U.S. patent number 3,602,333 [Application Number 04/871,180] was granted by the patent office on 1971-08-31 for silencer for suction or discharge of fluids under pressure.
This patent grant is currently assigned to Chiyoda Kako Kensetsu Kabushiki Kaisha. Invention is credited to Koichi Hiramatsu, Shunji Kobayashi, Sathihiro Kuwabara, Isao Yoshihara.
United States Patent |
3,602,333 |
Kobayashi , et al. |
August 31, 1971 |
SILENCER FOR SUCTION OR DISCHARGE OF FLUIDS UNDER PRESSURE
Abstract
On the basis of the observation that a fluid under pressure
diffuses in a conical path with a certain divergent angle into a
region of lower pressure, a silencer, through which a noise
generating flow of a fluid is passed, is made up of a combination
of concentric outer, intermediate, and inner shells respectively
having shapes of hollow truncated cones with specific divergent
angles in the discharge direction and provided on both surfaces or
single surfaces thereof with sound absorbing layers of specific
thicknesses.
Inventors: |
Kobayashi; Shunji
(Yokohama-shi, JA), Hiramatsu; Koichi (Tokyo-to,
JA), Yoshihara; Isao (Tokyo-to, JA),
Kuwabara; Sathihiro (Tokyo-to, JA) |
Assignee: |
Chiyoda Kako Kensetsu Kabushiki
Kaisha (Tokyo-to, JA)
|
Family
ID: |
25356880 |
Appl.
No.: |
04/871,180 |
Filed: |
October 15, 1969 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
|
658395 |
Aug 4, 1967 |
3503465 |
Mar 31, 1970 |
|
|
Current U.S.
Class: |
181/252;
415/119 |
Current CPC
Class: |
F01B
31/16 (20130101); F04B 39/0083 (20130101); F02C
7/24 (20130101); F04D 29/664 (20130101) |
Current International
Class: |
F04D
29/66 (20060101); F01B 31/00 (20060101); F01B
31/16 (20060101); F04B 39/00 (20060101); F02C
7/24 (20060101); F04b 039/00 (); F01n 001/10 ();
F01n 007/20 () |
Field of
Search: |
;181/42,46,50,56,60,33.22,33.221 ;415/119 ;417/312 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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601,872 |
|
Aug 1934 |
|
DD |
|
444,206 |
|
Mar 1936 |
|
GB |
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Primary Examiner: Ward, Jr.; Robert S.
Parent Case Text
This application is a division of the previously filed application
for a SILENCER FOR SUCTION OR DISCHARGE OF FLUIDS UNDER PRESSURE,
having Ser. No. 658,395; filed Aug. 4, 1967 which issued as U.S.
Pat. No. 3,503,465 on Mar. 31, 1970.
Claims
What we claim is:
1. A silencer for suction or discharge of a fluid due to a pressure
difference comprising: an inlet pipe for said fluid having the
construction of an increaser pipe; an outer shell made of a rigid
plate material having a sound shielding characteristic, said outer
shell having the shape of a hollow truncated cone with an outwardly
divergent angle and contiguously connected at the small-diameter
end thereof to the inlet pipe, the inner surface of the outer shell
being covered with a sound absorbing layer of a specific thickness;
at least one intermediate shell having the shape of a hollow
truncated cone and supported within and coaxially with the outer
shell by at least one supporting member; and an inner shell
disposed coaxially at the centerline of the outer shell, the
combination of the outer shell, said at least one intermediate
shell, and the inner shell constituting a noise-reducing
mechanism.
2. The silencer as claimed in claim 1 in which each intermediate
shell is covered over the inner and outer surfaces thereof with
respective sound absorbing layers filled with sound absorbing
material.
3. The silencer as claimed in claim 1 in which the inner shell has
a hollow interior space filled with a sound absorbing material
4. The silencer as claimed in claim 1 in which the outer shell,
each intermediate shell, and the inner shell have respective
outwardly divergent angles within the range of from 7.degree. to
33.degree..
5. The silencer as claimed in claim 1 in which the outer,
large-diameter end of the entire silencer is cut off along a plane
at an angle of from 30.degree. to 60.degree. relative to the
silencer centerline.
