close

Вход

Забыли?

вход по аккаунту

?

Патент USA US3077741

код для вставки
Feb. 19, 1963
A. N. ADDI‘E ETAL
COMPRESSOR MECHANISM FOR INTERNAL
Filed Nov. 24, 1958
3,077,731
COMBUSTION ENGINES AND THE LIKE
6 Sheets-Sheet l
%
@
Feb. 19, 1963
Filed Nov. 24, 1958
A. N. ADDIE ETAL
3,077,731
COMPRESSOR MECHANISM FOR INTERNAL
COMBUSTION ENGINES AND THE LIKE
6 Sheets-Sheet 2
QM
INVENTORS
a
ATTORNEY
Feb. 19, 1963
A. N. ADDlE ETAL
COMPRESSOR MECHANISM FOR INTERNAL
3,077,731
COMBUSTION ENGINES AND THE LIKE
Filed Nov. 24. 1958
I
6 Sheets-Sheet 3
9%;
INVENTORS
Feb. 19, 1963
Filed Nov. 24. 1958
A. N‘ ADDIE ETAL
COMPRESSOR MECHANISM FOR INTERNAL
COMBUSTION ENGINES AND THE LIKE
3,077,731
6 Sheets-Sheet 4
WK
INVENTORS
ATTOENEY
Feb. 19, 1963-
A. N. ADDIE ETAL
3,077,731
COMPRESSOR MECHANISM FOR INTERNAL
COMBUSTION ENGINES AND THE LIKE
Filed Nov. 24. 1958
6 Sheets-Sheet 5
W.’
1/, I /
/
l
INVENTORS
A TTOENEY
Feb. 19, 1963
Filed Nov. 24. 1958
‘A. N. ADDIE ETAL
COMPRESSOR MECHANISM FOR INTERNAL
COMBUSTION ENGINES AND THE LIKE
3,077,731
s Sheets-Sheet e
IN VENTORS
United States Patent Office
1
3,077,731
Patented Feb. 19, 1953
Z
to supply scavenging and charging air to a two-cycle
3,977,731
engine and which is selectively drivable by the engine
BUSTl?N ENGINEE AND THE LIKE
Albert N. Addie, La Grange Earth, and Brian M. Gal
and an exhaust gas turbine or by the exhaust gas turbine
alone; a silencer de?ning an intake duct connected to the
inlet of the compressor and lined with sound absorbing
material and including a rotatably driven axial flow fan
CQMZPRESSUR MECHANISM FUR INTERNAL GUM
lagher, Downers Grove, 1311., assignors to General Mo
tors Corporation, Detroit, Mich, a corporation of
member and stationary flow de?ecting struts cooperating to
impart limited swirl and pressure to the air ?owing to the
compressor inlet through the duct and to re?ectively
Delaware
Filed Nov. 24, 1958, Ser. No. 776,4.w9
32 Claims. (@l. dd-dZ)
10
This invention relates generally to a compressor mech
anism; more particularly, to a combined or unitary com
pressor mechanism including a centrifugal compressor, an
intake silencing means and/ or a rotary after-cooling heat
dampen the substantially unidirectional, high frequency
sound waves emanating from the compressor inlet; and
an air-to-air aftercooler including a matrix rotatably
driven through the discharge passage of the compressor
and a matrix cooling air passage de?ned in part by the
exchanger; and with regard to certain more speci?c features 15 intake silencer and intersected by an axial ?ow fan com~
of the invention, to such a combined compressor mech
mon to the intake silencer fan member.
anism in combination with and adapted to supply pres
surized charging air to an internal combustion engine
power plant.
is connectable to the atmosphere outside the car body
In this illustrative embodiment, the engine compartment
through a plurality of suitable ?lters and serves as an
In operation, high speed centrifugal compressors gener 20 acoustical capacitance further tending to attenuate the
ate a characteristic noise which normally consists of sound
noises emanating from the compressor inlet, particularly
wave components distributed throughout the audible sound
the lower, more audibly acceptable frequencies which
range spectrum. However, the higher frequency sound
otherwise might not be effectively silenced by the use of
the high frequency intake silencer alone. By connecting
waves, i.e., 5,000 to 20,000 c.p.s., thus generated tend to
dominate this noise and result in the auditory preception
of a relatively high pitch whine. Such a high pitch whine
is, at least, a source of extreme psychological annoyance
and, as both the frequency distribution or quality and the
magnitude or intensity level of the generated noise are
both the compressor inlet and the cooling air inlet of the
aftercooler to the interior of the engine compartment and
discharging the matrix heated cooling air to the atmos
phere outside the car body, the combined unit of the in
vention also serves to ventilate the engine compartment of
generally functions of the speed and capacity of the com 30 the car body thus permitting the engine to operate under
pressor unit, these factors may be combined in certain
more ideal ambient temperature conditions.
installations to achieve a noise level in which is psycho
The foregoing and other objects, advantages and features
logically unbearable, going not only beyond a deafening
of the invention will become apparent from the following
level but even beyond the so-called “threshold of feeling.”
description of the preferred embodiment thereof, having
Sustained exposure to such sounds produces a rapid de 35 reference to the drawings, wherein:
terioration of a person’s hearing ability to a condition of
FIGURE 1 is a side elevational view of a locomotive car
permanent deafness.
body with the engine compartment de?ning portion there
of enlarged and broken away to show the preferred il
Since the pressure discharge of a high speed compressor
lustrative embodiment of the invention and its operational
is generally connected to a sound attenuating pressure
system, the noise generated by such a compressor emanates 4.0 environment in somewhat diagrammatic form;
FIGURE 2 is a view showing the unitary compressor,
primarily from the compressor inlet. The invention thus
silencer and cooler of the preferred embodiment of the
contemplates a compact intake silencer arrangement which
invention in detailed section and showing digrammatically
is capable of damping the sound waves emanating from
the alternate turbine and engine drives of the compressor
the compressor inlet and particularly those higher fre
45 and the proportionate and reduced speed drives of the
quency waves falling Within the above speci?ed range.
ducted fan impeller which is common to the intake
In most compressor installations, a cooler or heat ex
changer is generally required to cool the pressurized air
silencer and the aftercooler;
discharge from the compressor thereby decreasing the
volume and increasing the density of the compressed air.
The invention further contemplates the provision of an
improved structural arrangement of a centrifugal com
pressor and an air-to-air heat exchanger wherein the heat
exchanger is built into and forms a cooperative part of the
compressor unit. The invention still further contemplates
the provision of an improved structural arrangement of a
centrifugal compressor, an intake silencer and a cooler
FIGURE 3 is a transverse sectional view of the com
bined compressor, silencer and cooler unit taken sub
stantially on the line 3——3 of FIGURE 2;
FIGURE 4 is an enlarged sectional view similar to and
showing portions of FIGURE 2 in greater detail;
FiGURE 5 is an enlarged sectional view similar to and
showing portions of FIGURE 3 in greater detail;
FIGURE 6 is another enlarged sectional view similar
to and showing other portions of FIGURE 2 in greater
wherein each component is built into and cooperates to
form a part of a unitary compressor mechanism.
As above de?ned, the combined compressor unit of the
detail;
certain more speci?c features thereof, to the pressure
charging of an internal combustion engine mounted in a
vehicle, such as a locomotive, having a limited engine
and
FIGURE 7 is a development view taken substantially
on the line 7~—7 of FIGURE 6 and shows the angular
invention has particular application to the pressure charg 60 relationship between the blades of the intake silencer and
ing of an internal combustion engine and, with regard to
cooler air fans and their cooperating ?ow de?ecting vanes;
compartment.
Ience, for the purpose of illustrating the
invention, a preferred embodiment thereof is herein il
lustrated and described as applied to a turbocharging sys
tem for a locomotive engine of the two-cycle combustion
ignition type. However, the invention is not considered to
FIGURE 8 is a sectional view similar to a portion of
FIGURE 6 showing a modi?ed form of the invention.
Referring more particularly to FIGURE 1 of the draw
ings, a locomotive car body is indicated generally at 10
and de?nes an engine compartment 12 in which a two
cyole combustion ignition engine 14 is suitably mounted.
The engine 14 is drivingly connected to a generator 16
70 which is operable to supply motive power to the several
be so limited.
In its illustrative embodiment, the invention features the
axle driving traction motors, not shown. The interior
combination of a centrifugal compressor which is adapted
of the engine compartment is connected to the atmosphere
3,077,731
3
4
ontside the locomotive car body through a plurality of
an overrunning drive control mechanism 86 to provide
car body ?lters, a few of which are shown at 18.
Pres
surized scavenging and charging air is supplied to the air
box of the engine 14 by a turbocomprcssor indicated
engine drive of the compressor impeller when the engine
In accordance with certain aspects of the invention, the
turbocompressor mechanism 20 includes a centrifugal
compressor 22 which is adapted to be both turbine and
engine driven, an intake silencer 24, and a rotary air-to
air heat exchanger 26, all cooperating to de?ne a compact
drive is rotating faster than the drive which would other
wise be provided by the turbine.
The drive control mechanism 86 is shown in FIGURE
2 by a conventional symbol representing an‘ overrunning
clutch or brake device wherein rotation of the carrier
and its shaft in the direction of the arrow A providing a
compressor speed taster than that possible with the avail
10 able exhaust gases supplied to the turbine tends to rotate
unitary structure which may be mounted on the accessory
the ring gear 82 in the same rotational direction and
drive or timing gear housing 28 ot the engine and extends
longitudinally therefrom in the compartment space im
or frame member 84.
mediately above the generator.
fected by the exhaust gas driven turbine is faster than
As best seen in FIGURE 2, the centrifugal compressor
22 includes a casing 30 rotatably mounting an impeller
32 and cooperating therewith to de?ne a central intake
chamber 34, and an annular dischargechamber 36. The
inlet and discharge chambers 34 and 36, respectively, are
that which would be provided by the mechanical drive
from the engine, the relative rotation between the carrier
at 20.
effects the braking of the ring gear to the stationary casing
When the compressor drive ef
and the turbine-compressor shaft 46 eiiects the opposite
direction of rotation of the ring gear 82 thus causing drive
control mechanism as to overrun or free wheel relative
interconnected by a plurality of ?ow-inducing, radially 20 to the stationary frame or. casing member 84 thereby
extending passages which are de?ned between the impeller
effectively disconnecting the turbocompressor from its
vanes.
