U.S. patent number 3,847,534 [Application Number 05/291,350] was granted by the patent office on 1974-11-12 for combustion apparatus.
This patent grant is currently assigned to Mitsubishi Denki Kabushiki Kaisha. Invention is credited to Toshio Ito, Tamotsu Nomaguchi, Masatada Sakai.
United States Patent |
3,847,534 |
Nomaguchi , et al. |
November 12, 1974 |
COMBUSTION APPARATUS
Abstract
Combustion apparatus having a combustion plate separating the
mixing chamber from the combustion chamber, and a plurality of flow
obstacles disposed above some of the flame holes of the combustion
plate whereby a mixture of vaporized fuel and combustion air passed
through the combustion plate is ignited, the collision of the
mixture with the flow obstacles resulting in turbulent flow flame
patterns. In addition, a wire net is disposed between the
combustion plate and the flow obstacles for further dividing the
gas mixture into fine segments, which in conjunction with the flow
obstacles, results in stable combustion.
Inventors: |
Nomaguchi; Tamotsu (Amagasaki,
JA), Sakai; Masatada (Wakayama, JA), Ito;
Toshio (Amagasaki, JA) |
Assignee: |
Mitsubishi Denki Kabushiki
Kaisha (Tokyo, JA)
|
Family
ID: |
26423330 |
Appl.
No.: |
05/291,350 |
Filed: |
September 22, 1972 |
Foreign Application Priority Data
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Oct 18, 1971 [JA] |
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46-82307 |
Nov 27, 1971 [JA] |
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46-95675 |
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Current U.S.
Class: |
431/329; 431/208;
431/210; 431/243; 431/347; 431/353 |
Current CPC
Class: |
F23C
99/00 (20130101); F23C 2700/026 (20130101) |
Current International
Class: |
F23C
99/00 (20060101); F23d 013/14 () |
Field of
Search: |
;431/208,210,211,243,328,329,346,347,353 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Dority, Jr.; Carroll B.
Attorney, Agent or Firm: Oblon, Fisher, Spivak, McClelland
& Maier
Claims
What is claimed as new and desired to be secured by letters patent
of the United States is:
1. Combustion apparatus comprising:
a mixing chamber for mixing combustion air and vaporized fuel;
a combustion chamber for burning said mixture of combustion air and
vaporized fuel;
a combustion plate, having a plurality of substantially evenly
spaced flame holes, disposed between said mixing chamber and said
combustion chamber;
a wire net supported on said combustion plate on the combustion
chamber side thereof; and
a plurality of discrete flow obstacles having a lower substantially
planar surface, being less in number than the number of said flame
holes, and substantially evenly spaced apart in a given plane so as
to be disposed above only some of said flame holes of said
combustion plate to thereby deflect the flow of said gas mixture
which passes through said combustion plate from the flame holes
obstructed by said flow obstacles substantially laterally into the
flow of said gas mixture from flame holes which are unobstructed by
said flow obstacles.
2. Combustion apparatus comprising:
a mixing chamber for mixing combustion air and vaporized fuels;
a combustion chamber for burning said mixture of combustion air and
vaporized fuel;
a combustion plate having a plurality of flame holes disposed
between said mixing chamber and said combustion chamber; and
a plurality of discrete flow obstacles disposed above only some of
said flame holes of said combustion plate whereby said gas mixture
which passes through said combustion plate from flame holes
obstructed by said flow obstacles collides with said flow obstacles
to be deflected substantially laterally into the flow of said gas
mixture from said flame holes which are unobstructed by said flow
obstacles,
wherein said flame holes comprise a first flame hole passage, open
to the rear surface of said combustion plate, having a depth
l.sub.1 and a diameter d.sub.1, and a second flame hole passage,
connected to said first flame hole passage, have a depth l.sub.2
and a diameter d.sub.2 at the front surface of said combustion
plate, wherein d.sub.2 is substantially equal to l.sub.2, d.sub.2
> 1.5d.sub.1, and l.sub.1 = 2d.sub.1.
