laid and not simply scaled Accelerator nozzle ........ DJD ₁ = OAS can be changed. Length of the burner muffle ...... LJD ₁ = about 1.4 ^The invention is based on the object of a Length of the acceleration nozzle LJD ₁ = 0.74 Burner of the type described at the beginning Thickness of the swirl vanes SdID ₁ = 0.03 make it a stable one from the Reynolds number Diameter of the spray hole .. d _s / D ₁ = 0.14 «has an independent flow pattern and is in particular the diameter of the housing .... i / ₂ / D, = 1.4 ^for smaller ones, for heating central heating boilers The inlet diameter of the ^od · ^d S '· required combustion performance is suitable Air supply. dJD = 06 '■■ · ■ · ■ · ^and also with "these small combustion outputs supplies a sooty flame. 2. Burner according to claim 1, charac- terized 50 This object is drawn according to the invention in that the flow equalization solves that the spray hole in flow connection device (14) in the annular space (15) between which is with the second plenum, and the im fol burner muffle and the housing is arranged, the indicated spiral angle ß, as well as the twisting blade carrier (7) related to the and that the swirl device (3) has a plate-shaped exit diameter D ₁ of the burner muffle, the external dimensions of which are 55 to the inlet diameter d _x circumference with the housing a throttle point of _{the burner muffle and the axial length A 1 of} the swirl (16) forming an annular gap with a gap width s are placed, taking into account the ratio of "0.09 to U _{1. Siclitigung der} Compensation rule of the rate of swirl 3. Burner according to one of claims 1 and 2, O ₁ · d _x · β = const, variable are characterized in that the comparative 60 _inlet diameter of the ßrennergungseinnchtung (14) as an annular perforated sheet muffle ' dlD = 05 with a passage area corresponding to 364 Lo - _{axial length of the swirl blades} '.' i. " bWi = <U7 brazen, their diameter to d _v in a ratio of 0.05 to the _{helical angle of the} air inlet stands, is trained. . the circumferential direction / J = 7-15 ° 4. Burner according to at least one of claims 65 - 1 to 3, characterized in that a per se known ratio, again based on the outlet aperture (19), is arranged at the outlet and furthermore following constant dimensional end (16) of the burner muffle (1). knife D ₁ are complied with