U.S. patent number 3,650,636 [Application Number 05/035,112] was granted by the patent office on 1972-03-21 for rotary gas compressor.
Invention is credited to Michael Eskeli.
United States Patent |
3,650,636 |
Eskeli |
March 21, 1972 |
ROTARY GAS COMPRESSOR
Abstract
Method and apparatus for a compressor for compressing air, gases
and vapors isothermally using a liquid stream to compress the gas;
the liquid issuing from an impeller intermittently, with the gas
being entrained between these liquid pulses and compressed by the
liquid; the liquid having high kinetic energy when leaving the
impeller and in slowing the kinetic energy is converted to pressure
for both the liquid and entrained gas. Also, this compressor may be
used advantageously to compress vapors, wherein the liquid is the
same fluid as the gas, in which case condensation of the gas to the
liquid occurs, and work of compression is reduced.
Inventors: |
Eskeli; Michael (Fort Worth,
TX) |
Family
ID: |
21880718 |
Appl.
No.: |
05/035,112 |
Filed: |
May 6, 1970 |
Current U.S.
Class: |
417/78; 415/178;
416/179; 415/1; 415/182.1 |
Current CPC
Class: |
F04D
17/18 (20130101) |
Current International
Class: |
F04D
17/18 (20060101); F04D 17/00 (20060101); F04b
023/04 () |
Field of
Search: |
;415/1,72 ;417/78 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Husar; C. J.
Claims
What is claimed new is as follows:
1. A machine for compressing gaseous fluid and having the major
components of:
a. an impeller for accelerating a motive fluid to a high velocity;
said impeller having a plurality of passageways that comprise
respective initially converging sections as the passageways extend
outwardly from the center of said impeller and at least
non-converging sections exteriorly of said converging sections;
said non-converging sections defining the discharge passageways of
said impeller for more effective use of the available energy of
said motive fluid which has been accelerated to high velocity
whereby a motive fluid may be partially vaporized at the decreasing
pressure due to said high velocity to attain even higher velocities
for more effective entrainment of said gaseous fluid; and
b. a casing for the compressor, said casing including a diffuser
section for slowing the high speed mixture of fluids and converting
the kinetic energy of the stream to pressure, said diffuser section
containing a throat section where the mixing of the motive fluid
from the impeller and the vapor to be compressed occurs, and a
plurality of suitable annular spaces disposed peripherally
exteriorly of said impeller respectively for the entering gaseous
fluid and for the mixture of motive fluid and gaseous fluid and
respective apertures for the entering gaseous fluid and the
effluent mixture of fluids.
2. The machine of claim 1 wherein said at least non-converging
section is diverging.
Description
BACKGROUND OF THE INVENTION
This invention relates generally to devices for compressing gases,
air and vapors, in which a liquid is in intimate contact with the
gas or vapor to be compressed.
DESCRIPTION OF PRIOR ART
There are numerous devices and machines available for compressing a
gas or a vapor. In some of these machines a liquid is rotated
inside an eccentric casing, so that the machine rotor will cause
the liquid to pulsate and the space between the rotor blades is
increased or decreased, and this variation compresses the gas.
These machines are called liquid piston type machines. Another
device is the jet ejector compressor, where a stream of liquid or
gas is used to entrain the gas or vapor to be compressed, and the
kinetic energy of the stream is converted in a diverging nozzle to
a pressure.
The main disadvantage of the liquid piston type machine is its poor
efficiency, since the liquid is rotated in the machine and requires
relatively large power input for compressing the gas. In the
ejector compressor, the velocity of the liquid stream is limited
and it entrains poorly of any gas; therefore the efficiency of the
device is very poor. The available kinetic energy in the liquid
stream is high, but due to poor entrainment of the gas by the
liquid, results for the device are poor.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is an end view of the compressor casing, showing the
exterior.
FIG. 2 is a side view and a section of the casing and the impeller
of the compressor.
FIG. 3 is a side view and a section of the impeller, and
Fig. 4 is an end view of the impeller, showing the fluid
passages.
DESCRIPTION OF PREFERRED EMBODIMENTS
It is an object of this invention to provide a method and a device
for compressing gases or vapors essentially isothermally in which
the kinetic energy contained by a liquid stream is used to compress
said gas to a higher pressure where the liquid in slowing in speed
will increase its pressure and increase the pressure of the gas
being entrained in it. Also, it is an object of this invention to
provide a method and a device in which the gas may be partially or
fully be condensed in the liquid stream thereby lowering the work
of compression; this occurring when the gas or vapor being
compressed is the same fluid as the liquid; that is, the gas being
compressed is the vapor phase of the fluid, and the liquid being
used for as the motive fluid is the liquid phase of the fluid.
