U.S. patent application number 11/093138 was filed with the patent office on 2005-09-01 for rotary ram-in compressor.
Invention is credited to Awdalla, Essam T..
Application Number | 20050191173 11/093138 |
Document ID | / |
Family ID | 35239591 |
Filed Date | 2005-09-01 |
United States Patent
Application |
20050191173 |
Kind Code |
A1 |
Awdalla, Essam T. |
September 1, 2005 |
Rotary ram-in compressor
Abstract
A rotary ram-in compressor, used for pressurizing a gas into a
container, comprising: a stationary casing having at least one
inlet passage, and a receiver; at least one conduit for
communicating the receiver with the container; a drive shaft
supported for rotation in a given direction inside the casing; and
a rotor assembly housed inside the casing and including at least
one rotary ram-in compressor stage. In operation, gas is rammed
through the feeding channels of the rotary ram-in compressor to the
compressor's receiver, from which it flows through the conduit to
the container, wherein it collects. In preferred embodiments, valve
means for controlling the flow of gas through the conduit, and a
pressure sensor(s) for detecting the degree of rise in the pressure
of gas supplied by the rotary ram-in compressor, are also
provided.
Inventors: |
Awdalla, Essam T.; (Raleigh,
NC) |
Correspondence
Address: |
Essam T. Awdalla
2309 Myron Drive Apt. F
Raleigh
NC
27607
US
|
Family ID: |
35239591 |
Appl. No.: |
11/093138 |
Filed: |
March 29, 2005 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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11093138 |
Mar 29, 2005 |
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10669514 |
Sep 23, 2003 |
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6877951 |
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11093138 |
Mar 29, 2005 |
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11070914 |
Mar 3, 2005 |
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Current U.S.
Class: |
415/199.2 |
Current CPC
Class: |
F04D 17/02 20130101;
F04D 17/168 20130101; F01D 1/06 20130101 |
Class at
Publication: |
415/199.2 |
International
Class: |
F04D 029/54 |
Claims
What is claimed is:
1. A rotary ram-in compressor, used for pressurizing a gas into a
container, said rotary ram-in compressor comprising: a stationary
casing having at least one inlet passage for admission of the gas,
and a receiver; at least one conduit for communicating the said
receiver with the said container; a drive shaft supported for
rotation in a given direction inside the casing by an arrangement
of bearings, and extending to a drive receiving end located outside
the casing; and a rotor assembly housed inside the casing and
including a first disk secured for rotation with the drive shaft
and lying in a first plane transverse to the rotational axis of the
drive shaft; a second disk lying in a second plane transverse to
the rotational axis of the drive shaft, with the inner surfaces of
the two disks defining an annular space in-between; and a plurality
of vanes arranged circumferentially within said annular space, each
vane attached to both disks defining the annular space, each vane
has a leading edge, a trailing edge, a concave surface and a convex
surface, with the average angles of inclination of the successive
portions of the vane with respect to a plane comprising the
midpoint of the vane and perpendicular to a radial plane including
the rotational axis of the rotor and the midpoint of the vane
decreases preferably gradually from its leading edge towards its
trailing edge, within a range from about +18 to about -18 degrees,
the opposing parts of the surfaces of each two adjacent vanes along
with the opposing parts of the two disks' surfaces confined between
the opposing parts of the surfaces of each two adjacent vanes
defining a feeding channel between them, each feeding channel has
an inlet communicating with the compressor's inlet passage and an
outlet communicating with the compressor's receiver.
2. The rotary ram-in compressor of claim 1, wherein the cross
sectional area of the inlet of each of the said feeding channels
equals the cross sectional area of its outlet
3. The rotary ram-in compressor of claim 1, wherein each of the
said feeding channels converges from its inlet towards its
outlet
4. The rotary ram-in compressor of claim 1, wherein the said
conduit communicating the compressor's receiver with the container
is provided with valve means for controlling the flow of gas
through the conduit.
5. The rotary ram-in compressor of claim 1, which further comprises
at least one pressure sensor for detecting the degree of rise in
the pressure of gas supplied by the rotary ram-in compressor.