3. Combustion apparatus as set forth in claim 2, wherein said wire
net has a mesh greater than 10.
4. Combustion apparatus comprising:
a mixing chamber for mixing combustion air and vaporized fuel;
a combustion chamber for burning said mixture of combustion air and
vaporized fuel;
a combustion plate, having a plurality of flame holes, disposed
between said mixing chamber and said combustion chamber, wherein
said flame holes comprise a first flame hole passage, open to the
rear surface of said combustion plate, having a depth l.sub.1 and a
diameter d.sub.1, and a second flame hole passage, connected to
said first flame hole passage, having a depth l.sub.2 and a
diameter d.sub.2 at the front surface of said combustion plate,
wherein d.sub.2 is substantially equal to l.sub.2, d.sub.2 > 1.5
d.sub.1, and l.sub.1 .gtoreq. 2d.sub.1 ; and
a wire net disposed above said combustion plate, said net having a
mesh greater than 10.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates generally to combustion apparatus and
more particularly to an improved combustion apparatus for burning a
mixture of vaporized fuel and combustion air.
2. Description of the Prior Art
When formulating a design for a combustion apparatus burner, it is
necessary to consider those characteristics which will affect flame
blow-out, back fire, the formation of soot, and the generation of
combustion noise. In combustion, the formation of soot increases as
the supply of primary air decreases. Similarly, flame blow-out and
back-fire are dependent upon a proper ratio of primary air to fuel
at the flame holes of the burner, as well as the velocity of the
mixture of fuel and air. When for example, the ratio of primary air
to fuel is one, if the velocity of the mixture at the flame holes
is high, flame blow-out is easily caused, while if the velocity of
the mixture at the flame holes is low, back fire is easily caused.
The higher the ratio of primary air to fuel, the narrower the range
of the velocity of the mixture within which both flame-out and
back-fire will not occur. A conventional burner, such as, for
example, a Bunsen burner, wherein the primary air and the secondary
air are separately used as sources of combustion air, is of
complicated structure. Similarly, the red flame type burner causes
a great deal of soot. Accordingly, in order to simplify the
structure and prevent the formation of soot, various burners were
considered which utilized, as combustion air, the primary air and
an excess of primary air which was more than the theoretically
useable combustion air. Consequently, such conventional burners has
the disadvantage in that they decreased the stability for flame
blow-out or back fire, while large conventional burners had the
added disadvantage of combustion noise.
Furthermore, in the conventional apparatus in which the combustion
conditions are obtained by a complete premixing process, the range
of stable combustion is quite narrow, so that a fluctuation in
shape of the flame could be easily caused, thus resulting in the
creation of a back fire, a low frequency sound, or a flame blow out
phenomenon which was the result of, a change in the output
resistance of an apparatus connected to the combustion apparatus,
such as, for example, a heat-exchanger, or a change in the excess
air coefficient of the combustion air depending upon the
temperature of the environment. Heretofore, in order to overcome
the aforementioned disadvantages and to stabilize the flame, it has
been proposed to finely divide the flame holes of the combustion
plate and to control the combustion air by an air shutter. In said
cases, however, the shape of the flame has been a lamina flow flame
18a, as shown in FIG. 2. Accordingly, it has been hard to obtain a
complete stable combustion because of changes in the air density
caused by a change in the environmental temperature and a
consequent effect upon the resistance at the output side.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the present invention to provide an
improved combustion apparatus which will overcome the disadvantages
noted heretofore.
Another object of the present invention is to provide an improved
combustion apparatus which will provide easy control of the mixture
velocity as well as the combustion reaction velocity.
Still another object of the present invention is to provide an
improved combustion apparatus which will maintain stable combustion
without the formation of soot, flame blow-out, or back-fire.