Referring to FIG. 1, there is shown an end view of the compressor.
10 is the compressor casing, 11 is the liquid inlet, 12 is the gas
or vapor inlet, and 13 is the outlet.
In FIG. 2, a side view of the compressor is shown. The impeller 22
is rotated by shaft 28, supported by bearings and sealed by packing
23 and stuffing box 24. Alternately a mechanical seal could be
used. The liquid that is used as the motive fluid enters through
opening 11, passes through the impeller 22 and leaves the impeller
at a high velocity and entering the throat section 21 and from
there the diffuser section 29 in the casing 10. After leaving the
diffuser at a higher pressure, and at a lower velocity, the gas and
liquid mixture is collected in annular space 30, and from there
passes out through opening 13. The liquid entrains gas from annular
space 31, and the gas enters the annular space from outside through
opening 12.
In FIG. 3, the impeller 22 is shown in more detail. 38 is the fluid
passage, and 36 is the opening for the drive shaft.
In FIG. 4, the impeller is shown, with 22 being the impeller and 38
being the fluid passage.
In operation, the compressor functions in a manner similar to a jet
ejector compressor. A motive fluid is accelerated in a passage in
the impeller to a high velocity; this corresponds to the motive
fluid nozzle in a jet ejector. However, the fluid stream issuing
from the impeller, when it rotates, is not continuous as seen by
the compressor casing, since in this particular instance, the
impeller has four fluid passages, with solid material between.
Therefore, the flow from impeller, as seen by the compressor
casing, is pulsating, with empty spaces between the high speed
liquid; these empty spaces being filled by the gas from the annular
spaces, item 31, FIG. 2, and the gas being rapidly moved with the
liquid to the outer annular space 30, and from there to discharge.
This pulsating action improves the entrainment of the gas by the
liquid, and more fully utilize the kinetic energy available in the
liquid stream.
The sizing of the fluid passages and the calculations pertaining to
same are fully described in thermodynamics literature for jet
ejectors and for steam injectors. The space of the passage 38 in
FIG. 3, would be either converging for liquids that do not vaporize
when leaving the passage; or the passage could be diverging at its
outlet for fluids that will vaporize either partially or fully when
leaving the passage. Of the non-vaporizing liquids, water would be
an example, and of the partially vaporizing types, butane would be
an example, both at atmospheric temperatures, and at low pressures.
As illustrated in FIGS. 2-4, passageways 38 comprise a converging
section nearest the center of the impeller but are at least
non-converging at the discharge section. Preferably, the at least
non-converging section is a diverging section for better taking
advantage of the energy available in the motive fluid to effect
higher effluent velocities thereof.
The fluid passages shown in FIG. 4, item 38, can be radial as
illustrated, or be forward or backward curved, depending on the
fluid used or the shape of the passages. Also, the throat section
21, FIG. 2, may have vanes of proper shape to prevent circular
motion of the fluid after it leaves the impeller. Vanes of this
type are commonly used in turbines and pumps and are not described
herein. Number of fluid passages in FIG. 4 is indicated to be four,
but this number would be as required when calculations are made
pertaining to the size of the passages, and the frequency of pulses
of liquid required to maintain suitable pressure and volume
relationships inside the compressor; also, the rotational speed of
the impeller would enter into these calculations.
Normally, the amount of liquid as compared to the amount of gas or
vapor, is large. Therefore, when compressing a gas, the heat of
compression from the gas is transferred to the liquid, resulting in
a temperature increase for the liquid, as well as the gas. This
temperature increase is much less than it would be for the gas
alone, resulting in nearly isothermal compression, and therefore
reduced work of compression, as compared to isentropic compression
that is often used in rotary compressors. Also, if a liquid that
will expand in the impeller is used, with an expanding fluid
passage, the temperature of the motive fluid is lowered, and the
fluid velocity greatly increased, resulting in much better
efficiency for the compressor; this is similar to the function of
converging-diverging diverging nozzles in jet ejectors.
The operation of the compressor may be inferred from the above
descriptive matter. A liquid source is connected to the impeller
inlet, and a gas or vapor source is connected to the gas inlet,
FIG. 1, 11 and 12, respectively. Discharge from the compressor is
from 13, FIG. 1. A suitable power source, such as an electric
motor, is connected to shaft 28, FIG. 2, causing the shaft to
rotate. The liquid is accelerated by the action of the impeller,
and as it passes through the annular space 31, FIG. 2, in pulsating
flow, it entrains the gas and carries it to annular space 30, and
from there to discharge.
Materials of construction for the compressor would be similar to
those used to make pumps for pumping liquids. Cast iron, steel,
bronze, brass, stainless steel and various plastics could be
used.
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