6. A rotary ram-in compressor, used for pressurizing a gas into a
container, said rotary ram-in compressor comprising: a stationary
casing having at least one inlet passage for admission of the gas,
and a receiver; at least one conduit for communicating the said
receiver with the said container; a drive shaft supported for
rotation in a given direction inside the casing by an arrangement
of bearings, and extending to a drive receiving end located outside
the casing; and a rotor assembly housed inside the casing and
functionally divided into at least two successive rotary ram-in
compressor stages, each of the rotary ram-in compressor stages
includes a first disk secured for rotation with the drive shaft and
lying in a first plane transverse to the rotational axis of the
drive shaft; a second disk lying in a second plane transverse to
the rotational axis of the drive shaft, with the inner surfaces of
the two disks defining an annular space in-between; and a plurality
of vanes arranged circumferentially within said annular space, each
vane attached to both disks defining the annular space, each vane
has a leading edge, a trailing edge, a concave surface and a convex
surface, with the average angles of inclination of the successive
portions of the vane with respect to a plane comprising the
midpoint of the vane and perpendicular to a radial plane including
the rotational axis of the rotor and the midpoint of the vane
decreases preferably gradually from its leading edge towards its
trailing edge, within a range from about +18 to about -18 degrees,
the opposing parts of the surfaces of each two adjacent vanes along
with the opposing parts of the two disks' surfaces confined between
the opposing parts of the surfaces of each two adjacent vanes
defining a feeding channel between them, each feeding channel has
an inlet and an outlet, with the inlets of the feeding channels of
the first rotary ram-in compressor stage communicating with the
said compressor's inlet passage, and with the outlets of the
feeding channels of the last rotary ram-in compressor stage
communicating with the said compressor's receiver.
7. The rotary ram-in compressor of claim 6, wherein the cross
sectional area of the inlet of each of the said feeding channels
equals the cross sectional area of its outlet
8. The rotary ram-in compressor of claim 6, wherein each of the
said feeding channels converges from its inlet towards its
outlet.
9. The rotary ram-in compressor of claim 6, wherein the said
conduit communicating the compressor's receiver with the container
is provided with valve means for controlling the flow of gas
through the conduit.
10. The rotary ram-in compressor of claim 6, which further
comprises at least one pressure sensor for detecting the degree of
rise in the pressure of gas supplied by the rotary ram-in
compressor.
Description
CROSS-REFERENCE TO RELATED APPLICATION(S)
[0001] This non-provisional utility patent application claims the
benefit of two prior filed co-pending non-provisional applications;
the present application is a continuation-in-part of U.S. patent
application Ser. No. 10/669,514, filed Sep. 23, 2003, and U.S.
patent application Ser. No. 11/070914, filed Mar. 3, 2005, which
are incorporated herein by reference in their entirety.
FIELD OF THE INVENTION
[0002] The present invention relates to a positive displacement
compressor and, more particularly, to a rotary positive
displacement compressor used for increasing the density and
pressure level of a gas within a container.
BACKGROUND OF THE INVENTION
[0003] Rotary positive displacement compressors are well known
devices, used in several fields to increase the density and
pressure level of a gas within a container. The main components of
a conventional rotary positive displacement compressor are a
casing; and a rotating element mounted within the casing, with
contact sealing means usually provided between the opposing
surfaces of the casing and the rotating element, which limits their
maximum allowable operating rotational speeds, and hence their
maximum provided mass flow rates, due to the developed friction
between the rubbing parts within them.
[0004] In some applications, e.g. pressurizing natural gas within
tanks for use by different types of land vehicles and the like, it
is desirable to have a rotary positive displacement compressor
having no rubbing parts within, to allow operating it at relatively
high rotational speeds, and thus providing high mass flow rate of
gas within it, to minimize the time needed for charging a given
tank with pressurized gas.
[0005] Thus, there is a need for a rotary positive displacement
compressor having no rubbing parts within, which allows its use in
the applications wherein relatively high mass flow rates are
needed.
SUMMARY OF THE INVENTION
[0006] The present invention provides a rotary positive
displacement compressor having no rubbing parts within, which
allows its use in the applications wherein relatively high mass
flow rates are needed.