6. A silencer for an axial flow fan for causing flow of a fluid,
comprising an outer shell and an inner shell disposed within the
outer shell, each shell having the shape of a hollow truncated cone
or pyramid with a divergent angle in the outward, discharge
direction and having sound absorbing material on surfaces thereof
along which said fluid is to flow, said shells being disposed and
supported in respective positions coaxial with said axial flow fan,
the inner shell being a hollow vessel structure closed at the end
thereof in the outward, discharge direction and having an open
opposite end covered by a porous sound absorbing structure, the
outer surface of the inner shell being covered with a sound
absorbing material.
7. A silencer for an axial flow fan having a propeller driven by a
shaft on the upstream side thereof and disposed coaxially within a
cylindrical structure, said silencer comprising, in combination: a
downstream silencer structure disposed coaxially with and
downstream from the propeller and consisting, essentially, in
concentric arrangement,
an outer shell connected at its upstream end to the downstream end
of said cylindrical structure, an inner shell closed at its
downstream end and having an open upstream end covered by a porous
sound absorbing structure, and
at least one intermediate shell disposed between the outer and
inner shells,
each of said shells having the shape of a hollow truncated cone
with a divergent angle in the downstream direction and having sound
absorbing material on surfaces thereof along which said fluid is to
flow; and
an upstream silencer structure disposed coaxially with and upstream
from the propelled and consisting, essentially in concentric
arrangement,
an outer shell connected at its downstream end to the upstream end
of said cylindrical structure,
an inner shell disposed around the propeller shaft, and at least
one intermediate shell disposed between the outer and inner
shells,
each of said shells having the shape of a hollow truncated cone
with a divergent angle in the upstream direction and having sound
absorbing material on surfaces thereof along which said fluid is to
flow.
Description
This invention relates generally to devices known as mufflers or
silencers for reducing noise due to high-velocity flow of fluids.
More particularly, the invention relates to silencers for reducing
excessive and undesirable noise generated in cases wherein a gas
under pressure such as steam or a compressed gas is caused to
undergo sudden expansion, wherein a gas is abruptly aspirated
and/or discharged by means of a fan or blower.
More specifically, the invention contemplates the provision of a
new silencer of the above stated character having the shape of a
hollow cone and producing very little back pressure, thereby to
provide effective suppression means with respect to frequently
occurring noise constituting a public nuisance.
Heretofore, the principal measures generally resorted to for
reducing noise of the character referred to above have been: a) to
separate the noise source from regions where the noise would be
undesirable, b) to provide a sound shielding wall or barrier
between the noise source and the regions where the noise would be
undesirable, and c) to muffle the noise at its source by means of
one or more mufflers or silencers (hereinafter referred to as
silencers).
The above measure a obviously not suitable in an industrial area,
where the population density in high, in already existing plants,
mills, etc., and in similar places where noise reduction is often
most needed. While measure b is substantially effective when the
sound shielding wall structure is appropriately designed, its
installation often entails very high costs.
In most of the silencers known heretofore fore the above measure c,
sound reduction is accomplished principally by ejecting the gas
causing the noise through numerous fine holes and, at the same
time, reducing the gas velocity in a stepwise manner or by causing
the gas to flow through a circuitous or tortuous path to reduce the
gas flow velocity. In each case, since the gas velocity is forcibly
reduced, the pressure loss of the silencer itself, that is, the
back pressure, is disadvantageously excessive.
It is an object of the present invention to overcome the above
described difficulties heretofore accompanying attempts to reduce
noise.
More specifically, an object of the invention is to provide a
silencer of simple and economical organization having high
effectiveness in silencing noise with very low back pressure and
not requiring special materials or special fabrication
techniques.
According to the present invention, briefly summarized, there is
provided a silencer for reducing noise generated by a flow of a
fluid through an opening, the silencer comprising an outer shell of
a configuration lying substantially in and along a surface
corresponding to the outer boundary layer of the fluid flow in free
state which it would assume prior to provision of the silencer and
connected to the opening, the fluid thereby being caused to flow
within the outer shell with or without one or more shell-like guide
members disposed within the outer shell to divide the flow therein
into a plurality of concentric flow paths without appreciably
increased flow resistance and to provide streamline flow without
turbulence, and sound absorbing material lining the surfaces of the
outer shell and guide member or members along the flow paths.
The nature, principle, details, and utility of the invention will
be more clearly apparent from the following detailed description
with respect to preferred embodiments of the invention when read in
conjunction with the accompanying drawings, in which like parts are
designated by like reference numeral and characters.