The compressor discharge chamber 36. is em
engine drive.
braced by a ring 38 of circumferentially spaced, curved
The compressor discharge scroll serves to support the
diffuser vanestwhich de?ne a plurality of passages through
combined intake silencer and aftercooler assembly 24, 26
which the velocity of the air- discharged from the periph 25 relative to the compressor casing 30. In the illustrative
cry of the impeller is converted into ?uid pressure in
embodiment the scroll-de?ned discharge chamber 49 is
a well understood manner. Thepressurized air ?owing
[formed between the outer diffuser portion of the com
radiallyv outwardly from the diffuser. 38 passes into an
pressor casing 3%, an inner cylindrical member 46', and
annular discharge chamber or scroll 4%.
An arcuately
an outer annular member 46''.
The member 4d” also
extending opening 42formed in the periphery of the scroll 30 serves to partially form the arcuate ‘discharge opening 42.
40 is connectable to the air box of the engine through the
The cylindrical member 44V extends longitudinally from
rotary air-to-air heat exchanger 26 and two impingement
the diffuser portion of the compressor casing and is spaced
typeair ?lters indicated at 44.
concentrically of the compressor inlet. The member lltl"
Thecompressor impeller 32 is mounted on one end of
embraces the member 40' and is secured thereto adjacent
‘a hollow shaft 46 which may be integral with the hub of 35 its end opposite the diffuser and, except for its discharge
an axial ?ow turbine wheel 48, projecting therefrom in
opening de?ning portion, extends longitudinally there
opposite directions, as shown. The exhaust gases of
from to the compressor casing radially outwardly of the
the engine 14 ?ow through an exhaust manifold 50
diiiuser outlet to partially de?ne the discharge chamber
extending longitudinally of the engine to a turbine inlet
46. As best seen in FIGURE 3, this chamber-de?ning
scroll 52which is connected thereto at its turbine-adjacent 40 portion of the member 40" extends through an angle or‘
end. The exhaust gases supplied to the inlet scroll 52‘
approximately 240° and terminates adjacent its discharge
are directed through a nozzle ring 54 against the blades
opening de?ning portion. This last-mentioned portionv
56 of the turbine wheel thereby driving the turbine. The
of the member 40” is ?ared longitudinally away from its
exhaust gases discharge from the turbine wheel through
chamber-de?ning portion.
an‘ annular exhaust diffuser. 58 into an annular discharge
chamber or scroll 60. The discharge scroll 60 is in turn
connected to the atmosphere outside the locomotive car
body by a suitable exhaust stack 62. The turbine 4-8 is
A frusto-conical spider member 90 extends longi
tudinally and radially outwardly from the end of the
cylindrical scroll member 4t)’, being nested with and
secured outwardly to the last-mentioned portion of the
thus operable to drive the compressor in accordance with
member 4t)"; The spider E90 serves as an intermediate
thesupply of engine exhaust gases thereto.
50 support member for the aftercooler 26 and has a plurality
To provide su?icient pressurized air for scavenging and
of arcuately extending ports 96’ extending therethrough.
charging the. two~cycle engine 14 during periods of low
The ports git’ subtcnd the major portion OLE‘ the spider
speed» engine operation and engine acceleration, the turbo
and are de?ned by struts of limited angular width which
compressor unit 22 is preferably provided with a mechan
extend between the ?anged ends of the spider.
ical drive 66 intermediate the engine and the compressor 65 The aftercooler 26 includes an outer casing 92 which
which includes an overrunning drive control means oper
able to drivingly connect the compressor to the engine
Whenever the mechanical engine drive is being driven
cooperates with the structure of the intake silencer 24
to de?ne a cooling air duct 94»; a cylindrical air-to-air
heat exchanging matrix 96 which is rotatably mounted
taster than the turbine and operable to disconnect the
and sealed with respect to the casing 92 to require heat
compressor. from the engine whenever the turbine is 60 exchanging air ?ow therethrough; and an axial ?ow fan
being rotatably driven by the exhaust gases at a rate faster
98‘which is operable to induce the flow of cooling air
than would be provided by the mechanical drive.
through the matrix and the cooling air duct 9'4.
The mechanical drive 66 includes an external gear 64
The aftercooler casing 92 includes an annular end
which is formed adjacent the end of the hollow shaft 46
plate 190 which extends radially outwardly from the pe
opposite the compressor.
The gear. 64 serves as the sun 65 riphery of the compressor casing.
gear of a planetary gear set.
The sun gear 64 meshes
A second annular
plate 102 extends radially outwardly of the spider 90
with a plurality of equi-angularly spaced planetary gears
in parallel relation to the plate 100. The outer peripheries
68. which are rotatably supported at 72 by a planetary
of these plates are of identical con?guration. As best
carrier 70. A stub shaft 76 integral with the planetary
seen in FIGURE 3, the upper portion of each of these
carrier‘70 is suitably journaled, as indicated at 74, in the 70 plates is partially de?ned by an arcuate surface which is
turbocompressor casing. A driving gear 78 secured to
vformed on a radius R1 about the axis of the compressor
the carrier shaft '7 6 meshes with and is driven by an engine
and subtends an angle slightly less than that subtended
driven accesory drive gear 80. The planetary gears 68
by the discharge chamber forming portion of the scroll
mesh with a ring gear 82 which. is rotatably mounted in‘
member 40'’. Two ?at surfaces extend tangentially from
the rturbocornpressor. casing, and connectable thereto by 76 the opposite ends of this arcuate surface and intersect
3,077,731
5
a second arcuate surface which is formed on a radius
R2 about the axis of the generator 16. This con?gura
tion of the lower portion of each plate permits the com
pact, relatively close radially spaced mounting of these
plates, and thus of the aftercooler, immediately above the
generator housing while providing relatively large open
ings for the ?ow of the cooled pressurized air from the
aftercooler to the inlet passages of the ?anking impinge
6
of the drum for each provided with external gear teeth
indicated at 146. These gear teeth drivingly engage the
mating gear teeth of two pinion gears 148 which are
secured to an engine-driven shaft 15% in longitudinally
spaced relation to each other. A suitable driving con
ection between the pinion drive shaft 15% and the en
gine-driven accessory drive gear 82'} is indicated diagram
matically in FXGURE 2 by the line 152 extending be~
ment filters 44. In this connection, it will be noted that
tween these gears.
these tangential surfaces are radial to the generator axis, 10
The longitudinal ends of the matrix drum are sealed
and de?ne planes which are symmetrical with respect to
with respect to the casing plates Tilt) and 162 by seals
a vertical plane common to the axes of both the turbo
154 extending therebetween. As best seen in FIGURE
charger and generator.
4, each of the seals 154} includes a seal ring 155 of a
As shown in FIGURE 3, two angled members 1M
suitable material, such as Te?on, which is heat resistant
and 1% constitute frame members extending intermedi
and capable of being biased into nonlubricated rotative
ate the lower portions of the casing plates The and M2.
sealing contact with the adjacent radially extending face
Each of these members has a major leg portion M’ and
of one of the matrix end plates 14%. The relatively
1%’, respectively, which is outwardly coextensive with
?exible seal ring 155 is preferably backed by a rela
the corresponding, longitudinally aligned tangential sur
tively more rigid metal ring T56 and an annular ?exible
faces of the plates 1% and M2. The legs led’ and tilt’
diaphragm seal member 157 is interposed between the
de?ne outlet ports 1% and 167, respectively, which are
backing ring and the adjacent casing plate. The dia
suitably connectable to the ?anged inlet ducts of the sym
phragm seal 157 is preferably made of a highly heat
metrically arranged impingement ?lters, as indicated at
resistant ?exible material, such as silicon rubber, and may
Tilt} and 116, respectively. The bottom of the casing
be fabric reinforced. The seal ring 1155, the backing ring
92 intermediate the plates 1% and 1102 and the port
156 and the adjacent end of the ?exible diaphragm mem
de?ning legs of the members 1% and 1% is closed by
ber 1557 may be secured together in any suitable man—
a plate lldll which extends longitudinally between and
ner, such as by a plurality of equiangularly spaced rivets
conforms to the lower arcuately de?ned peripheral sur
as indicated at 158. The opposite end of the ?exible
faces of the plates Hill and 162. The upper portion of
diaphragm member is somewhat similarly secured to the
the aftercooler casing between the plates Tilt} and it}?! 30 adjacent casing plate by suitable but detachable means,
is embraced by a perforated cooling air intake screen
such as a plurality of equiangularly spaced nuts and bolts
103 which extends arcuately between the upper ends of
as indicated at
The longitudinal movement of the
the members lib-l and res and longitudinally between
seal and backing rings it'd and 155 relative to the cas
the plates lltlil and 1&2 and is suitably secured to the
ing plates 1% and Th2 and the matrix end plates Mt}
several casing members.
The minor legs 104-” and 1656" of the members lit-ll
and res, respectively, extend radially inwardly toward
the common rotative axis of the several elements of the
combined turbocharger unit from the upper end of the
major legs 104' and res’. As best seen in FIGURES
3 and 5, the longitudinally disposed ends of these radi
ally extending minor legs NM” and ice" are each pro
vided immediately adjacent the casing plates 1% and
T02 with bosses or lugs M2 and 114, respectively, which
extend laterally and downwardly therefrom. These
paired bosses 112 and ltd support the opposite ends of
shafts T16 and 118, respectively, upon which cylindrical
guide rollers 12d and 122, respectively, are suitably jour
naled. The guide rollers 12% and 122 in turn rotatably
support or cradle the cylindrical heat exchanging matrix
is guided by a plurality of equiangularly spaced pins
res. The pins see are carried by and project axially
from the backing ring and are telescopically and guid
ingly embraced by the adjacent ends of hollow cylin
drical pins 162 which are carried by the casing plate.
Each of the hollow pins 152 is closed at its opposite end
and a relatively light spring 163 is compressively inter
posed in its hollow portion between its closed end and
the backing-ring-carried pin 16% projecting therein. The
springs 153 thus serve to bias the backing ring and the
‘
seal ring carried thereby into relatively light rotative
sealing engagement with the axial face of the adjacent
matrix end plate Mil.
In addition to its guide roller supporting function, each
of the minor legs 1%" and Hi5” of the members 1-34
50 and 1% forms a radially extending partition wall and
carries a radially adjustable close clearance seal 166 and
The matrix drum 96 is also rotatably supported in
168, respectively, which seals its supporting partition
ternally by longitudinally extending guide rollers 124 and
wall with respect to the external surface of the matrix.