[0007] Accordingly, the present invention provides a rotary ram-in
compressor, used for pressurizing a gas into a container, having a
plurality of feeding channels, moving at high speed, through which
the gas to be pressurized is rammed, followed by positive
displacement of the rammed in gas to a receiver, from which it
flows to the container.
[0008] In a preferred embodiment, the rotary ram-in compressor,
used for pressurizing a gas into a container, comprises a
stationary casing having at least one inlet passage, for admission
of the gas, and a receiver; at least one conduit for communicating
the said receiver with the said container wherein the pressurized
gas collects; a drive shaft supported for rotation in a given
direction inside the casing by an arrangement of bearings, and
extending to a drive receiving end located outside the casing; and
a rotor assembly housed inside the casing and including a first
disk secured for rotation with the drive shaft and lying in a first
plane transverse to the rotational axis of the drive shaft; a
second disk lying in a second plane transverse to the rotational
axis of the drive shaft, with the inner surfaces of the two disks
defining an annular space in-between; and a plurality of vanes
arranged circumferentially within said annular space, each vane
attached to both disks defining the annular space, each vane has a
leading edge, a trailing edge, a concave surface and a convex
surface, with the average angles of inclination of the successive
portions of the vane with respect to a plane comprising the
midpoint of the vane and perpendicular to a radial plane including
the rotational axis of the rotor and the midpoint of the vane
decreases preferably gradually from its leading edge towards its
trailing edge, within a range from about +18 to about -18 degrees,
the opposing parts of the surfaces of each two adjacent vanes along
with the opposing parts of the two disks' surfaces confined between
the opposing parts of the surfaces of each two adjacent vanes
defining a feeding channel between them, each feeding channel has
an inlet communicating with the compressor's inlet passage(s) and
an outlet communicating with the compressor's receiver.
[0009] In a preferred embodiment of the rotary ram in compressor of
the present invention, each two opposing surfaces, of those
defining each of the feeding channels between them, are parallel to
one another, with the cross-sectional area of the inlet of each of
the channels being equal to the cross sectional area of its
outlet.
[0010] In another preferred embodiment, in order to increase the
level of pressure rise provided by the rotary ram-in compressor of
the present invention, each of the feeding channels is slightly
converging from its inlet towards its outlet. The convergence of
the feeding channel is provided by designing the boundaries
confining the channel between them so that the axial width of the
channel and/or the width between the opposing parts of the surfaces
of the two adjacent vanes confining the channel between them
decrease preferably gradually from the inlet of the channel towards
its outlet, and hence, the cross-sectional area of the channel
decreases preferably gradually from its inlet towards its
outlet.
[0011] The gradual decrease in the axial width of the feeding
channel is provided by designing the part(s) of the surface(s) of
one (or both) of the disks related to the channel and confined
between the opposing parts of the surfaces of the two adjacent
vanes so that it is sloping preferably gradually from the inlet of
the channel towards its outlet. The gradual decrease in the width
between the opposing parts of the surfaces of the two adjacent
vanes is provided by designing the vanes with suitable angles of
inclination at their different parts, according to the desired rate
of convergence of the channel.
[0012] In operation, gas is rammed through the feeding channels of
the compressor, which displace it in a generally radially inward
direction (when a radial in-flowing rotary ram-in compressor is
used), or in a generally radially outward direction (when a radial
out-flowing rotary ram-in compressor is used), to the compressor's
receiver. The rammed in gas is first compressed by both the
pressurized gas collecting within the compressor's receiver and by
the reaction force developed on the free parts of the surfaces of
the vanes next to the outlets of the feeding channels, followed by
displacing the pressurized freshly introduced gas to the receiver,
by the free parts of the surfaces of the vanes. Then, the
pressurized gas flows through the conduit to the container, wherein
it collects, due to the pressure gradient between the compressor's
receiver and the container. As used herein, the free part of the
surface of a vane refers to the part of the surface of the vane
that is not opposed by any part of the surfaces of its adjacent
vanes.