The foregoing objectives are achieved according to this invention
through the provision of a combustion plate disposed between a
combustion chamber and a mixture chamber, the plate having a
plurality of flame holes over which are disposed a plurality of
flow obstacles, the number of obstacles being less than the number
of holes, thereby covering some and not others. Disposed between
the holes and the obstacles is a wire net which finely divides the
mixture prior to ignition. Issuance of the mixture through the
holes causes collision with the obstacles, resulting in turbulent
flame flow patterns upon ignition. The cross-sectional
configuration of the flame holes may vary, such aiding in the
attainment of stable combustion.
BRIEF DESCRIPTION OF THE DRAWINGS
Various other objects, features and attendant advantages of the
present invention will be more fully appreciated as the same
becomes better understood from the following detailed description
when considered in connection with the accompanying drawings, in
which like reference characters designate like or corresponding
parts throughout the several views, and wherein:
FIG. 1 is a partial sectional view of one embodiment of a
combustion apparatus constructed according to this invention;
FIG. 2 is a schematic view of the shape of the flames formed by
conventional apparatus;
FIG. 3 is a schematic view of the improved shape of the flames by
the combustion apparatus constructed according to this invention;
and
FIGS. 4 and 5 are sectional views of the combustion plate for the
combustion apparatus constructed according to this invention,
showing two embodiments of flame holes.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings, and more particularly to FIG. 1,
thereof, the combustion apparatus comprises an axially located
combustion chamber 1 for burning a gas mixture of vaporized fuel
and combustion air, and a peripherally located heating chamber 1a,
partially surrounding combustion chamber 1, for heating the
combustion air which is supplied to the combustion chamber 1. A
cylindrical wall portion 2 of the combustion chamber 1 has heat
accumulation properties while a vaporizing tube 3, for vaporizing
the liquid fuel by means of the accumulated heat, and a heater 4,
for providing heat to the wall portion 2 at the initiation of the
operation, are located in an upper, radially extending wall portion
of combustion chamber 1. A mixing compartment 5, for mixing the
vaporized fuel, sprayed from a spray nozzle 6, and the combustion
air, passed through the combustion air heating chamber 1a, is
connected to a substantially annular gas mixture passage 7 via an
inlet port 8. An axially located cylinder 9 forms a gas mixture
collector 10 below the combustion chamber 1, a plurality of flow
regulating holes 9a being provided within the bottom wall portion
of cylinder 9 for connecting the gas mixture passage 7 to the gas
mixture collector 10. The mixing chamber thus comprises the mixing
compartment 5, the gas mixture passage 7, and the gas mixture
collector 10.
An outer cylindrical housing 11 separates, in conjunction with the
radially extending wall portion of combustion chamber 1, the
combustion air heating chamber 1a from the gas mixture passage 7.
Furthermore, an axially located combustion plate 12, having a
plurality of cylindrical flame holes 12a, separates the gas mixture
collector 10 from the combustion chamber 1. A wire net 13 is
provided above the combustion plate 12, while a plurality of
discrete, three dimensional type of flow obstacles 14, being of a
number less than that of the flame holes 12a, are mounted upon the
wire net 13, so as to be respectively disposed above only some, but
not all, of the flame holes 12a, the burner for combustion thus
comprising the combustion plate 12, the wire net 13 and the flow
obstacles 14. A radially extending spark plug 15 is provided within
the wall of combustion chamber 1, while an inlet pipe 16 supplies
the vaporized fuel from the vaporizing tube 3 to the spray nozzle 6
which leads into the mixing compartment 5. An inlet pipe 17
similarly supplies combustion air from a blower, not shown in the
drawings, to the heating chamber 1a.
The operation of the combustion apparatus will now be described.
During a specific time before the initiation of combustion, the
heater 4, an oil pump, now shown in the drawing, and the air blower
also not shown in the drawing, are operated so that the wall 2 of
the combustion chamber 1 may accumulate heat by means of heater 4.
Vaporizer tube 3 is likewise heated, and when liquid fuel is
supplied to the vaporizing tube 3 by the oil pump, such is
vaporized by the accumulated heat.