126 which engage its inner surface opposite the rollers
llil and T22, respectively. The inner guide rollers T24
and 126 are suitably journaled on shafts
and 13%,
respectively, which are supported at their opposite ends
The guide roller supporting partition members 136 and
133 similarly carry radially adjustable close clearance
seals 17%) and 172, respectively, which seal their respec
tive partition members with respect to the inner surface
by paired bosses or lugs 132 and 1354, respectively. These
bosses extend laterally and downwardly in parallel spaced
of the matrix. it will thus be seen that the several parti
tion de?ning members and the several seals divide the
casing intermediate the plates 1% and 162 into an air
heating or matrix-cooling chamber 174 and an air-cooling
or matrix-heating chamber T76.
The close clearance seals 16%, 179 and 172 are sub
stantially identical with the close clearance seal 166 which
is shown in enlarged detail in FIGURE 5. Each of these
close clearance seals comprises a channel-shaped member
llliti which is carried by and extends longitudinally of the
partition portion of the member lild between the roller
relation to the bosses 112 and 114, respectively, from par
tition members 136 and 138 which extend longitudinally
between the casing plates Tilt} and N2 in radial align
ment with the legs ill/s" and res", respectively.
As rotatably mounted by the guide rollers 12%), 122,
124 and 126, the matrix drum 96 spacedly embraces the
compressor discharge scroll 4b‘ and the spider 9d‘ and ro—
tatably passes the arcuate discharge opening 42. The
matrix drum comprises two annular end plates Mill and
a plurality of radial plates or strips 142 (see FIGURE
3) which extend longitudinally therebetween. The spaces
intermediate the end plates lit-(l and the strips 142 are
packed with a suitable porous heat exchanging material
indicated at 144, such as a woven or spun metal gauze,
and de?ne a plurality of substantially radial heat exchang
ing air ?ow passages therethrough. The end plates Mil
supporting lugs 112. The channel de?ning side walls of
the member 18%‘ slidably mount a longitudinally extend
ing T-shaped seal pad 182 which is radially adjustable
by four screws 184}, two adjacent each end thereof, to
vary the radial clearance between the matrix and its
clearance—der'ining surface. Each of the screws 1554 is
provided with a reduced diameter portion 184' thread-v
answer
ableinto the cam pad member with one hand of rotation
and a larger threaded portion 184" which is threadable
wise emanate from the compressor inlet, the intake
silencer 24 is preferably a multistage silencing device par
through the channel~shaped member with the opposite
ticularly adapted for dampening or silencing of the
extremely unpleasant higher frequency sound waves char
cteristic of such high speed centrifugal compressors.
hand of rotation.
Due to the use of threads of opposite
hands adjacent the opposite ends of the screws 184,
In addition to the duct de?ning sections 226 and 228,
the intake silencer 24 includes several other duct de?ning
sections 236, 238 and 240. These sections are coaxially
aligned with the compressor and its inlet and cooperate
ing such clearance adjustments, the larger channel
engaging ends of the screws 184 are each provided with 10 to de?ne an intake duct 242 of annular cross-section
converging toward and connecting the inlet chamber of
sockets, as shown at 186, which are adapted to receive
the compressor to the interior of the vehicle compart
hexagonal wrench members of the Allen type.
ment 12. The fan member 98 intersects the intake duct
The outer duct de?ning casing 92 of the aftercooler 26
242 and divides it into a ?rst portion 242' de?ned between
further comprises a cylindrical member 1% which is
rotation of these screws in opposite directions effects
alternate variations in the radial clearances intermediate
the matrix and the cam pad. For the purpose of eifect
supported by and extends longitudinally from the ?anged 15 the sections 226 and 236 and a second portion 242"
outer end of the spider member 99. The member 1%
converges frusto-conically inwardly to the cylindrical
de?ned between the sections 228, 238 and 240.
The fan member is perforated to de?ne a plurality of
axial ?ow inducing fan blades 252. These blades extend
throat portion 190’ of constant diameter. This constant
radially between the fan rim 221 and the impeller hub
diameter throat portion embraces the axial flow fan Sit;
and cooperates with the portions of the intake silencer 24 20 254- and, as best seen in the development of FIGURE 7,
are inclined to induce air ?ow axially in the intake duct
which it spacedly embraces to de?ne an annular duct of
toward the compressor inlet. The cooling air fan blades
constant dimension through the fan 98. The throat end
229 are of course oppositely inclined to effect air ?ow
of the member 196 mates coaxially with a second cylin
in the opposite direction in the cooling air duct 94. The
drical duct member 192 and is connected thereto by a
resilient coupling indicated at 194. The duct member 25 fan impeller @d is supported and driven by a shaft 256
which is journaled immediately adjacent its fan end in
192 is secured at its opposite end by suitable means to
a bearing 25$. As shown in FIGURE 6, the bearing
a. discharge header 1%. The header 1% de?nes an
258 is supported by the silencer section 228 through a
upwardly extending duct or opening 198 which is con
plurality of stationary de?ector vanes 260 which depend
nected by a resilient coupling 202 to an exhaust stack
200. The exhaust stack 2% is mounted in the car body 30 radially inwardly from its fan adjacent end and terminate
and extends to the atmosphere outside the engine com
partment. The end of the header member 1% opposite
its connection to the member 192 is provided with an
opening 264 which embraces and supports an air inlet
assembly 2106.
The inlet assembly 206 forms a part of the intake
silencer 24- and supports the adjacent end of an intake
duct de?ning section 226 of the silencer. This inlet
assembly comprises a cylindrical member 2% which is
in a bearing supporting rim, or hub 262. The vanes 260
cooperate with the fan blades to impart a limited helical
swirl to the air ?owing to the compressor inlet. This
swirl is preferably complementary to the con?guration of
35 the vane-de?ned radial passages of the compressor im
peller and provides a reduced inducer angle of attack
for the air entering the compressor at all fan and com
pressor speeds thereby increasing the range and capacity
of the compressor.
embraced by and supported in the header opening 204.
The opposite end of the shaft 256 is splined, as in
The member 203 in turn telescopically embraces and
dicated at 264, to the end of a quill shaft 266. The quill
shaft 2&6 extends through the hollow turbine drive shaft
45 and its distal end is drivin‘gly splined, as indicated at
268, to the stub shaft 76 of the engine driven planetary
the'flanged end of the member 208 and a mating ?ange
formed on the adjacent end of an annular intake bell 45 carrier ‘7%. The shaft 265 is journaled by a bearing 270
supports the adjacent end of the silencer section 226.
An annular air intake screen 210 is sandwiched between
212 and extends radially inwardly therefrom.
A plurality of de?ector blades 216 and 218 extend
radially of the throat portion of the fan duct and respec
immediately adjacent its splined connection to the shaft
256. The bearing 279 is mounted in an inlet hub portion
3%’ of the compressor casing, This hub portion is in turn
supported and centered in the compressor inlet chamber
tively serve to introduce the air de?ectively into and to
receive the air discharged from the blades 22% of the 50 34 by a plurality of equiangularly spaced radial struts
39" which extend between the hub and the outer inlet
cooling air fan 98 in a well known manner. The blades
de?ning portion of the compressor casing. A cap 272
220 of the fan member 98 are rooted in an annular rim
secured to the end of the inlet hub 30’ retains the bearing
221 which extends intermediate the cooling air duct 94
276 in its mounted position and carries a rotary shaft
and the silencer de?ned intake duct. The discharge
seal 274 which sealingly embraces the splined end of the
de?ecting blades 218 are carried by and extend radially
shaft 256. The bearing assembly 276 is sealed with re
inwardly. from the duct de?ning member 190 to an inner
ring 222. The ring 222 carries a seal ring 22d which
spect to the compressor inlet by a rotary shaft seal 276
cooperates with the fan rim 221 to provide a labyrinth
interposed between the inlet hub and the shaft 266 and
seal 225 therebetween. The ring 222 also telescopically
by a pressurized air seal 278. Pressurized air for the
supports the adjacent end of the intake silencer duct sec 60 air seal 273 is delivered thereto from the compressor out
tion 226 which extends longitudinally therefrom to its
let chamber 36 by a bleed passage 286} which is formed
inlet end which, as mentioned above, is supported by the
in the compressor casing and extends to the air seal
cylindrical member 294 of the air inlet assembly.
through one of the radial struts 39".
_ A second intake duct de?ning section 2280f the silencer
The several duct de?ning sections of the silencer 24
24 is supported by the coaligned adjacent ?anges of the 65 also de?ne a plurality of sound attenuating chambers
scroll member 40’ and of the frusto-conical spider 9t} and
which are connected to the intake duct. The sections
extends longitudinally therefrom to a point immediately
226, 228, 236 and 233 are each in the form of canisters
adjacent the fan rim 221. The fan adjacent end of the
of toroidal con?guration and de?ne sound attenuating
section 228 carries a ring 230 which in turn mounts the
chambers which are preferably packed with a suitable
several fan inlet de?ector blades or vanes 216. The 70 porous, sound absorbing material, such as steel wool or
de?ector ring 230 also mounts a seal ring 232 which
spun glass, as indicated at 226', 228', 236' and 233’, re
cooperates with the fan rim 221 to provide a multiple
spectively. The duct de?ning walls of these sections are
labyrinth seal 234 therebetween.
suitably perforated as indicated at 226", 228", 236" and
Due to the complex nature and high level of noise
238".
which is generated by the compressor and would other 75
The sections 226 and 236 are both of constant radial
9..
3,077,731
Th
dimensions and are concentrically spaced with the inner
section 236 being supported relative to the outer section
226 by a plurality of straps 244- and 246 which extend
radially therebetween adjacent their ends. The inlet por
tion 242’ of the silencer de?ned intake duct 242 is thus
of constant annular cross-section.