In the drawings:
FIG. 1 is a diagrammatic representation indicating the state and
behavior of the released gas in the case wherein a gas under
pressure is discharged naturally to a region of low pressure
through a straight tube;
FIG. 2 is a side view, in longitudinal section, showing the basic
form of a silencer according to the invention, in which an outer
shell of the shape of a hollow truncated cone having a certain
outwardly divergent angle is connected to the straight tube shown
in FIG. 1;
FIG. 3 is a side view, in longitudinal section, showing a silencer
similar to that shown in FIG. 2 in which the interior gas flow path
is divided by an inner shell of the shape of a hollow truncated
cone disposed coaxially with the outer shell and having
sound-absorbing layers on the inner and outer surfaces thereof;
FIG. 4 is a perspective view, showing one example of a silencer
according to the invention;
FIG. 5 is a side view, in longitudinal section, of the silencer
shown in FIG. 4;
FIG. 6 is an enlarged, fragmentary view showing the details of one
part of the view shown in FIG. 5;
FIG. 7 is a cross-sectional view taken along the plane indicated by
line VII--VII in FIG. 5;
FIG. 8 is a graphical representation indicating the sound reducing
effect due to a silencer of the invention;
FIG. 9 is a side view, in longitudinal section showing one example
of a known axial flow air fan and indicating the air flow
thereabout during operation;
FIG. 10 is a view similar to FIG. 9 showing an axial flow air fan
provided with one example of a silencer according to the invention
and indicating improved air flow;
FIG. 11 is a view similar to FIG. 10 showing an axial flow air fan
provided with another example of a silencer according to the
invention;
FIG. 12 is a graphical representation indicating a comparison of
characteristics with respect to frequency of noise generated by a
known axial flow air fan and of noise generated by an axial flow
air fan provided with a silencer according to the invention;
and
FIG. 13 is a diagrammatic elevational view showing the essential
parts of the apparatus used for experimental measurements from
which the characteristic curves of FIG. 12 were obtained.
In general, when a body of a gas under a certain first pressure is
released to be discharged in a natural manner through a straight
tube to a region at a second pressure lower than the first
pressure, the gas is diffused in a conical pattern with a jet angle
.alpha. which is determined by the difference between first and
second pressures, this jet angle .alpha. being, in general, between
10.degree. and 40.degree.. As this discharged gas travels away from
the point of discharge, the discharge gas velocity decreases until,
finally, it is dissipated.
A gas discharge of this nature is accompanied by the generation of
excessively loud noise, which is understood to be caused by
turbulence accompanying the gas discharge. More explicitly, a
turbulent gas flow consisting principally of eddies or vortices is
produced by the velocity differences at the interface layer between
the discharged gas stream and the surrounding stationary gas and by
the differences in the velocities at various parts throughout the
discharged gas. The transformation of this turbulent flow into
vibration energy gives rise to the excessively loud noise.
Therefore, a measure for imparting sound reducing effect can be
realized by suppressing as much as possible turbulent flow in the
above mentioned interface layer and within the discharge gas
flow.
The silencer of the present invention, in general, has a principal
outer shell structure of a shape in which the cross-sectional area
of the gas flow path therethrough increases progressively in the
flow direction at a rate such that the resulting divergent angle of
the flow path formed within the shell structure coincides
substantially with the jet angle of the high-pressure gas
determined by the above mentioned pressure difference, the inner
surface of the shell structure, that is, the surface of the
structure to contact the gas to be subjected to noise reduction,
being covered with a sound-absorbing layer.
The principle of the invention will first be considered with
reference to FIG. 1. When a gas under pressure is discharged
through a straight tube 1, it disperses with a jet angle .alpha.,
and the velocity distributions at various cross sections of the
resulting gas flow are as indicated by intermittent-line curves 5.
These velocity gradients within the gas flow progressively decrease
in the flow direction and become zero at a point where the gas
becomes fully mixed and diffused with the atmosphere.
Since the velocity gradient at the interface layer 2 between the
discharged gas flow and the outside air 3 at any cross section is a
maximum, vortices of maximum intensity are present in layer form in
this interface layer 2. The intensity of these vortices decreases
progressively with the distance from the discharge outlet of the
straight tube 1 until it is finally dissipated.
