U.S. patent number 3,793,848 [Application Number 05/309,909] was granted by the patent office on 1974-02-26 for gas compressor.
Invention is credited to Michael Eskeli.
United States Patent |
3,793,848 |
Eskeli |
February 26, 1974 |
GAS COMPRESSOR
Abstract
A method and apparatus for compressing gases, wherein a gas is
compressed in a continuous flow centrifuge provided with cooling.
The gas enters said centrifuge near axis of rotation, and leaves
near axis of rotation, thus providing for low work input to the
compressor. Gas to be compressed may be air, and the coolant may be
water. Leaving gas after compression will have lower temperature
than at compressor entry.
Inventors: |
Eskeli; Michael (Dallas,
TX) |
Family
ID: |
23200183 |
Appl.
No.: |
05/309,909 |
Filed: |
November 27, 1972 |
Current U.S.
Class: |
62/402; 415/120;
62/86; 165/86; 415/1; 415/178 |
Current CPC
Class: |
F04D
29/582 (20130101) |
Current International
Class: |
F04D
29/58 (20060101); F25d 009/00 () |
Field of
Search: |
;62/402,86,87 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wye; William J.
Claims
What is claimed is:
1. A device for compressing gases and comprising:
a. a rotor for compressing said gas, rotatably mounted and
supported by a shaft and bearing, said rotor having an entry for
said gaseous fluid near center of rotation, said rotor having
passages built within to pass said gaseous fluid from said entry
outwardly to rotor periphery and then to an exit near the center of
rotation, said gaseous fluid being compressed within said rotor by
centrifugal action by said rotor on said gaseous fluid to a higher
pressure near the periphery of said rotor, and then said gaseous
fluid being allowed to expand on the exit side of said rotor, vanes
being provided in rotor cavity to assure that said fluid will
rotate with said rotor, said gaseous fluid being cooled by a
coolant fluid being supplied to said rotor and being circulated in
heat exchange relationship with said gaseous fluid during
compression, said coolant fluid being supplied to said rotor near
axis of rotation and then being discharged from said rotor near
axis of rotation, said rotor being rotated and supplied with power
from an external source, said gaseous fluid pressure being lower at
rotor entry than at rotor exit; said coolant being in separate
passages within rotor;
b. a casing to support said rotor and to house said rotor.
2. The device of claim 1 wherein said casing is sealed to said
rotor at areas near the center of rotation, and where said casing
space between said casing and said rotor is evacuated by using a
vacuum pump to reduce friction losses on said rotor.
3. The device of claim 1 wherein said gaseous fluid is air, and
said coolant fluid is water.
Description
BACKGROUND OF THE INVENTION
This invention relates generally to devices for compressing air and
other gases by employing centrifugal force to compress said gas,
from a lower pressure to a higher pressure.
Various devices for compressing gases using centrifugal force have
been used in the past. In most conventional centrifugal
compressors, the gas is compressed by accelerating said gas to a
high velocity within a rotating impeller, and then discharging said
gas to a stationary diffuser where the gas velocity is reduced with
an accompanying increase in gas pressure. These devices generally
are inefficient due to high friction losses and turbulence losses
in the rotor passages and in the diffuser.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 illustrates a cross section of the compressor, seen from the
side, and
FIG. 2 shows an end view of the unit with a section removed to show
the interior construction of the rotor and housing.
DESCRIPTION OF PREFERRED EMBODIMENTS
It is an object of this invention to provide a method and apparatus
for compressing gases in a centrifugal machine wherein the energy
required to compress said gas is partially supplied from external
sources, and partially obtained from the gas being compressed,
resulting in a compressor for which power input is low. Further, it
is an object of this invention to provide a machine with a simple
construction wherein gas velocities are low within the machine thus
reducing friction losses.