The end of the sec
tion 236 adjacent the air inlet assembly 2% is provided
the pressure rise effected by these intake fan blades is
preferably restricted to less than one inch of Water at the
compressor inlet thus minimizing the driving power ab
sorbed thereby. In addition to providing this limited ?rst
stage of compression, the fan blades 2E2 serve as a driv
ing connection intermediate the fan hub 254 and the outer
fan rim and blades 221 and 220, respectively. In cooper
with a hemispherical closure cap 248. This cap is tele
scopically embraced by the air inlet screen 216 and co
ation with the air ?ow de?ecting vanes sea, the fan blades
252 also impart a helical swirl into the air ?owing to the
operates with the air inlet bell 212, which is radially 10 compressor inlet. This fan induced swirl varies with driv
ing speed of the shaft 256 and tends to be complementary
spaced therefrom, to de?ne an annular air inlet 250 of
converging con?guration. The opposite end of the sec
to the radial passages de?ned by the impeller vanes 32
providing means for substantially reducing inducer angle
tion can is mounted in limited spaced relation to the im-i
peiler hub 254 and cooperates therewith to de?ne a cen
of attack at all engine and compressor speeds. Such re
tral sound attenuating chamber 282 connected to the
duction of angle of attack increases the ?ow range or
intake duct M2 immediately adjacent the roots of the
capacity of the compressor. As explained in somewhat
blades 252 through the limited annular clearance 234
greater detail below, the fan blades 252 also cooperate
therebetween.
with the stationary vanes ass to re?ectively and de?ec
tively dampen the substantially unidirectional high fre
The silencer sections 228, 238 and 240 which de?ne
the intake duct portion 242" intermediate the fan and the 20 quency sound waves emanating from the compressor in
let.
compressor inlet are of frusto-conical longitudinal con
?guration and cooperate to provide convergence of this
The air discharged from the compressor passes through
the diffuser 38 into the compressor discharge scroll 40.
portion of the intake duct from the fan to the compressor
It then passes through the rotating matrix 96 in the air
inlet. The section 244) extends between the section 223
and the compressor inlet and provides a duct de?ning sur 25 cooling chamber 175, transferring a portion of the com
pression induced heat from the pressurized air to the
face coextensive with that of the section 228. The inner
duct de?ning section 238 is supported at its fan adjacent
matrix. After passing through the matrix, the relatively
cool pressurized air is delivered through the impingement
end by the bearing supporting rim 262 and at its compres
?lters
to the engine air box. As the heated matrix
sor end by the bearing retaining cap 272. The chamber
rotates through the matrix cooling chamber 174, the heat
23S’ de?ned within the section 238 and thus the sound
imparted to the matrix by the pressurized air is transferred
absorbent packing therein is of constant radial dimension
to the cooling air ?ow induced by the axial ?ow fan 93
throughout its length although the area thereof presented
thus cooling the matrix 96. The cooling air heated by
to the intake passage progressively increases away from
the matrix passes through the fan $8 and is then dis
the compressor inlet. The chamber 228’ is of trapezoidal
charged outside the car body through the exhaust stack
frusto-conical longitudinal cross-section with divergence
2%.
of its radial dimension toward the compressor inlet thus
progressively increasing the depth of the sound absorbent
As indicated above, the high frequency sound Waves
generated by the compressor impeller are substantially
material packed therein as presented to the intake duct.
unidirectional and highly echoic. In passing outwardly
A conical chamber 286 is formed centrally of the section
238. This chamber may be connected to the intake duct 40 of the annular intake duct, a portion of such waves ini
tially strikes the duct de?ning surfaces of the silencer
by a series of perforations 288 immediately adjacent its
section 238, being partially absorbed by the packing ma
fan adjacent end to form another sound attenuating
terial 238' and partially de?ected thereby toward the
chamber. A similar sound attenuating chamber may be
sound absorbing sections 226 and 228. A second portion
provided by connecting the intake duct through a plu
of the high frequency sound waves emanating from the
rality of perforations indicated at 292 to a chamber 290
de?ned between the cylindrical scroll member an’, the 45 compressor inlet are directed toward the duct de?ning
surfaces of the silencer sections 226 and 228, being
compressor housing, the duct de?ning section 24%) and
similarly partially absorbed by the packing material of
the adjacent end of the section 228.
such sections and partially de?ecting therefrom. A third
In a typical application of the above-described unitary
turbo-compressor, heat exchanger, and air intake silencer, 50 portion of the compressor generated high frequency uni
directional waves are directed longitudinally of the intake
the accessory drive or timing gear train of the engine 14
duct and, in the absence of the sound re?ection and de
is such that the planetary carrier shaft "76 is driven at ap
?ection cooperation of the fan and stationary vanes 252
proximately 2,800 rpm. at a maximum engine speed of
and 269, respectively, would normally pass outwardly
900 rpm. The drive ratio of the auxiliary gear drive
152 is such that the matrix 536 is driven at a speed of ap— 55 of the silencer unit without possible de?ection and ab
sorption by the duct de?ning surfaces and chambers of
proximately 70 rpm. at the maximum rated engine speed.
the several silencer sections. The fan blades 252 are
in the absence of exhaust gases su?icient to overdrive the
of a con?guration and equi-angularly spaced so that sub
turbine relative to the mechanical drive, as during engine
stantially all of the higher frequency sound waves reach~
starting or accelerating periods, the accessory drive gear
train of the engine will partially drive the compressor 60 ing the intake fan area, either directly from the com
ressor inlet or by de?ection, are de?ected by the fan
impeller 32 through the planetary gear set providing a
blades. The sound waves de?ected by the fan blades
maximum engine driven compressor speed of approxi
are directed toward the adjacent sound absorbing sur
mately 16,230 rpm. at the maximum rated engine speed.
faces
and chambers of the several silencer sections. A
However, as the engine load and speed increases, the
exhaust gases from the engine will progressively increase 65 portion of the sound waves de?ected by the fan are
further de?ected by the stationary vanes 26!) to be effec
until the turbine overdrives the mechanical drive 66. As.
tively re?ected back to the compressor inlet in out-of
the engine approaches full load and speed operation, the
phase relation thereby effectively dampening the sound
exhaust gases will normally be su?icient to drive the
waves emanating therefrom.
turboco-mpressor at a speed of 19,000 to 20,000 rpm.
From the foregoing description of the operation of the
In operation, air is drawn into the engine compartment 70
intake silencer, it will be seen that this intake silencer
12 through the several car body ?lters 18 by the combined
suctions of the compressor 22 and the axial ?ow fan 93..
As indicated above, the intake fan blades 252 serve as a
24 is primarily anechoic being designed to re?ectively
and de?ectively dampen the higher frequency sound waves
limited ?rst stage of compression inducing air ?ow in
emanating from the compressor inlet. However, a sub
the intake duct toward the compressor inlet. However, 75 stantial portion of the lower frequency sound waves
3,077,731.
11
12
generated by the compressor as well as a limited por
and scope of the invention as de?ned in the following
claims.
tion of the higher frequency sounds are also attenuated
by the acoustical capacitance provided by the chambers
282, 286 and 2%. Any sound Waves passing outwardly
of the silencer intake duct 242, and particularly the
lower frequency waves, are further attenuated by the
acoustical capacitance provided by the engine compart
We claim:
.
1. In combination, a housing member having an en
gine compartment therein, an internal combustion en
gine mounted in said compartment, ?lter means con
necting the interior of said compartment to the atmos
ment 12.
phere outside the compartment, means for supplying pres~
,In certain installations requiring a higher degree of
surized charging air to said engine including a casing,
noise abatement or where space limitations require the 10 a compressor rotatably mounted within said casing, said
intake duct de?ning silencer sections to be of less than
compressor having an inlet connectable to the interior
optimum sound absorbing length or capacity, further
anechoic silencing of the compressor generated high fre
of said engine mounting compartment and a discharge
connectable to said engine, said compartment and ?lter
quency sound waves may be desirable. As shown in
means de?ning acoustical impedance means operable to
FIGURE 8, an additional stage of anechoic silencing 15 damp the sound waves generated by and emanating from
may be provided in such installations by a silencer as
said compressor and said engine constituting a high fre
sembly 3% including an anechoic target ba?‘le 302 spaced
quency sound attenuating means connected to said com
axially of the intake duct nozzle bell 2-12 and an annular
pressor discharge, turbine means operable to rotatively
drive said‘ compressor at a relatively high speed in no
directionalizing ba?le 3124 which spacedly embraces the
outer periphery of the intake bell and the anechoic target 20 cordance with engine exhaust gases, supplied thereto,
The target ba?le 36-2 comprises a plurality of plates 308
which are mounted in spaced parallel relation trans
versely of a circular mounting plate 396 and extend lon
gitudinally therefrom toward the intake bell. A cylin~ 25
manifold‘ means for supplying engine exhaust gases to
said- turbine means. and therefrom to the atmosphere
outside the compartment, mechanical drive means inter
mediate the engine and the compressor and including
overrunning. means operable‘ to drivingly’ connect said
drical member 310 is- secured to the periphery of the
compressor to said engine under low exhaust gas supply
plate 3% and de?nes a. wall embracing the parallel plates
conditions to said turbine, said; drive‘ means being oper
3% which are- of varying lengths limited to the chordal
able to disconnect said compressor from said engine
dimensions imposed by the mounting plate 306 and the
whenever said turbine means is rotatably driven faster
wall member 319. The plates 3% are tapered away 30 than said‘ mechanical drive means, whereby said com
from the mounting plate to provide a plurality of sound
pressor is partially engine driven when said mechanical‘
de?ective surfaces or wedges which are covered with
drive means is being driven faster than said turbine,
suitablevsound absorbing material 312 such as spun glass
means and said turbine drive means is permitted to over
blanket type insulation. The exposed surfaces 314 of
run said mechanical drive means whenever said turbine.
the spun glass blanket material lining the plates 308 35 drive means is being driven faster than said mechanical
are preferably spray coated with a thin vinyl ?lm inter‘
drive means, high frequency silencer means associated
locking the exposed glass ?bers to, prevent erosion by
with the inlet of said compressor and de?ning an annular
the intake air ?ow. Wire cloth screening 316 may also
intake duct, converging toward and connecting the inlet
be used to provide additional erosion protection of the
of said compressor to the interior of said compartment,
The annular directionalizing ba?cle 304 cooperates with
40 at ?rst fan means intersecting said silencer duct and oper
able to impart limited pressure and swirl to the air ?ow
the cylindrical wall member 310 to de?ne an annular air
intake 313 and requires a change of direction of any
ing to the compressor inlet thereby increasing the effi
ciency and air ?ow characteristics of the compressor
sound waves emanating past the target ba?le member.
and to re?ectively dampen substantially unidirectional
exposed ?berglass material.