In a silencer according to the invention of basic form as
illustrated in FIG. 2, an outer shell 7 is communicatively
connected at its inner or upstream end to the above mentioned
straight tube 1 and is formed with an outwardly divergent angle. In
the case wherein this divergent angle is caused be equal to the jet
angle .alpha. resulting from the natural discharge of the gas, the
inner surface of the outer shell 7 will coincide with the interface
2 which would exist in the case of natural discharge. Accordingly,
direct contact between the flowing gas and the outside air 3 is
prevented by the presence of the outer shell 7 constituting a
physical barrier therebetween, whereby there is no generation of a
turbulent flow layer due to inductive action of the flowing gas on
the outside air 3.
Thus, generation of noise can be suppressed. Moreover, by thus
providing an outer shell 7 with a divergent angle equal to or close
to the above mentioned jet angle, there is no possibility of
development of a back pressure in the discharged gas.
As the discharged gas flows through the outer shell 7, its velocity
progressively decreases until, at the discharge outlet 8 of the
shell 7 opening to the atmosphere, the velocity is amply reduced,
whereby the noise generated in the region downstream from the
discharge outlet 8 is of very low level.
The velocity gradient at the inner surface of the outer shell 7
existing in the position of the above mentioned interface layer is
still of large magnitude and generates noise of high intensity.
Accordingly, as a noise reducing measure, the entire inner surface
of the shell 7 is covered with a sound absorbing layer 9 made of a
sound absorbing material of a specific thickness, as mentioned
hereinbefore. The sound absorbing layer 9 absorbs most of the noise
generated at the part corresponding to the above mentioned
interface layer and, at the same time, functions also to absorb
noise generated by velocity gradients arising within the discharge
gas stream. The velocity distribution across one cross section of
the silencer interior is indicated in FIG. 2 by intermittent-line
curve 5a constituting an envelope of the velocity components 10-1,
10-2, etc. at that cross section.
The gas flow path within the silencer illustrated in FIG. 2 may be
divided into two concentric flow paths as shown in FIG. 3 by an
inner shell 7a disposed coaxially relative to the outer shell 7 and
covered over the inner and outer surfaces thereof with sound
absorbing layers 9a, 9a. In this case, the gas discharged through
tube 1 is caused to flow in divided flow paths with velocity
distributions as indicated by intermittent-line curves as, for
example, curve 5a-1. Thus, it will be apparent that the resulting
velocity distributions are different from that indicated by curve
5a in FIG. 2, and the absolute velocity differences mutually
between the velocity components 10a -1, 10a -2, etc., are
remarkably reduced. Therefore, the inner shell 7a provides an
increase in the sound absorbing area and, moreover, functions also
to impart a flow straightening effect and to decrease velocity
gradients.
In another embodiment of the invention as illustrated in FIGS. 4,
5, 6, and 7, the silencer shown therein has an outer structure
consisting of an inlet pipe 15 for introducing steam or a
compressed gas (hereinafter referred to as "fluid") and an outer
shell 7 contiguously connected to the discharge end of the inlet
pipe 15 and enclosing and forming a part of a noise silencing
structure. The inlet pipe 15 has a flange 15a at its inlet end for
connection to a pipe line or some item of equipment (not shown)
which the fluid is to be released.
The inlet pipe 15 has the form of an increaser, and the ratio of
the cross-sectional areas at its inlet and outlet is from 1:1 to
1:2. The noise silencing structure is of concentric construction
and comprises a central inner shell 7c, an intermediate shell 7b,
and the outer shell 7, the inner and intermediate shells 7c and 7b
being coaxially supported and secured to the outer shell 7 by
support struts 14, 14. The discharge end 16 of the noise silencing
structure thus constituted is diagonally cut and lies in a plane at
an angle of from 30.degree. to 60.degree. relative to the
longitudinal axis of the structure.
WHile a single intermediate shell 7b and a central inner shell 7c
are shown in the illustrated example, two or more intermediate
shells may be used with or without the central inner shell,
depending on the desired effectiveness of the silencer.
As shown in FIG. 6, the outer shell 7 is a hollow truncated cone
formed from a material of high mechanical strength such as steel
sheet or plate and is covered over its entire inner surface with a
sound absorbing layer 12 of a specific thickness made of a sound
absorbing material such as glass fiber or asbestos. The entire
inner surface of the layer 12 is covered with a retaining layer 13
made of a perforated sheet material to retain and protect the
surface of the sound absorbing layer 12 and to prevent erosion
thereof.