[0013] In a preferred embodiment, the conduit used for
communicating the compressor's receiver with the container is
provided with valve means for controlling the flow of gas through
it. Once a predetermined pressure level is reached within the
compressor's receiver (to be determined experimentally for each
design), the driving means used to drive the compressor's rotor is
turned off, and the valve means controlling the flow of gas through
the conduit communicating the compressor's receiver with the
container is closed, to prevent raising the pressure level within
the compressor above the allowed design levels. In a preferred
embodiment, turning off the driving means and closing the valve
means are done manually. In another preferred embodiment, at least
one pressure sensor is used for detecting the degree of rise in the
pressure of gas supplied by the rotary ram-in compressor, either
within the compressor's receiver or within the said conduit, and
when a predetermined pressure level is reached, the sensor sends
correlative signals to turn off the driving means and to close the
valve means.
[0014] In another preferred embodiment, the rotary ram-in
compressor, used for pressurizing a gas into a container, comprises
a stationary casing having at least one inlet passage, for
admission of the gas, and a receiver; at least one conduit for
communicating the said receiver with the said container wherein the
pressurized gas collects; a drive shaft supported for rotation in a
given direction inside the casing by an arrangement of bearings,
and extending to a drive receiving end located outside the casing;
and a rotor assembly housed inside the casing. The rotor assembly
is functionally divided into at least two successive rotary ram-in
compressor stages, with each of the rotary ram-in compressor stages
including a first disk secured for rotation with the drive shaft
and lying in a first plane transverse to the rotational axis of the
drive shaft; a second disk lying in a second plane transverse to
the rotational axis of the drive shaft, with the inner surfaces of
the two disks defining an annular space in-between; and a plurality
of vanes arranged circumferentially within said annular space, each
vane attached to both disks defining the annular space, each vane
has a leading edge, a trailing edge, a concave surface and a convex
surface, with the average angles of inclination of the successive
portions of the vane with respect to a plane comprising the
midpoint of the vane and perpendicular to a radial plane including
the rotational axis of the rotor and the midpoint of the vane
decreases preferably gradually from its leading edge towards its
trailing edge, within a range from about +18 to about -18 degrees,
the opposing parts of the surfaces of each two adjacent vanes along
with the opposing parts of the two disks' surfaces confined between
the opposing parts of the surfaces of each two adjacent vanes
defining a feeding channel between them, each feeding channel has
an inlet and an outlet, with the inlets of the feeding channels of
the first rotary ram-in compressor stage communicating with the
compressor's inlet passage(s) and with the outlets of the feeding
channels of the last rotary ram-in compressor stage communicating
with the compressor's receiver.
[0015] In operation, when the rotor assembly is functionally
divided into two successive rotary ram-in compressor stages, the
gas is rammed through the feeding channels of the first rotary
ram-in compressor stage, which displace it in a generally radially
inward direction (when a radial in-flowing rotary ram-in compressor
is used), or in a generally radially outward direction (when a
radial out-flowing rotary ram-in compressor is used), to the inlets
of the feeding channels of the second rotary ram-in compressor
stage, through which it is rammed to the compressor's receiver,
from which it flows through the conduit to the container, wherein
it collects. When the rotor assembly is functionally divided into
more than two successive rotary ram-in compressor stages, the gas
is rammed through the feeding channels of the first rotary ram-in
compressor stage, which displace it in a generally radially inward
direction (when a radial in-flowing rotary ram-in compressor is
used), or in a generally radially outward direction (when a radial
out-flowing rotary ram-in compressor is used), followed by further
ramming of the gas through the feeding channels of the successive
intermediate rotary ram-in compressor stage(s), till it is rammed
through the feeding channels of the last rotary ram-in compressor
stage to the compressor's receiver, from which it flows through the
conduit to the container, wherein it collects.
[0016] In a preferred embodiment, the conduit used for
communicating the compressor's receiver with the container wherein
the pressurized gas collects is provided with valve means for
controlling the flow of gas through it. Once a predetermined
pressure level is reached within the compressor's receiver (to be
determined experimentally for each design), the driving means used
to drive the compressor's rotor is turned off, and the valve means
controlling the flow of gas through the conduit communicating the
compressor's receiver with the container is closed, to prevent
raising the pressure level within the compressor as described
herein before.
BREIF DESCRIPTION OF THE DRAWINGS
[0017] The description of the objects, features and advantages of
the present invention, will be more fully appreciated by reference
to the following detailed description of the exemplary embodiments
in accordance with the accompanying drawings, wherein:
[0018] FIG. 1 is a sectional view in a schematic representation of
an exemplary embodiment of a rotary ram-in compressor, used for
pressurizing a gas into a container, in accordance with the present
invention.