The directionalizing bathe comprises a cylindrical cas 45 high frequency sound Waves emanating from the inlet of
ing 32th of angled cross-section having a radial ?ange
said compressor, drive means intermediate said‘ engine
322 embracing the intake bell 212 with slight radial.
and said ?rst fan means, an annular discharge manirold
clearance therebetween. The casing 329 may be sup-.
de?ned by said casing and embracing the discharge of
ported by a suitable bracket 324 carried by the generator
said compressor and connected thereto by an annular
16 and in turn supports the target ba?le 302 by means 50 diffuser, said annular discharge manifold having an ar
of a plurality of radial straps 326. The casing 320 is
cuate outlet opening therein, a cylindrical heat exchange
lined‘ with sound absorbing insulation material 328, simi»
matrix embracing said annular manifold and supported
lar to that lining the anechoic wedges of the target ba?le,
by said casing for rotation past said manifold opening,
which may be similarly spray coated with a thin vinyl
seal means interposed between said matrix and said cas
?lm and covered with wire cloth screening 330 to pre 55 ing and cooperating therewith to de?ne a matrix cooling
vent erosion by the intake air ?ow.
chamber and a compressed air cooling chamber, passage
means including sound attenuating impingement ?lter
The distance between the target baffle and the nozzle
means connecting said air cooling chamber to said engine,
and the diametrical dimensions of the target and. direc
means for drivingly connecting said matrix to said engine,
tionalizing baf?e members are preferably such that a tan
gent, indicated in broken lines at 332, to the bell 212 60 said silencer means and said casing de?ning a cooling
and: passing through the peripheral face 334 of the di
rectionalizing ba?le intersects the cylindrical Wall mem
air duct therebetween embracing said intake duct, said
cooling air duct connecting said matrix cooling chamber
to. the interior of said compartment and to the atmos
ber 310 of the target assembly 302. It will be seen
phere outside said compartment, and a second fan means
that the ba?le members of this additional stage of silenc-'
ing thus cooperate to provide a combined dissipative and 65 drivingly connected to said ?rst fan means and operable
to induce cooling air ?ow through said matrix from
a non-dissipative reaction muf?er achieving noise reduc
the interior of said compartment to the atmosphere, said
cooling
air duct and the relatively low velocity cooling
energy emanating from the intake nozzle 212 and partly
air ?ow induced therethrough cooperating to insulate
by re?ecting the wave energy back toward the compressor
70 and attenuate sounds transmitted radially ouwardly of said
source.
intake duct.
From the foregoing description of the several forms‘
2. In. combination, a. housing member having an en
of the invention, it will be obvious to those skilled in
gine compartment therein, an internal combustion engine
tion partly by de?ection and absorption of the sound
the art that various changes might be made in the illus
mounted in said compartment, ?lter means connecting
trative embodiments without departing from the spirit 75 the interior of said compartment to the atmosphere out
3,077,731
id
side the compartment, means for supplying pressurized
charging air to said engine including a casing, a high
speed rotary compressor mounted in said casing, said
compressor having an inlet conne-ctable to said engine
surized charging air to said engine and having an inlet
said compressor and de?ning an intake duct connecting
the inlet of said compressor to said compartment, said
the compressor inlet and said fan means being capable
of re?ective dampening of the substantially unidirec
tional high frequency sound waves emanating from the
connectable to atmosphere and a discharge connected
to said engine, silencer means associated wtih and defin
ing an intake duct connected to the inlet of said com
mounting compartment and a discharge connectable to OX pressor, fan means operable to impart limited pressure
said engine, silencer means associated with the inlet of
and swirl to the air ?owing through said intake duct to
silencer means including a first fan means operable to
impart limited pressure and swirl to the air iiowin 10 inlet of said compressor, and drive means intermediate
through said duct to the compressor inlet and to re?ect
said engine and said compressor and fan means and oper
substantially unidirectional high frequency sound waves
emanating from the inlet of said compressor thereby
damping such waves, said casing de?ning a discharge
manifold interconnecting the discharge of said compres
sor with said engine, said manifold having an opening
therein, a cylindrical heat exchange matrix supported for
rotation by said casing and intersecting said manifold
through said manifold opening, seal means interposed
between said matrix and said casing and cooperating 20
therewith to seal said matrix relative to said manifold
and to de?ne a matrix cooling chamber outside said mani
fold, said matrix cooling chamber interconnecting the
able to drive both said compressor and fan means at‘
rotative speeds proportional to the speed of the engine
with the driven speed of said fan means being substantially
slower than the sound-generating and air-?ow-inducing
driven speed of said compressor.
5. in combination with an internal combustion engine,
means for supplying pressurized charging air to said en—
gine including a high speed rotary compressor having
an inlet connectable to the atmosphere and a discharge
connectable to said engine, a discharge manifo'd inter
connecting the discharge of said compressor with said
engine and having an opening therein, a cylindrical heat
cooling air ?ow through said matrix and said cooling
exchange matrix supported for rotation and intersecting
said manifold through said manifold opening, seal means
interposed between said matrix and said manifold, duct
chamber from the interior of said compartment to the
atmosphere, and means operable to drive said compressor,
said matrix, and said fan means at substantially propor
tionate and predetermined rotative speeds varying in ac
means de?ning a matrix cooling chamber outside said
manifold, fan means operable to induce cooling air flow
through said matrix and said cooling chamber, and means
operable to drive said compressor, said matrix, and said
corda ce with the operation of the engine.
3. In combination, a housing member having an en
fan means at different rotative speeds proportionate to
gine compartment therein, an internal combustion engine
gine to provide substantially even charging air tempera
mounted in said compartment, ?lter means connecting
the interior of said compartment to the atmosphere out
side the compartment, compressor means operable to
ture under all engine operating conditions.
6. In combination, an internal combustion engine,
means for pressure charging said engine including a com
supply pressurized charging air to said engine, said com
pressor means capable of being rotatably driven, turbine
interior of said compartment to the atmosphere outside
the compartment, secondary fan means operable to induce
pressor means having an inlet connectable to the inte
and varying in accordance with the operation of the en'
‘
means drivingly connected to and operable to drive said
rior of said engine mounting compartment and a dis
compressor means in accordance with the engine exhaust
charge connected to said engine, said compartment and 40 gases supplied thereto, overrunning drive means inter
?lter means de?ning acoustical impedance means oper
mediate said engine and said compressor means and oper
able to insulate and damp sound waves generated by
able to drivingly connect said compressor to said engine
said compressor and engine, said engine constituting a
when said engine drive means is rotating faster than said
high frequency sound attenuating means connected to the
turbine driving means whereby said compressor means is
discharge of the compressor, turbine means operable to
both engine and turbine driven under such operating con
ditions and said overrunning drive means being operable
drive said compressor means in accordance with engine
when said turbine means is rotating faster than said en
exhaust gases supplied thereto, mechanical drive means
gine drive means to permit said turbine to overrun said
intermediate the engine and the compressor means and
including overrunning means operable to drivingly con
engine drive means, silencer means associated with the
inlet of said compressor and de?ning an intake duct con
nect said compressor means to said engine and operable
necting the inlet of said compressor means to the atmos
to disconnect said compressor means from said engine
phere, a ?rst fan means in said intake duct and operable
whenever said turbine means is being rotatably driven
to impart limited pressure and swirl to the air supplied
faster than said mechanical drive means, whereby said
to said compressor inlet, said ?rst fan means being ca
compressor means is partially engine driven when said
pabie of reflecting unidirectional high frequency sound
mechanical drive means is being driven faster than said
waves thereby damping such waves emanating from the
turbine means and said turbine drive means is permitted
inlet of said compressor, a diffuser connecting the dis
to overrun said mechanical drive means whenever said
charge of said compressor to a discharge manifold, said
turbine drive means is being driven faster than said me
discharge manifold having an opening therein, a cylin—
chanical drive means, silencer means associated with the
inlet of said compressor means and de?ning an intake 60 drical heat exchange matrix supported for rotary move
ment relative to said manifold opening, seal means inter
duct connecting the inlet of said compressor means to
posed between said matrix and said manifold, a second
the interior of said compartment, a fan means associated
fan means associated with said matrix and operable to
with said intake duct and operable to impart limited pres
induce the ?ow of cooling air through the portion of said
sure and swirl to the air ?owing to the compressor inlet
thereby increasing the efficiency and air flow pumping 65 matrix outside said manifold, and means for drivingly
connecting said matrix and said fan means to said engine,
characteristics of the compressor and said fan means
said last-mentioned means being operable to drive said
being capable of re?ective dampening of the substantially
matrix at a substantially lower rotative speed relative to
unidirectional high frequency sound waves emanating
its driving speed of said fan means.
from the inlet of said compressor, and drive means inter
7. In combinaation, a housing member de?ning an
mediate said engine and said fan means and operable 70
engine compartment, an internal combustion engine
to drive said fan means at a proportionate and substan
mounted in said compartment, ?lter means connecting
tially lower rotative speed than the sound-generating and
said compartment to the atmosphere outside the compart~
air-?ow-inducing driven rotative speed of said compressor.
merit, means for supplying pressurized charging air to
4. In combination, an internal combustion engine, a
high speed rotary compressor operable to supply pres
said engine including a casing, a compressor rotatably
answer
15
mounted within said casing, said compressor having an
inlet connectable to the interior of said engine mounting
compartment and a discharge connectable to said engine,
silencer means associated with the inlet of said compres
sor and de?ning an intake duct connecting the inlet of
said compressor means to the interior of said compart
ment, a ?rst fan means associated with said intake duct
and operable to impart limited pressure and swirl to
the air ?owing to the compressor inlet and to re?ectively
lb
means and said fan means at predetermined proportionate
rotative speeds varying in accordance with engine opera
tion, said drive means being operable to drive said fan
means at a substantially lower rotative speed than its
driving speed of said compressor means.