The intermediate shell 7b is similarly a hollow truncated cone
formed from a material such as steel sheet or plate and is covered
over the entire inner and outer surfaces thereof with sound
absorbing layers 12, 12 similar to that of the outer shell 7, which
layers 12, 12 are similarly covered with respective retaining
layers 13, 13.
The inner shell 7c comprises an outer shell 13a of a perforated
sheet material formed into a hollow truncated cone of small taper
and a sound absorbing material 12a filling the interior of the
cone.
As is well known, the discharge end 16 of the silencer cut
diagonally at an angle of from 30.degree. to 6.degree. relative to
the silencer axis as described above causes mutual nullification of
resonance effects of specific frequencies within the silencer
shells, and the increased area of the exit section makes possible
further decrease in the velocity of the fluid at the discharge end.
Moreover, there is no occurrence of reaction due to change of
direction of the fluid flow within the silencer, whereby
directivity can be imparted thereto.
In the silencer of the above described construction, the fluid
under pressure passes through the inlet pipe 15 and flows into the
noise silencing structure. The fluid then proceeds to flow through
this structure to the discharge end as its pressure and velocity
are progressively diminished. During this flow, the fluid is
subjected to the noise silencing effect as described above, whereby
the fluid discharged from the discharge end 16 releases its kinetic
energy, and the noise generated is amply reduced.
The principal dimensions and configuration of the above described
silencer are determined in the following manner. The angle of
divergence of the shells of the silencer are determined within a
range of from 7.degree. to 33.degree., which is from 3.degree. to
10.degree. narrower than the jet angle determined by the
aforementioned pressure difference, that is, from 10.degree. to
40.degree.. The sectional area of the discharge end 16 is so
determined that the fluid discharge velocity at the section will be
less than 60 meters/sec. Furthermore, the length L of the silencer
is also selected in accordance with the required degree of noise
reduction, similarly as in the selection of the number of
intermediate shells and in the decision on whether or not to use an
inner shell.
The noise reducing effectiveness of the silencer according to the
invention is indicated by the results as shown in FIG. 8 of one
instance of actual practice. In this graphical representation,
contour line (A) is one of a family of similar contour lines shown
therebelow each of which is an isophonic contour joining the
respective points of sound pressure levels which noise at various
frequencies impart isophonically to the human ear and is generally
referred to as a noise rating number (NRN) curve. The noise rating
number is generally expressed in terms of the magnitude of the
sound pressure level at a frequency of 1,000 c./s.
In the same FIG. 8, curve (B) is a frequency characteristic curve
of noise emitted from a specific noise source (in this case,
high-pressure steam at a pressure of 10 kg./cm..sup. 2 discharged
into the atmosphere through a 2-inch nozzle at a flowrate of 3
tons/hour), the noise being measured at a position 8 meters
directly in front of the nozzle.
To the nozzle of the above described noise source, a silencer in
accordance with the invention was connected. This silencer
comprised outer, intermediate, and inner shells and had an overall
length of 1.4 meters, an inlet throat diameter of 2 inches, a shell
divergent angle of 6.degree., and a diagonally cut discharge end at
an angle of 45.degree. relative to the silencer axis. Steam was
discharged under the same conditions as in the case when the curve
(B) was obtained, and the resulting noise was measured at the same
position, whereupon completely satisfactory noise-reducing results
as indicated by curve (C) were obtained.
While the invention has been described above with respect to
silencers for fluid discharge, it should be understood that the
present invention can be applied also to silencers for reducing
noise arising from fluid suction or aspiration with the same
facility and effectiveness.
The silencer according to the present invention has the following
advantageous features.
1. Since the flow direction of the fluid does not change, the
pressure loss due to the silencer is very small. Accordingly, when
the silencer is used, for example, for reducing the noise of
discharge of a safety valve, the adjustment of the discharge
pressure of the safety valve is facilitated.
2. Since a reaction force is not produced at the time of fluid
discharge, the construction of the mounting part of the silencer
can be simplified, and the handling of the silencer also is
facilitated.
3. High noise-reducing performance is obtained by a silencer of
simple organization and relatively small overall size.
4. Since the organization is simple, and the overall size is small,
the adaptability of the silencer with respect to the required
degree of noise reduction is excellent.
The silencer of the present invention in various embodiments
thereof has wide applicability, one typical example of which is the
use of the silencer to reduce the noise of an axial flow fan of an
air-cooled heat exchanger, as described below.