In FIG. 1, gas enters the machine via entry 16, and passes to rotor
11 at entry port 21, and then passes within the said rotor to near
the periphery of said rotor and is being compressed by centrifugal
action by said rotor, with cooling being provided during
compression by cooling coil 12. After compression, said gas is
returned to center of rotor and leaves rotor at exit 14. Coolant
fluid is being supplied via coolant entry 17, and passes to rotor
via shaft 19, to distribution conduit 13, and from there to heat
exchanger coil 12, and from there back to passage in shaft, and to
coolant exit 18. 10 is rotor casing, 22 and 23 are rotor seals, 20
is rotor shaft bearing, 27 is thermal insulation applied to rotor
divider 25, 24 is rotor vane to assure that said gas will rotate
with said rotor, and 15 is a vent opening from space between rotor
and housing, said vent may be connected to a vacuum pump to
evacuate said space and thus reduce drag on said rotor.
In FIG. 2, an end view of the unit shown in FIG. 1, is illustrated.
A section is removed from the unit to show interior details. 10 is
casing, 11 is rotor, 13 is coolant supply to heat exchanger 12, 24
is a radial vane within rotor cavity, 16 is inlet for gas, 19 is
rotor shaft, 26 is unit base.
In operation, said gaseous fluid enters said rotor, near the axis
of rotation, and is compressed within the rotor cavity by
centrifugal action by said rotor on said gas, said compression
being nearly isothermal, with cooling being supplied during
compression by a heat exchanger provided within said rotor cavity.
After reaching rotor periphery, said gaseous fluid is passed on the
other side of said rotor back to rotor center; thus, the work
require to compress said gaseous fluid on entry side of said rotor,
is nearly all recovered on the exit side of said rotor, with vanes
placed within rotor cavity assuring that the gaseous fluid will
rotate with rotor at all times. There is a decrease in gaseous
fluid pressure when the fluid passes from the rotor periphery to
rotor exit at center of rotation, but this pressure loss is less
than the pressure gain was on the entry side; thence, the unit exit
pressure is higher than the unit entry pressure. Thermal insulation
is placed on the rotor dividing wall to prevent heat being added to
the cool gaseous fluid at the exit side of the rotor, as shown in
FIG. 1, item 27. It should be noted that the gaseous fluid
temperature is lower at unit exit, than at unit entry, and that the
temperature of the leaving cooling fluid is higher than the
temperature of the entering cooling fluid.
The rotor cavity is sized to provide for relatively low gaseous
fluid velocities, relative to rotor, typically these velocities in
the area near the periphery are below 100 feet per second. The
rotor tangential velocities at periphery are high, and may range
from 500 feet per second upwards; these rotor velocities are
dependent of the physical properties of the fluid being compressed,
and the pressure required at rotor exit.
Power from an external source is supplied to rotor shaft 19.
The rotor entry and exit openings may be the same diameter, or they
may be different, as indicated in FIG. 1, or as required for
pressure differential between rotor entry and exit.
The rotor side walls at rotor exterior may be built closely to
rotor casing so that the space between rotor and wall may be
partially evacuated by rotating thus reducing drag losses. Also,
the space between rotor and casing may be evacuated by using a
vacuum pump thereby eliminating losses due to friction on rotor
outer surface.
There are variety of applications that this device may be used. It
can be used as an air compressor, or to compress gases or various
kinds. Also, it can be used as the compressor stage in gas turbines
and jet engines; also, it can be used as the basic unit to form a
thrust generator by attaching a suitable nozzle to the rotor exit
opening, so that the gas is accelerated to high velocity and then
discharged.
Control for the unit may be provided by controlling the coolant
flow, or by having a control valve either at rotor entry or
exit.
Various controls, gages and governors may be used with the device
of this invention. They do not form a part of this invention and
are not further described herein.
The heat exchanger is shown in the drawings to be made of finned
tubing loops placed within said rotor cavity. There are numerous
other heat exchanger arrangements that can be used without
departing from the spirit of the invention.
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