10. In a power plant, the combination comprising, an
internal combustion engine, a high speed rotary com
pressor having an inlet connectable to atmosphere and a
discharge connectable to supply pressurized charging air
dampen substantially unidirectional high frequency sound
to the engine, turbine means operable to drive said com
waves emanating from the inlet of said compressor, an
pressor in accordance with engine exhaust gases supplied
annular discharge manifold de?ned by said casing em
bracing the discharge of said compressor and being con
thereto, manifold means for supplying engine exhaust
nected thereto by an annular diffuser, said annular dis
gases through said turbine means, mechanical drive means
intermediate the engine and the compressor and includ
charge manifold having an arcuate outlet opening therein, 15 ing overrunning means operable to drivingly connect said
a cylindrical heat exchange matrix embracing said an
compressor to said engine when said mechanical drive
nular manifold and supported by said casing for rotation
means is being driven faster than said turbine means and
past said manifold opening, seal means interposed be
operable to disconnect said compressor from said engine
tween said matrix and said casing and cooperating there
whenever said turbine means is being rotatably driven
with to de?ne a matrix cooling chamber and a com
pressed air cooling chamber, passage means connecting
said air cooling chamber to said engine, said silencer
faster than said mechanical drive means whereby said
compressor is partially engine driven when said mechani
cal drive means is being driven faster than said turbine
means and said casing de?ning a cooling air duct there
means and said turbine drive means is permitted to over
between embracing said silencer and interconnecting said
compartment with the atmosphere outside said compart
run said mechanical drive means whenever said turbine
drive means is being driven faster than said mechanical‘
drive means, silencer means associated with the inlet of
said compressor and de?ning an annular intake 'duct con
verging toward the inlet of said compressor, a ?rst fan
means intersecting said annular duct intermediate its ends
ment through said matrix cooling chamber, secondary
fan means associated with said ?rst fan means and oner
able to induce cooling air ?ow through said cooling air
duct and matrix, and means operable to drive said com
pressor, said matrix, and said fan means at different rota 3O and operable to impart limited pressure and swirl to the
tive speeds proportionate to and varying in accordance
air ?owing to the compressor inlet and to re?ect the
with the operation of the engine.
substantially unidirectional high frequency sound waves
8. A power plant installation comprising, in combina
emanating from the inlet of said compressor thereby
tion, a housing member having an engine compartment
dampening such sound waves, an annular discharge mani
therein, an internal combustion engine mounted in said 35 fold embracing the discharge of said compressor and be
engine compartment, ?lter means connecting the interior
ing connected thereto through an annular diffuser, said
of said compartment to the atmosphere outside said hous
discharge manifold having an outlet opening therein, pas
ingmember, means for supplying pressurized charging air
sage means connecting said outlet opening to said engine,
to said engine including a casing, a compressor rotatably
a cylindrical heat exchange matrix embracing said an-v
mounted within said casing, said compressor having an
nular manifold and supported by said casing for rotation
inlet connected to the interior of said engine mounting
between said manifold opening and said passage means,
compartment and a discharge connectable to said engine,
cooling air duct means for directing cooling air through
silencer means associated with the inlet of said compres
sor and including a ?rst fan means operable to dampingly
said matrix outside said manifold opening, seal means
re?ect substantially unidirectional high frequency sound
sage means and said cooling air duct means and cooperat
ing therewith to de?ne a matrix cooling chamber, a sec
ond fan means drivingly connected to said ?rst fan means
waves emanating from the inlet of said compressor, a
discharge manifold connected to the discharge of said
compressor and having an opening therein, a cylindrical
interposed between said matrix, said manifold and pas
and operable to induce cooling air flow through said
heat exchange matrix supported by said casing for rota
matrix from the interior of said compartment to the at
tion past said manifold opening, seal means interposed 50 mosphere, and means for drivingly connecting said matrix
between said matrix and said casing and cooperating
and said fan means to said engine and operable to drive
therewith to de?ne a matrix cooling chamber and a com
pressed air cooling chamber, said air cooling chamber
said matrix and said fan means at different speeds pro
portionate to and varying in accordance with the engine
being connected to said engine and said matrix cooling
operating speed.
chamber interconnecting said compartment to the atmos 55
11. in combination, a high speed rotary compressor
phere outside said housing member, second fan means
capable of generating high frequency sound waves and
operable to induce cooling air ?ow through said matrix
having an air inlet and a pressurized air discharge con
and cooling chamber from said compartment to the at
nectable to a sound attenuating system, silencer means
mosphere, and means operable to drive said compressor,
including an intake duct connected to the inlet of said
said matrix and said fan means at predetermined propor 60 compressor and lined with sound absorbing material,
tionate rotative speeds varying in accordance with engine
and fan means intersecting said intake duct and operable
operation.
to impart limited pressure and swirl to the air ?owing
9. A power plant comprising, in combination, a hous
through said intake duct to the compressor inlet to in
ing member having an engine compartment therein, an
crease the pumping efficiency and air flow characteristic
internal combustion engine mounted in said engine com 65
of the compressor, said fan means being further capable
partment, ?lter means connecting the interior of said
of
de?ecting and reflecting the substantially unidirectional
compartment to the atmosphere outside, compressor
high frequency sound waves generated by and emanating
means operable to supply pressurized charging air to said
from the inlet of said compressor against the lined sound
engine, said compressor means ‘having an inlet connected
to the interior of said engine mounting chamber and a 70 absorbing side walls of said intake duct and toward the
compressor inlet thereby damping such high frequency
discharge connected to said engine, a relatively low pres
sure induction fan means associated with the inlet of said
compressor and operable to dampingly re?ect high fre
sound waves.
12. The combination set forth in claim 11 and includ
quency sound waves emanating from the inlet of said
ing means for rotatively driving said compressor and fan
compressor, and means operable to drive said compressor 75 means at proportionate speeds, the driven speed of said
3,077,731
1?
1
fan means being substantially slower than the'driven
speed of said compressor.
two radially spaced frusto~conical cylindrical wall mem~
bers converging toward said source connectable end, a
13. The combination set forth in claim 11 and includ
ing means for rotatively driving said fan means at a
nectable end being de?ned by two radially spaced cylin
second portion of said duct distal from said source con
speed proportionate to the primary frequency generated
drical members of constant radial dimension and axially
by said compressor.
14. In combination, a high speed rotary compressor
aligned with said ?rst duct portion, rotary baf?e means
intersecting said duct intermediate its ends and operable
capable of generating substantially unidirectional high
to deflect the unidirectional hgh frequency sound waves
frequency sound waves and having a fluid inlet opening
emanating from the source connectable end against the
and a pressurized ?uid discharge opening connectable 10 lined sound absorbing side walls of said duct and back
to a sound attenuating pressure receiving system, silencer
toward the source connectable end in out-of-phase, wave
means including an intake duct connected to the inlet
damping relation to the high frequency sound emanating
opening of said compressor, fan means intersecting said
therefrom, means for rotatively driving said ba?‘le means
intake duct and operable to impart limited swirl to the
at a relatively low speed proportional to the primary fre
air flowing through said intake duct to the compressor in 15 quency of the sound emanating from said source con
let thereby increasing the pumping efficiency and air flow
nectabie end, a ?rst stationary ba?ie means mounted in
characteristic of the compressor, said fan means being
spaced relation adjacent to the other end of said duct
comprising a circular plate mounted normal to and in
axial alignment with the common axis of said duct por
further capable of de?ecting and re?ecting at least a por
tion of the substantially unidirectional high frequency
sound waves emanating from the inlet of said compressor 20 tions, a plurality of plates mounted in parallel spaced
back toward the compressor inlet in out~of-phase rela
relation on said circular plate and tapered to form a
tion thereby damping the generated high frequency sound
plurality of acoustical wedges normal to and extending
"ayes, and means for rotatively driving said compressor
toward the adjacent end of said duct, said parallel plates
and fan means at substantially proportionate speeds, the
being lined with a sound absorbing material and provid
driven speed of said fan means being substantially slower 25 ing a tapered sound absorbing thickness to said material
than the driven speed of said compressor.
longitudinally of said parallel plates thereby varying
15. A silencer for a high frequency sound generator
the optimum sound wave absorbing characteristic of
such as a high speed rotary compressor and having a
said material presented to the adjacent end of said duct
sound emitting opening therein, said silencer comprising
to broaden the frequency absorption spectrum of said
a duct member connectable at one end to the sound gen
?rst stationary baffle means, and a cylindrical member
erator opening and lined with a sound absorbing ma
embracing said circular plate and extending longitudinally
terial, rotary ba?le means intersecting said duct and
therefrom to de?ne a side wall of a length embracing
operable to de?ect at least a portion of the substantially
said parallel plates and plate lining material, and a sec
uudirectional high frequency sound waves against the
ond stationary bai'?le means including an annular cas
line sound absorbing side walls of the duct and back to 35 ing member of angled cross-section having a radially ex
ward said one end of the duct in out-of-phase relation
tending ?ange closely embracing said other end of said
thereto thereby damping the sound waves entering said
duct and a longitudinally extending ?ange spacedly em
one end, and means for rotatively driving said ba?ie
bracing the cylindrical wall member of said ?rst stationary
means at a relatively low speed proportional to the pri
ba?ie means, said annular casing member being lined
40 with sound absorbing material, said ?rst and second sta
mary frequency being generated by said generator.
16. A silencer for a sound generator capable of gen—
tionary ba?’le means being dimensioned and mounted in
erating substantially unidirectional high frequency sound
such spaced relation to each other and to the adjacent end
waves such as a high speed rotary compressor and hav
of said duct that a cone generated by a line extending be
ing a sound emitting opening therein, said silencer includ
tween the adjacent end of the duct and the distal end of
ing a duct connectable at one end to the opening in the 4.5 said casing member intersects the duct adjacent end of
sound generator, rotary ba?le means intersecting said
said cylindrical wall member.
duct and operable to de?ect the generated high frequency
20. A silencer for unidirectional high frequency sound
sound waves entering said one end against the side walls
of said duct and back toward said one end in out-of
waves including a duct connectable at one end to a source
of such high frequency sound, as least a portion of said
phase relation to the generated high frequency sound 50 duct being de?ned by two radially spaced frusto-conical
waves thereby damping such sound waves, and means
for rotatively driving said ba??e means at a relatively
cylindrical wall members converging toward said one end
and lined with a sound absorbing material, a target baf
low speed proportional to the primary frequency being
?e means mounted in spaced relation adjacent to the
generated by said generator.
other end of said duct and comprising a circular plate
17. A silencer for a wide spectrum of substantially 55 mounted normal to and in axial alignment to the axis of
unidirectional high frequency sound including a duct of
annular cross-section connectable to and converging to
ward an opening of a high frequency sound emitting
source, rotary ba?ie means intersecting said duct inter
mediate its ends, said ba?ie means being operable to re
fleet at lea-st a portion of the high frequency sound waves
toward the side walls of said duct and back toward the
sound emitting source in out-of-phase, damping rela
said duct, a plurality of plates mounted in parallel spaced
relation on said circular plate and being tapered to form
a plurality of acoustical wedges normal to and extending
toward the adjacent end of said duct, said parallel plates
each being lined with a sound absorbing material to pro
vide a tapered sound absorbing thickness to said material
longitudinally of said parallel plates toward the adjacent
end of said duet thereby varying the optimum sound
tion to the waves emanating therefrom, and means for
wave absorbing characteristic of said material, and a
rotatively driving said baffle means at a speed propor 65 cylindrical member embracing said circular plate and
tional to the primary frequency of the sound emanating
extending longitudinally therefrom to de?ne a side wall
from the source.