[0019] FIG. 2 is a cross sectional view, taken at the plane of line
2-2 in FIG. 1.
[0020] FIG. 3 is a cross sectional view, taken at the plane of line
3-3 in FIG. 1.
[0021] FIG. 4 is a sectional view in a schematic representation of
another exemplary embodiment of a rotary ram-in compressor, used
for pressurizing a gas into a container, in accordance with the
present invention.
[0022] FIGS. 5-10 are schematic representations of alternatives in
which the feeding channels confined between the opposing parts of
the surfaces of the adjacent vanes of a rotary ram-in compressor in
accordance with the present invention, may be designed.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0023] Prior filed U.S. patent application Ser. Nos. 10/669,514 and
11/070,914 provide rotary ram-in compressors having a plurality of
vanes attached to discs, with the opposing parts of each two
adjacent vanes defining a feeding channel in-between. In operation,
working gases are rammed through the feeding channels, followed by
positive displacement of the rammed-in gases to a receiver wherein
pressurized gases collect. The pressurized gases are actively swept
from the receiver by either a successive rotary ram-in compressor
or a successive rotary ram compressor (disclosed in the inventor's
earlier International Patent Application Serial number:
PCT/US00/17044, entitled "Rotary ram fluid pressurizing machine"),
which enables providing a flowing stream of pressurized gases, and
thus making them convenient for use in gas turbine engines, and the
like. However, this arrangement makes them inconvenient for use in
the applications wherein increasing the density and pressure level
of a gas within a container is needed. The present application
clearly defines a rotary ram-in compressor, wherein the pressurized
gas provided by the compressor collects within a container.
[0024] FIG. 1 is a sectional view in a schematic representation of
an exemplary embodiment of a rotary ram-in compressor, used for
pressurizing a gas into a container, in accordance with the present
invention.
[0025] The main components of the rotary ram-in compressor in this
embodiment are a stationary casing (21) having an inlet passage
(22) for admission of the gas to be pressurized (23), and a
receiver (24) wherein pressurized gases (25) collect; a conduit
(26) for communicating the receiver (24) with the said container
(not shown in the drawing for simplicity), wherein the pressurized
gas (25) collects; a drive shaft (27) supported for rotation in a
given direction inside the casing by an arrangement of bearings
(28), and extending to a drive receiving end located outside the
casing; and a rotor assembly housed inside the casing and secured
for rotation with the drive shaft (27). The rotor assembly is
functionally divided into four successive rotary ram-in compressor
stages (29,30,31,32), the first two rotary ram-in compressor stages
(29,30) include a disk (33) secured for rotation with the drive
shaft (27) and lying in planes transverse to the rotational axis of
the drive shaft; two disks (34,35) having large open centers and
widened rims, and lying in planes transverse to the rotational axis
of the drive shaft, with the opposing surfaces of each two adjacent
disks defining an annular space in-between; and plurality of vanes
(36,37) arranged circumferentially within said annular spaces, each
vane attached to both disks defining the annular space. The last
two rotary ram-in compressor stages (31,32) include a disk (38)
secured for rotation with the drive shaft (27) and lying in planes
transverse to the rotational axis of the drive shaft; two disks
(39,40) having large open centers and widened rims, and lying in
planes transverse to the rotational axis of the drive shaft, with
the opposing surfaces of each two adjacent disks defining an
annular space in-between; and plurality of vanes (41,42) arranged
circumferentially within said annular spaces, each vane attached to
both disks defining the annular space. As shown in FIG. 2 which is
a cross sectional view, taken at the plane of line 2-2 in FIG. 1,
each vane (36) has a leading edge (43), a trailing edge (44), a
concave surface (45) and a convex surface (46), with the average
angles of inclination of the successive portions of the vane with
respect to a plane comprising the midpoint of the vane and
perpendicular to a radial plane including the rotational axis of
the rotor and the midpoint of the vane decreases preferably
gradually from its leading edge towards its trailing edge, within a
range from about +2 to about -18 degrees, the opposing parts of the
surfaces of each two adjacent vanes along with the opposing parts
of the two disks' surfaces confined between the opposing parts of
the surfaces of each two adjacent vanes defining a feeding channel
(47) between them, each feeding channel (47) having an inlet (48)
communicating with the inlet passage of the compressor (22), and an
outlet (49) communicating with the space relatively radially
outward of the vanes (50), which forms the receiver of the first
rotary ram-in compressor stage and the inlet passage of the second
rotary ram-in compressor stage.