With the recent scarcity of water for industrial use in most
industrial areas, there has been a rapid increase in the use of
air-cooled heat exchangers to take the place of formerly used
water-cooled heat exchangers. Since an air-cooled heat exchanger of
this type requires a supply of a large flowrate of air at a
relatively low pressure, an axial flow fan is generally used for
supplying this air. In general, an axial flow fan for this purpose
is of large size with a propeller diameter of the order of from 1.8
to 5 meters and produces an air velocity below 60 meters/sec.
Moreover, the air flow through the fan is such that, on the suction
side, the flow velocity is high at the outer periphery and
decreases toward the center, and vortices are formed in the
vicinity of the rotational axis, whereby a part of the fan driving
power is wasted.
Furthermore, the noise generated by an axial flow fan is as high as
from 90 to 110 phon (average) at a distance equal to the propeller
diameter from the end of the fan casing. Since the frequency
characteristic of this noise is such that a greater part of the
components are of frequencies below 500 c./s., noise reduction is
difficult and, in general, has heretofore been neglected, whereby
this noise has been a source of discomfort to person in the
vicinity of fans of this type and even a source of public
nuisance.
This noise can be reduced in a simple manner by the application of
the silencer of the present invention whereby noise components of
frequencies higher than 200 c./s. which cause discomfort to the
human ear of the noise generated by an axial flow fan of the type
referred to above are reduced without causing any appreciable rise
in the power required for driving the fan.
The causes of noise generated by an axial flow fan may be divided
into the following kinds.
1. Intermittent cutting of air layers by the rotating propeller
blades.
2. Vortices created particularly in the vicinity of the rotational
axis and blade tips.
3. vibration of the propeller blades.
4. Other causes such as vibrations of structural parts.
Noise due to cause 4, above, can be suppressed by a direct measure
such as increasing the rigidity of the structural parts. All of the
causes other than cause 4, however, are due to the basic nature of
construction and operation of the fan, and, therefore, a
supplementary measure such as the installation of a silencer is
more practical and effective.
In one example as illustrated in FIG. 9 of an axial flow fan of the
type referred to above, a propeller 23 fixed to and driven by a
shaft 22 is positioned to rotate within a ring 21 and thereby to
draw air through a nest 30 of a large number of thin tubes, such as
a radiator, through which tubes a fluid is passed and thereby
cooled, and the air thus drawn is discharged to the opposite side
of the propeller, as indicated by arrows. On the discharge side,
vortices as indicated by arrows are formed by differences in the
flow velocities of the flowing air.
As mentioned hereinbefore, when vortices are formed in the vicinity
of the rotational axis, the air flowrate is reduced
correspondingly, whereby the effective air delivery of the fan
decreases, and, consequently, there is a loss of air delivery
power.
One example of a silencer of the invention installed on the
discharge side of the above described axial flow fan as illustrated
in FIG. 10 to overcome the above described difficulties comprises a
silencer outer shell 24 and an inner shell 26. The outer shell 24
is made of steel sheet formed into a truncated cone with an
outwardly divergent angle and covered over its inner surface with a
sound absorbing material such as asbestos or glass fiber of a
specific thickness. Accordingly, the outer shell 24 causes the
dynamic pressure of the fan to be recovered as an effective static
pressure and, moreover, has the effect of reducing the noise.
In the case where the fan diameter is large, or when necessitated
by the required degree of noise suppression, it is possible to
install also an intermediate shell 25 as shown in FIG. 11. The
intermediate shell 25 is made of steel sheet formed into a
truncated cone with an outwardly divergent angle and is covered
over its inner and outer surfaces with a sound absorbing material
of specific thickness. In this case, the intermediate shell 25
functions as a flow straightening guide plate on the discharge side
and also has the effect of absorbing and diminishing noise.
The length l in the axial direction of the outer shell 24 and the
intermediate shell 25 is determined from the relationship of the
frequency range of the noise to be reduced and the velocity of
sound. One or more intermediate shells 25 can be used depending on
the required degree of noise reduction.
The inner shell 26 is made of steel sheet formed into a truncated
cone with an outwardly divergent angle and is closed at its outer
or downstream end by a cover plate 27. The inner and outer surface
of the inner shell 26 and its cover plate 27 are covered with a
sound absorbing material. The inner or upstream end of the inner
shell 26 is covered by a sound absorbing structure consisting of a
combination of a perforate plate 29 and a porous sound absorbing
material.