of a length embracing said parallel plates and lining ma~
18. In a silencer as set forth in claim 17, said duct
terial, and a directionalizing ba?de means including an
being lined with sound absorbing material of tapered
annular casing member of angled cross-section having a
70 ?rst longitudinally extending flange spacedly embracing
19. A silencer for substantially unidirectional high fre
the cylindrical wall member of said target baffle means
quency sound including a duct lined with sound absorb~
and a second ?ange extending radially inwardly there
radial dimension.
ing material and connectable at one end to a source of
such high frequency sound, a ?rst portion of said duct
adjacent to said source connectable end being de?ned by
from and closely embracing said adjacent end of said
duct, the inner surfaces of said ?rst and second ?anges
of said casing member being lined with sound absorbing
sprtgr'sl
"in
material, and said ?rst and second ba?ie means being
dimensioned and mounted in such spaced relation to each
other and to the adjacent end of said duct that a cone
generated by a line extending between the inner surface
of the opening de?ned by the adjacent end of the duct
pable of generating a wide spectrum of substantially uni-1v
directional high frequency sound waves and comprising a
casing de?ning a compressor chamber and having inlet
and outlet openings therein, said outlet opening being
connectable to a pressure receiving system, a compressor
impeller rotatably mounted in said compressor chamber
and operable to deliver pressurized air to said outlet open
cylindrical wall member.
ing, a cylindrical heat exchange matrix supported by said
21. A silencer for substantially unidirectional high fre
casing for rotation past said outlet opening, said casing-v
quency sound waves comprising a member connectable to
and de?ning a duct divergent from a source of such high 10 de?ning a compressed air cooling chamber adjacent said
and the distal end of said casing member intersects said
outlet opening and a matrix cooling chamber, said com
frequency sound, a target ba?le means mounted in spaced
pressed air cooling chamber being connected to said pres
relation adjacent to the divergent end of said duct and
sure receiving system, a ?rst fan means operable to induce
comprising a ?rst plate mounted normal to the adjacent
cooling air ?ow through said matrix within said matrix
divergent end of said duct, a plurality of plates mounted
in parallel spaced relation to each other on said ?rst plate 15 cooling chamber, a ?rst silencer means including an intake
duct connected at one end thereof to the inlet opening
and tapered to form a plurality of acoustical wedges nor
and lined with sound absorbing material, a second fan
mal to and extending toward the adjacent end of said
means operable to impart limited swirl to the air ?owing
duct, said parallel plates being lined with a sound absorb
through the intake duct to the compressor inlet and im
ing material to present a tapered sound absorbing thick
ness of said material longitudinally of said parallel plates 20 peller, said second fan means including a plurality of fan
toward the adjacent end of said duct, thereby varying the
‘blades capable of de?ecting and re?ecting a portion of
optimum sound wave absorbing characteristic of said ma
the substantially unidirectional high frequency sound
terial, said ?rst plate having a side wall extending longi
tudinally therefrom and embracing said parallel plates and
Waves emanating from the inlet against the lined sound
absorbing side Walls of said intake duct and back to‘
ward the compressor inlet thereby damping such high
lining material, a directionalizing ba?le means including
a casing member lined with sound absorbing material and
closely embracing the divergent adjacent end of said duct
and spacedly embracing the wall extending from said ?rst
frequency sound waves, secondary silencer means asso
ciated with the end of said intake duct distal from said
compressor inlet and comprising a target plate parallel
to and exceeding the size of said adjacent duct end, a
plate, and said baffle means being dimensioned and
mounted in such spaced relation to each other and to the 30 plurality of relatively thin acoustical wedges carried by
said plate and tapered toward said intake duct, said wedges
adjacent divergent end of said duct that any line extend
de?ning a plurality of recesses therebetween, sound ab~
ing between the inner surface of the adjacent end of the
sorbing material covering said wedges and substantially
duct and the distal end of said casing member intersects
?lling the recesses therebetween, and said secondary
said wall.
22. A silencer for a device generating substantially uni 35 silencer means being mounted in limited parallel spaced
relation to said adjacent duct end thereby tending to pre
directional high frequency sound waves and having a
vent any straight-line emission of high frequency sound
sound emitting opening therein, said silencer including a
waves therebetween from said duct, said silencer wedges
target ba?le mounted in spaced relation to said opening
de?ecting a portion of such high frequency sound waves
and comprising a recessed plate exceeding the size of said
opening and having a bottom Wall in spaced parallel rela~ 40 for dissipation by said Wedge covering material and said
target plate re?ecting a portion of such high frequency
tion to said opening and a peripheral wall extending longi
waves back into said duct in out-of-phase relation tend=
tudinally toward said opening, a plurality of plates
mounted in parallel spaced relation to each other on said
ing to dampen such waves passing said second fan means,
and means operable to drive said compressor impeller at
plate within the recess de?ned by said peripheral wall and
ibeing tapered to form a plurality of acoustical wedges 45 a relatively high speed and including means for driving
said matrix and said fan means at relatively slow speeds
normal to and extending toward said opening, said wedge
proportional to the impeller driven speed.
plates being lined with sound absorbing material of
25. A high speed rotary compressor mechanism capable
tapered sound absorbing thickness longitudinally of said
of generating a wide spectrum of substantially unidireed
opening to provide a variation in the optimum sound wave
frequency absorption characteristic of the material, and 50 tional high frequency sound waves comprising a casing
de?ning a compressor chamber and having inlet and out
a directionalizing ba?ie including a casing member inter
let openings therein,'said outlet opening being connectable
nally lined with sound absorbing material, said casing
to a pressure receiving system, a compressor impeller
member extending from said opening and embracing said
rotatably mounted in said compressor chamber and 0p
target battle in limited spaced relation thereto preventing
any straight-line emission of high frequency sound there 55 erable to deliver pressurized air to said outlet opening,
said casing de?ning a compressed air cooling chamber ad
between from said opening.
jacent said outlet opening, said compressed air cooling
23. A silencer for a device generating substantially uni
directional high frequency sound waves and having a
chamber being connected to said pressure receiving sys
tem, said casing further de?ning a matrix cooling cham
a target plate exceeding the size of said opening, a plu 60 ber, a cylindrical heat exchange matrix supported by said
casing for rotation through said cooling chambers, a ?rst
rality of relatively thin acoustical wedges carried by said
fan means including a ?rst plurality of fan blades operable
plate and tapered toward said opening, said wedges de
sound emitting opening therein, said silencer comprising
?ning a plurality of recesses therebetween, sound absorb
to induce cooling air flow through said matrix within said
matrix cooling chamber, silencing means including an in
ing material covering said wedges and substantially ?lling
the recesses therebetween, and said silencer being mounted 65 take duct connected at one end thereof to the inlet open
ing and lined with sound absorbing material, a second fan
in limited parallel spaced relation to said opening thereby
means including a second plurality of fan blades operable
tending to prevent straight-line emission of high fre
to impart limited swirl to the air ?owing through the in->
quency sound therebetween, said silencer wedges de?ect
take duct to the compressor inlet and impeller, said sec
ing a portion of the generated high frequency sound waves
for dissipation by said sound absorbing material and said 70 ond fan blades being capable of de?ecting and re?ecting
a portion‘of the substantially unidirectional high frequency
target plate ‘re?ecting a portion of the generated high fre
sound Waves generated by and emanating from the inlet
quency waves back toward said opening in out-of-phas'e
of the compressor against the lined sound absorbing side
relation tending to dampen the sound waves emitting from
walls of said'intake duct and back towardthe compressor
the opening.
24. A high speed rotary compressor mechanism ca~ 75 inlet thereby damping such high frequency sound waves,‘
3,077,731
21
means operable to drive said compressor impeller at a
relatively high speed, and means for driving said matrix
and said fan means at speeds proportional to the impeller
driven speed.
26. A high speed rotary compressor mechanism capable
of generating a wide spectrum of substantially unidirec
tional high frequency sound waves comprising a casing
de?ning a compressor chamber having inlet and outlet
openings leading thereto, an impeller rotatably mounted
in said compressor chamber and operable to deliver
pressurized air to said outlet opening, said casing de?ning
a compressed air cooling chamber adjacent said outlet
opening, said compressed air cooling chamber being con
nectable to a pressure receiving system, said casing fur
ther de?ning a matrix cooling chamber, a cylindrical heat
22
dissipation by said wedge covering material and said
target plate re?ecting a portion of such high frequency
waves back into said duct in out-of-phase relation tend
ing to dampen such waves passing said ?rst fan means,
and a directionalizing ba?le including an annular casing
member of angled cross-section closely embracing said
other end of said duct and spacedly embracing the cylin
drical wall member of said ?rst stationary baffle means,
said annular casing member being lined with sound ab
sorbing material, said target and directionalizing ba?le
means being dimensioned and mounted in such spaced
relation to each other and to the adjacent end of said
duct that a cone generated by a line extended between
the adjacent end of the duct and the distal end of said
casing member intersects said cylindrical Wall member.