[0026] As also shown in FIG. 3 which is a cross sectional view,
taken at the plane of line 3-3 in FIG. 1, each of the vanes (37) of
the second rotary ram-in compressor stage (30) has a leading edge
(51), a trailing edge (52), a concave surface (53) and a convex
surface (54), with the average angles of inclination of the
successive portions of the vane with respect to a plane comprising
the midpoint of the vane and perpendicular to a radial plane
including the rotational axis of the rotor and the midpoint of the
vane decreases preferably gradually from its leading edge towards
its trailing edge, within a range from about +18 to about -2
degrees, the opposing parts of the surfaces of each two adjacent
vanes along with the opposing parts of the two disks' surfaces
confined between the opposing parts of the surfaces of each two
adjacent vanes defining a feeding channel (55) between them, each
feeding channel (55) having an inlet (56) communicating with the
inlet passage of the compressor stage (50), and an outlet (57)
communicating with the space relatively radially inward of the
vanes (58), which forms the receiver of the second rotary ram-in
compressor stage and the inlet passage of the third rotary ram-in
compressor stage.
[0027] In operation, gas is rammed through the feeding channels
(47) of the first rotary ram-in compressor stage (29), which
displace it in a generally radially outward direction, followed by
further ramming of the gas through the feeding channels of the two
successive intermediate rotary ram-in compressor stages (30,31),
till it is rammed through the feeding channels of the last rotary
ram-in compressor stage (32) to the compressor's receiver (24),
from which it flows through the conduit (26) to the container,
wherein it collects.
[0028] The embodiment also includes a valve (59) for controlling
the flow of gas through the conduit (26) communicating the receiver
(24) with the container, and a pressure sensor (60) for detecting
the degree of rise in the pressure of gas within the compressor's
receiver (24). Once a predetermined pressure level is reached
within the compressor's receiver (24), the pressure sensor (60)
sends correlative signals to a linear step motor (61) to close the
valve (59), and to turn off the driving means used for driving the
compressor's rotor (not shown in the drawing for simplicity).
[0029] The outer surface of the casing is provided with a plurality
of circumferential ribs (62) for cooling the pressurized gas
in-between the rotary ram-in compressor stages, to improve the
operating efficiency of the compressor.
[0030] FIG. 4 is a sectional view in a schematic representation of
another exemplary embodiment of a rotary ram-in compressor, used
for pressurizing a gas into a container, in accordance with the
present invention.
[0031] The main components of the rotary ram-in compressor in this
embodiment are a stationary casing (71) having an inlet passage
(72) for admission of the gas to be pressurized (73), and a
receiver (74) wherein pressurized gases (75) collect; a conduit
(76) for communicating the receiver (74) with the said container
(not shown in the drawing for simplicity), wherein the pressurized
gas (75) collects; a drive shaft (77) supported for rotation in a
given direction inside the casing by an arrangement of bearings
(78), and extending to a drive receiving end located outside the
casing; and a rotor assembly (79) housed inside the casing and
secured for rotation with the drive shaft (77), with the design and
operating principals of the rotor assembly (79) in this embodiment
being similar to that of the first rotary ram-in compressor stage
of the embodiment of FIGS. 1,2.
[0032] In operation, gas is rammed through the feeding channels the
compressor's rotor (79), which displace it in a generally radially
outward direction to the compressor's receiver (74), from which it
flows through the conduit (76) to the container, wherein it
collects.
[0033] The embodiment also includes a valve (80) for controlling
the flow of gas through the conduit (76) communicating the receiver
(74) with the container, and a pressure sensor (81) for detecting
the degree of rise in the pressure of gas within the compressor's
receiver (74). Once a predetermined pressure level is reached
within the compressor's receiver (74), the pressure sensor (80)
sends correlative signals to a stepping motor (82) to close the
valve (80), and to turn off the driving means used for driving the
compressor's rotor (not shown in the drawing for simplicity).