Similarly, combustion air is supplied by means of the inlet 17 to
the combustion air heating chamber 1a, the air then being mixed
within compartment 5 with the vaporized fuel sprayed from the spray
nozzle 6 to result in the gas mixture. The gas mixture is
subsequently passed through the inlet 8 to the gas mixture passage
7 for consequent passage through the flow regulating holes 9a to
the gas mixture collector 10. The gas mixture is then divided at
the flame holes 12a, of the combustion plate 12, and the wire net
13, the mixture then being ignited by the spark plug 15 to initiate
the combustion within the combustion chamber 1.
Referring now to FIG. 3, it will be noted that a part of the gas
mixture passing through the flame holes 12a of the combustion plate
12 collides with the flow obstacles 14 whereby a plurality of
turbulent flow flame patterns 18 are formed. It has been confirmed
that stable combustion can be attained with the combustion
apparatus of the present invention even though the ratio, of excess
air supplied to the theoretical supplied amount of the combustion
air, is 1.0, whereas the air excess ratio of conventional apparatus
was 1.4. In operation, the gas mixture collides with the flow
obstacles 14 so as to produce a negative pressure area around the
flow obstacles 14, whereby the results are turbulent flow
conditions around the flow obstacles 14, the flame, by chemical
reaction, as shown by the arrows, and the concentration of the
ions, is increased and the velocity of flow passing through the
flame holes 12a, as well as the combustion reaction velocity, are
controlled.
Referring now to FIGS. 4 and 5, there is shown, respectively, other
burner embodiments constructed according to this invention. The
flame holes 40 of the combustion plate 120 consist of first flame
hole passages 41 and second flame hole passages 42. The first flame
hole passages 41 are respectively opened to the rear or lower
surface of the combustion plate 120 and each one of the first flame
hole passages has a depth of l.sub.1 and an inner diameter of
d.sub.1. The second flame hole passages 42 are respectively opened
to the front or upper surface of the combustion plate 120 and each
one of the second flame hole passages has a depth of l.sub.2 and an
inner diameter of d.sub.2 , the diameter d.sub.2 being equal to
depth l.sub.2 and wherein the diameter d.sub.2 of the embodiment of
FIG. 4 is constant, whereas, in that embodiment of FIG. 5, d.sub.2
is the maximum diameter of passage 42, the passage being
frusto-conical and therefore tapering downward from diameter
d.sub.2 to diameter d.sub.1 of passage 41.
Still referring to FIGS. 4 and 5, the gas mixture is injected
through the first flame hole passages 41 and the second passages 42
whereby they then collide with the wire net 13 which finely divides
the gas mixture so that fine flames providing a lower noise of
combustion are formed within the area downstream of the wire net
13. When such burners are used, the limit of back fire is dependent
upon the inner diameter d.sub.1 of the first flame hole passage 41.
However, the limit of flame blow-out can be increased, by the
effect of the wire net 13, in addition to the limit defined by the
inner diameters d.sub.1 and d.sub.2 of the first and second flame
hole passages, 41 and 42, respectively.
The second flame hole passages 42 can be used as an expansion area
for the flow of the gas mixture injected from the first flame hole
passages 41. In the structures shown in FIGS. 4 and 5, when d.sub.2
> 1.5 d.sub.1, the flash back region of the gas mixture having
the theoretical mixing rate, can be decreased, to be about
one-third. Similarly, when l.sub.1 .gtoreq. 2 d.sub.1, the unstable
combustion, caused by a change in pressure within the ignition
area, can be avoided so that highly stable combustion can be
attained. It has also been confirmed that the effect of the wire
net can be high when the mesh of the wire net is higher than
10.
It will be noted that in the above embodiments, the cross-section
of the flame holes 40 of the combustion plate 120 is circular in
shape. However, it is not necessary that they be of circular
cross-section, and when they are not the inner diameters d.sub.1
and d.sub.2 can be considered to be equivalent to the corresponding
linear dimensions.
Obviously many modifications and variations of the present
invention are possible in light of the above teachings. It is to be
understood therefore, that within the scope of the appended claims,
the invention may be practiced otherwise than as specifically
described herein.
* * * * *