29. A high speed rotary compressor mechanism com
prising a casing de?ning a compressor chamber having
inlet and outlet openings leading thereto, animpeller ro
with the inlet of said compressor and including an intake
tatably mounted in said compressor chamber and operable
duct connected at one end thereof to the inlet of said com
pressor chamber, a ?rst fan means including a ?rst plu 20 to deliver pressurized air to said outlet opening, said casing
de?ning a compressed air cooling chamber adjacent said
rality of fan ‘blades intersecting said intake duct and op
outlet opening, said compressed air cooling chamber be
erable to impart limited swirl to the air ?owing through
ing connectable to a pressure receiving system, said casing
the intake duct to the compressor inlet and impeller, said
further de?ning a matrix cooling chamber, a cylindrical
?rst fan blades being capable of de?ecting and re?ecting
heat exchange matrix supported by said casing for ro
a portion of the substantially unidirectional high frequency
tation through said cooling chambers, an intake duct
sound waves generated by and emanating from the inlet
exchange matrix supported by said casing for rotation
through said cooling chambers, silencer means associated
of the compressor against the side walls of said intake
duct and back toward the compressor inlet thereby damp
ing such high frequency sound waves, said intake duct and
said casing de?ning a cooling air duct therebetween con
centrically embracing said intake duct and connected to
said matrix cooling chamber, a second fan means associ
ated with said ?rst fan means and including a second plu
rality of fan blades intersecting said cooling air duct and
connected at one end thereof to the inlet, said intake duct
tively high speed and including means for driving said
relatively high speed and including means for driving
and said casing de?ning a cooling air duct therebetween
concentrically embracing said intake duct and connected
to said matrix cooling chamber, a fan member having a
?rst plurality of fan blades intersecting said intake duct
and operable to impart limited swirl to the air ?owing
through the intake duct to the compressor inlet and im
peller and having a second plurality of fan blades in
operable to induce cooling air flow through said cooling 35 tersecting said cooling air duct and operable to induce
cooling air ?ow through said cooling air duct and matrix,
air duct and matrix, and driving means including means
and means for driving said compressor impeller at a
operable to drive said compressor impeller at a rela
matrix and said fan means at relatively slower speeds
said matrix and said fan means at relatively slower speeds
proportional to the impeller driven speed.
proportional to the impeller driven speed.
27. A compressor mechanism as set forth in claim 26
and including a second silencer means associated with
the end of said intake duct distal from said compressor
inlet and comprising a target plate parallel to and exceed
ing the size of said adjacent duct end, a plurality of rela
30. A silencer for a high speed rotary compressor
mechanism having an impeller rotatably driven at a rela
tively thin acoustical wedges carried by said plate and
tapered toward said intake duct, said wedges de?ning a
plurality of recesses therebetween, sound absorbing mate_
rial covering said wedges and substantially ?lling the
recesses therebetween, and said secondary silencer means
being mounted in limited parallel spaced relation to said
adjacent duct end thereby tending to prevent straight
line emission of high frequency sound waves therebetween
from said duct, said silencer wedges de?ecting a portion of
such high frequency sound Waves for dissipation by said
wedge covering material and said target plate re?ecting
a portion of such high frequency Waves back into said
duct in out-of-phase relation tending to dampen such
tively high speed and operable to deliver pressurized air
to an outlet opening and generating substantially unidirec<
tional high frequency sound waves capable of echoic
transmission from an inlet opening, said silencer com
prising an intake duct connectable at one end thereof to
the sound transmitting inlet of the compressor and termi
nating at its opposite end in an annular bell generated
by an arc diverging radially and longitudinally outwardly
from said one end, and silencer means associated with
said opposite end of the intake duct and comprising a
circular target plate of a diameter exceeding that of said
intake duct bell, a plurality of relatively thin acoustical
wedges carried by said plate and tapered toward said in
take duct, said wedges de?ning a plurality of recesses
therebetween, and sound absorbing material covering said
wedges and substantially ?lling the recesses therebetween,
said silencer means being mounted in limited parallel
waves passing said ?rst fan means.
28. In a compressor mechanism as set forth in claim 60 spaced relation to and coaxially of said duct bell end
26, a second silencer means including a target ba?ie
thereby preventing straight-line transmission of high fre
mounted in spaced relation to the other end of said intake
duct and comprising a circular plate mounted normal to
the axis of said duct, said circular plate being diametrical
ly larger than the adjacent end of said intake duct, a plu 65
said silencer wedges de?ecting a portion of such high
frequency sound waves for dissipation by said wedge
covering material and said target plate re?ecting a portion
rality of relatively thin acoustical wedges carried by said
quency sound waves therebetween from said intake duct,
of such high frequency waves back into said duct in
out-of-phase relation tending to dampen such waves.
circular plate and tapered toward the adjacent end of
31. A silencer for a high speed rotary compressor
said duct, said wedges de?ning a plurality of recesses
mechanism having inlet and outlet openings and an im
therebetween, sound absorbing material covering said
wedges and substantially ?lling said recesses, a cylindrical 70 peller rotatably driven at a relatively high speed and
operable to deliver pressurized air to said outlet opening
peripheral wall carried by said circular plate and extend
ing longitudinally therefrom to de?ne a side wall of a
and generating substantially unidirectional high frequency
length embracing said parallel plates and lining material,
sound Waves capable of echoic transmission from the inlet
opening, said silencer comprising an intake duct con
said silencer wedges de?ecting a portion of any high fre
quency sound waves emanating from said intake duct for 75 nectable at one end thereof to the sound transmitting
23
24
inlet of the. compressor and terminating at its opposite
housing member and a discharge connected to the engine,
end in an annular bell generated by an arc diverging
silencer means associated with the inlet of the compressor
radialiy and longitudinally outwardly from said one end,
and including an intake duct connecting the compressor
inlet to the interior of the compartment, said housing com
partment and intake duct de?ning an acoustical impedance
a target baiiie mounted in spaced relation to said intake
bell and comprising a circular plate mounted normal to
the ‘axis of said duct, said circular plate being diametri
means operable to damp the primarily unidirectional high
cally larger than the periphery of said intake bell, a
frequency sound Waves generated by and emanating from
plurality of relatively thin acoustical wedges carried by
the inlet of the compressor, said engine constituting a high
‘said circular plate and tapered toward the adjacent end
frequency sound attenuating means connected to the com
of said duct, said Wedges de?ning a plurality of recesses 10 pressor discharge, fan means operable to impart limited
therebetween, sound absorbing material covering said
pressure and swirl to the air ?ow induced through said in
wedges and substantially ?lling said recesses, a cylindrical
take duct to the compressor inlet thereby increasing the
peripheral wall carried by said circular plate and extend
ef?ciency and airflow pumping characteristics of the com
ing longitudinally therefrom to de?ne a side wall of a
pressor, said fan means being further capable of re?ective
length embracing said parallel plates and lining material,
damping of the substantially unidirectional high frequency
said silencer wedges de?ecting a portion of the high fre
quency sound waves emanating from said intake duct for
sound wave emanating from the inlet of the compressor,
and drive means intermediate the engine and compressor
and the fan means and operable to drive both said com
pressor and fan means at rotative speeds proportional to
sound waves ‘back into said intake bell and duct in out 20 the speed of the engine with the driven speed of said fan
of-phase relation thereby tending to dampen the high
means being substantially lower than the sound-generat
dissipation by said wedge covering material and said
target plate re?ecting a portion of such high frequency
frequency sound waves passing outwardly of said duct,
ing and air-iiow-inducing driven ‘speed of the compressor.
and a directionalizing bafile including an annular casing
member of angled cross-section closely embracing the
outer periphery of said intake bell and spacedly embrac
ing the cylindrical Wall member of said ?rst stationary
baffle means, said annular casing member being lined
With sound absorbing material, and said target and -di
rectionalizing ba?'les being dimensioned and mounted in
such spaced relation to each other ‘and to the adjacent 30
end of said bell that said cylindrical wall intersects any
line tangent to the inner surface of said bell passing
through the distal end of said casing member thereby
preventing such high frequency sound Waves from passing
between said baffles in a straight line.
32. In combination, a housing member having an en~
gine compartment therein, an internal combustion engine
mounted in said compartment, a high speed rotary com
pressor operable to supply pressurized charging air to the
engine, said compressor having an inlet connectable
through said compartment to the atmosphere outside the
References €ited in the ?le of this patent
UNITED STATES PATENTS
2,160,666
2,267,275
McMahan ___________ _~ May 30, 1939
Gevrenz _____________ __ Dec. 23, 1941
' 2,313,244
Jones ________________ __ Mar. 9, 1943
2,353,998
2,397,941
2,402,725
2,434,726
2,585,968
2,646,027
2,647,372
2,714,881
2,749,998
2,801,518
Cortez ______________ __ July 18,
Birkigt _______________ __ Apr. 9,
Birkigt ______________ __ June 25,
Udale _______________ __ Jan. 20,
Schneider ____________ __ Feb. 19,
Ackerman et al _________ __ July 21,
Fell _________________ __ Aug. 4,
Bancel _______________ __ Aug. 9,
Walton et a1 __________ __ June 12,
Wosika et al. _________ __ Aug. 6,
1944
1946
1946
1948
1952
1953
1953
1955
1956
1957
2,869,670
Hoffman _____________ __ Ian. 20, 1959
2,916,026
2,929,198
Eoit et al ______________ __ Dec. 8, 1959
Crocchi _____________ __ Mar. 22, 1960
Mfr
UNITED STATES PATENT OFFICE
CERTIFICATE OF CORRECTION
Patent No» 3,077,731
February 19, 1963
Albert N, Addie et al.
It is hereby certified that error appears in the above numbered pat~
ent requiring correction and that the said Letters Patent should read as
corrected below.
Column 1, line 32, strike out "in"; column 3, line, 73,
for "accesory" read —— accessory ——; column 6, linell, for
"for" read —— are ——; column 14, line 3, for "wtih" I‘€ad+..-"
with ——;
line 70, ' for "combinaation" read‘ —- combination ——;
column 18, line 8, for "hgh" read —- high ——.
Signed and sealed this 14th day of April 1964.
(SEAL)
Au t: w. SWIDER
ERN‘ZISST
Attesting Officer ,
EDWARD J’ BRENNER
v
Commissioner of Patents
UNITED STATES PATENT OFFICE
CERTIFICATE OF CORRECTION
Patent» No» 3,077,731
February 19, 1963
Albert N. Addie et al.
It is hereby certified that error appears in the above numbered pat
ent requiring correction and that the said Letters Patent should read as
corrected below.
Column 1, line 32, strike out "in"; column 3, lines 73,
for "accesory" read —— accessory ——; column 6, line...l_,, £01‘
"for" read —— are ——; column 14,
with ——;
line 3, for "wtih" reads..n,v——
line 70, ' for "combinaation" read- —— combination ——;
column 18, line 8, for "hgh" read —— high ——.
Signed and sealed this 14th day of April 19641.°
(SEAL)
An; st: w. SWIDER
ERNQEST
Attesting Officer .,
EDWARD J° BRENNER
Commissioner of Patents
Документ
Категория
Без категории
Просмотров
0
Размер файла
2 817 Кб
Теги
1/--страниц
Пожаловаться на содержимое документа