[0034] FIGS. 5-10 are schematic representations of alternatives in
which the feeding channels confined between the opposing parts of
the surfaces of the adjacent vanes of a rotary ram-in compressor in
accordance with the present invention, may be designed.
[0035] As discussed herein before, the boundaries of each of the
feeding channels are formed of the opposing parts of the surfaces
of the two adjacent vanes confining the channel between them (right
front and left rear surfaces of the drawings), and of the opposing
parts of the disks' surfaces related to the channel and confined
between the opposing parts of the surfaces of the two adjacent
vanes.
[0036] In FIG. 5 each two opposing surfaces (91,92 & 93,94), of
those defining the feeding channel between them, are parallel to
one another, with the cross-sectional area of the inlet of the
channel being equal to the cross sectional area of its outlet.
[0037] In FIG. 6 the feeding channel is slightly converging from
its inlet towards its outlet. The convergence of the feeding
channel is provided by designing the boundaries confining the
channel between them so that the axial width of the channel
decreases gradually from the inlet of the channel towards its
outlet, with the gradual decrease in the axial width of the channel
provided by designing one (95) of the opposing parts of the disks'
surfaces related to the channel and confined between the opposing
parts of the surfaces of the two adjacent vanes so that it is
gradually sloping from the inlet of the channel towards its
outlet.
[0038] In FIG. 7 the feeding channel is slightly converging from
its inlet towards its outlet. The convergence of the feeding
channel is provided by designing the boundaries confining the
channel between them so that the axial width of the channel
decreases gradually from the inlet of the channel towards its
outlet, with the gradual decrease in the axial width of the channel
provided by designing both (96,97) of the opposing parts of the
disks' surfaces related to the channel and confined between the
opposing parts of the surfaces of the two adjacent vanes so that
they are gradually sloping from the inlet of the channel towards
its outlet.
[0039] In FIG. 8 the feeding channel is slightly converging from
its inlet towards its outlet. The convergence of the feeding
channel is provided by designing the boundaries confining the
channel between them so that the axial width of the channel and the
width between the opposing parts of the surfaces of the two
adjacent vanes (99,100) confining the channel between them decrease
gradually from the inlet of the channel towards its outlet, with
the gradual decrease in the axial width of the channel provided by
designing one (98) of the opposing parts of the disks' surfaces
related to the channel and confined between the opposing parts of
the surfaces of the two adjacent vanes so that it is gradually
sloping from the inlet of the channel towards its outlet, and with
the gradual decrease in the width between the opposing parts of the
surfaces of the two adjacent vanes (99,100) provided by designing
the vanes with suitable angles of inclination at their different
parts, according to the desired angle of convergence of the
channel.
[0040] In FIG. 9 the feeding channel is slightly converging from
its inlet towards its outlet. The convergence of the feeding
channel is provided by designing the boundaries confining the
channel between them so that the axial width of the channel and the
width between the opposing parts of the surfaces of the two
adjacent vanes (103,104) confining the channel between them
decrease gradually from the inlet of the channel towards its
outlet, with the gradual decrease in the axial width of the channel
provided by designing both (101,102) of the opposing parts of the
disks' surfaces related to the channel and confined between the
opposing parts of the surfaces of the two adjacent vanes (103,104)
so that they are gradually sloping from the inlet of the channel
towards its outlet, and with the gradual decrease in the width
between the opposing parts of the surfaces of the two adjacent
vanes provided by designing the vanes with suitable angles of
inclination at their different parts, according to the desired
angle of convergence of the channel.
[0041] In FIG. 10 the feeding channel is slightly converging from
its inlet towards its outlet. The convergence of the feeding
channel is provided by designing the boundaries confining the
channel between them so that the width between the opposing parts
of the surfaces of the two adjacent vanes (105,106) confining the
channel between them decreases gradually from the inlet of the
channel towards its outlet, with the gradual decrease in the width
between the opposing parts of the surfaces of the two adjacent
vanes (105,106) provided by designing the vanes with suitable
angles of inclination at their different parts, according to the
desired angle of convergence of the channel.
* * * * *