Thus, the inner shell 26 has a construction which is a modification
of the so-called Helmholtz resonator. Accordingly, a part of the
noise energy is passed through the perforated plate 29 and enters
the interior of the inner shell 26 whereby sounds of certain
frequencies are damped in accordance with the principle of the
Helmholtz resonator, and the sounds of other frequencies are
absorbed and reduced in intensity by the sound absorbing material
covering the inner surface of the inner shell 26.
Furthermore, the upstream and lateral outer surfaces of the inner
shell 26 serve to smooth and straighten the vortices produced in
the vicinity of the propeller axis and, therefore, have the effect
of increasing the fan efficiency. The shape and dimensions of the
inner shell 26 are determined by the frequencies of the noise to be
reduced.
By the above-described outwardly divergent construction, the
silencer according to the invention causes recovery of the fan
dynamic pressure as effective static pressure, and vortices are
eliminated by the position of the inner shell on the silencer axis
thereby to cause an increase in the fan efficiency. Moreover, the
silencer of the invention has high noise-reducing effectiveness due
to the multiplication; in effect, of the noise-reducing effect of
the sound absorbing material of large surface area disposed in the
form of concentric cones coaxially relatively to the silencer axis
and the noise-reducing effect due to the hollow inner shell.
In the reduction of noise through the use of a silencer according
to the invention, the noise-reducing performance of the silencer
can be adjusted in accordance with the requirements by
appropriately selecting factors such as the shape and dimensions of
the inner shell 26, the use of one or more intermediate shells 25,
the number of intermediate shells 25, and the length l of the
shells.
Furthermore, it is possible, as illustrated in FIG. 11, to install
the above-described silencer on the discharge side of the propeller
23 and, in addition, to install another silencer comprising an
outer shell 31, an intermediate shell 32, and an inner shell 33 on
the inlet or suction side of the propeller. In such an
installation, it is necessary that the silencer on the suction side
have an organization capable of reducing noise and a streamlined
configuration such that the silencer parts will not disturb the
flow of air and will not constitute parts imposing unnecessary air
resistance.
The noise-reducing effectiveness of the silencer of the invention
is further indicated by the NRN curves shown in FIG. 12 resulting
from an actual instance of installation of a silencer according to
the invention in a large axial flow fan which was connected to an
air-cooled heat exchanger and had a propeller of 3.6 -meter
diameter rotating at 300 r.p.m. As indicated in FIG. 13, the fan
constituting a noise source S was positioned at a height of 7
meters above the ground level G.L., and the noise emitted therefrom
was measured at a sound reception point P positioned 1 meter above
the ground level at a horizontal distance of 11.5 meters from the
noise source S.
In FIG. 12, curve (E) is the acoustic output curve of the large
axial flow fan and corresponds to NRN-110 Curve (F) indicates the
frequency characteristic values of the noise at the sound reception
point P in the case wherein sound insulation and sound absorption
effects are not considered and, corresponding to NRN-75, indicates
the reduction of curve (E) due to distance. Curve (G) is the NRN
curve corresponding to an allowable value of noise at the sound
reception point P of NRN- 40. Accordingly, in the case of an
allowable noise value of NRN-40, it is necessary to take various
noise-reducing measures before the noise characteristic curve
assumes sound pressure levels below those of the curve (G).
In accordance with the graph shown in FIG. 12, we carried out tests
on the characteristics of the silencer of the invention. Curve (H)
indicates the sound reducing effect due to the provision of a sound
shielding wall 0-0a as shown in FIG. 13. From this result it was
clearly apparent that a measure of this order wherein a small-scale
noise shielding O`Oa was provided was insufficient to reduce the
noise to a value below the above mentioned allowable noise
value.
Then, when a silencer according to the invention was installed on
the discharge side of the large axial flow fan, and measurements
were made at the sound reception point P, it was possible to obtain
results, as expected, as indicated by curve (J). In FIG. 12, the
region with diagonal cross hatching indicates the sound pressure
level values reduced by the silencer of the invention.
It should be understood, of course, that the foregoing disclosure
relates to only preferred embodiments of the invention and that it
is intended to cover all changes and modifications of the examples
of the invention herein chosen or the purposes of the disclosure,
which do not constitute departures from the spirit and scope of the
invention as set forth in the appended claims.
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