Improved Rotary Motor or Pump.
Year: 1897

page_text: PROVIDIONAL OF FUIFICATION.
Improved Rotary Motor or Pump.
I, GEORGE WESTINGHOUSE, of Westinghouse Building, Pittsburg, County of
Allegheny, and State of Pennsylvania, United States of America, Manufacturer,
do hereby declare the nature of this invention to be as follows:-
My invention relates to rotary motors or pumps and particularly to the class
of machines in which a drum mounted to rotate eccentrically within a cylindrical
cavity is provided with blades moving in radial slots in said drum, said blades
forming the pistons which are either acted upon by the motive fluid admitted
to the cavity and thereby rotate the shaft or when the shaft is rotated draw in
air or other fluid at one side of the cavity and discharge it at the other side of the
same so as to act as a pump.
The object of my invention is to construct a machine of the type men-
tioned which may either be operated as a motor by means of steam, compressed
air, or other fluid or which may be driven mechanically or otherwise as a pump.
A further object of my invention is to provide a pump which when rotated in
either direction acts to force the fluid in the same direction, that is to say, in
which the suction and delivery orifices are not changed when the direction of
rotation of the shaft is reversed.
The chief features of my invention are as follows:-
I provide between the outer edges of the blades and the internal periphery of
the cylinder one or more rotatable rings which I term balancing rings the
function of this ring or rings being to reduce the friction between the blades and
cylinder. I also provide special packing arrangements at the edges of the blades
and between the blades and the slots of the rotary drum in which said blades are
mounted. I further provide in recesses in the rotating drum rings located
between the inner edges of the blades which serve to maintain these blades in
proper position and their outer edges in contact with the inner periphery of the
cylinder. Further important features relate to the means I provide for lubricating
the moving parts of the machine, and to the utilisation of oil as a packing
medium. Another feature relates to the special devices for cooling the cylinder
when the machine is used as a pump.
My invention also comprises various constructions all details of which will be
hereinafter fully described.
In the accompanying drawings
Figure 1 is side elevation of the motor or pump constructed in accordance
with my invention.
Figure 2 is a plan of the machine also showing air and water reservoirs and
fluid conducting pipes.
Figure 3 is a plan partly sectional, a portion of the machine at one end being
broken away.
Figure 4 is a vertical longitudinal section and
Figures 5 to 8 are transverse sections on the lines V-V; VI-VI, VII—VII.
VIII VIII, of Figure 1 looking in the direction of the arrow in said figure.
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page_text: Figures 9 to 15 are views shewing details and hereinafter explained.
Figure 16 is a side elevation of a pump of modified construction.
Figure 17 is a plan partly sectional and
Figure 18 is a vertical longitudinal section of the pump shewn in Figure 16
looking from the rear.
Figures 19 to 21 are transverse sections on lines XIX-XIX, XX-XX, and
XXI-XXI Figure 16 looking in the direction of the arrow Figure 16.
Figure 22 is a diagrammatic plan view of a railway vehicle shewing an air
pump, storage cylinder valves, pipes, and other parts forming an air brake
equipment.
Figures 3 to 13 and 17 to 21 are drawn to a larger scale than the other figures
of the drawings, and similar parts are denoted by the same reference numerals
throughout.
The apparatus illustrated in Figures 1 to 16 of the drawings is intended for
and will be described as an air compressing and storing apparatus, but it is to be
understood that the invention is not limited to this particular use.
The air compressor is of the compound double cylinder type and comprises a
low pressure cylinder 1, a high pressure cylinder 2, and an intermediate annular
plate 3, 4 is a head bolted to the end of the cylinder 1, and a similar head 5 is
bolted to the end of the cylinder 2 by bolts 6 which may extend through the
cylinder 2 and plate 3 into the cylinder 1. 7 is the base which may be cast in
one piece with the cylinder 1 if desired. Within the base 7 is a cavity. 8 having
an opening 9, and immediately above said opening is a valve seating 10 forming
the upper end of a tube 11, this tube descending nearly to the bottom of the
chamber 8. 12 is an upwardly opening valve at the top of the tube 11, and
above said valve is a cavity 13 which communicates with a chamber 14 (see
Figures 3 and 7) located in the side-wall of the cylinder 1 and extending the
entire length of the same. Chamber 13 is closed by a screw cap 15 having a
guiding socket for the stem of the valve 12. The chamber 14 communicates
with the interior of the cylinder 1 by ports 16 as shewn in Figure 3, and in the
opposite wall of the cylinder is a chamber 17 communicating with the interior
by ports 18. Said chamber 17 communicates either through the plate 3
as shewn, or through an external tube with a similar chamber 17 in the
wall of the cylinder 2, the latter chamber communicating with the interior of
cylinder 2 by ports 19. 20 is a chamber located in the wall of cylinder 2 similar
to chamber 14 and communicating with the interior of this cylinder by ports 21
and having an orifice 53 in its outer wall. The walls of the cylinders contain
other cavities as will be seen from Figures 6 to 8 namely the chambers 22 and 23
in the upper part which are connected by a passage 24 and chambers 25 and 26
in the lower part connected by passage 27. The chambers 23 and 25 are also
connected by passage 28, and it will be seen on reference to Figure 1 that this
latter passage is located at one end of the machine while the passages 24. and 27.
are located at the other end of the machine.
A shaft 29 extends from end to end of the machine and within the head 4 has
secured to it or formed in one piece with itself a plate 30 which plate also forms
part of an enlargement 31 supported by a series of bearing rollers 32 contained
in a cage 33 in the usual manner; the part of the head 4 containing the rollers
is preferably lined with a steel bushing 34. On the outer end of the shaft 29
a driving pulley 73 is provided and to prevent any egress of air from the cylinder
and at the same time avoid friction between the shaft and head I provide suit-
able packing rings 35 some of which are secured to the head while others of
slightly less external diameter are secured to and rotate with the shaft. Other
forms of packing may be used.
35 is a passage leading from the packing rings 35 to the chamber 8 by which
any oil which passes the bearings, flows back into said chamber.
Upon the shaft 29 is mounted a drum 37 provided with slots in which ara

page_text: located the blades 38 which move radially in the slots as the drum rotates. The
number of slots and blades may of course be varied, and the radial arrangement
Each blade is pro-
of the same though preferable is not absolutely necessary.
vided at its outer edge with radially movable packing strips 38" clearly shewn
in Figures 9 and 10 which shew respectively the end elevation and a part sectional
elevation of a portion of the drum and one of the blades. These strips automa-
tically adjust themselves by centrifugal force so as to make close contact with
the inner periphery of the cylinder. Recesses or cavities are provided at the end
of the drum 37 adjacent to its shaft in which are placed rings 39, said rings being
located between the inner edges of the blades 38 serve to maintain the blades in
position and their outer edges very nearly in contact with the inner periphery
of the cylinder.
In order to prevent leakage past the blades from the cylinder into the cavities
within the drum, and at the same time to permit of the free movement of the
blades in their slots I provide triangular packing strips 386 in recesses in the
head at one
drum on each side of each blade, each strip having a
end as shewn in Figure 11 which is a perspective view of one pair of strips. It
will be readily observed that the end of each strip which projects beyond the
blade enclosed between the pair of strips is flush and rests laterally against the
head of the other strip of the pair. The centrifugal force when the drum is in
motion tends to force these strips radially outwards from the shaft, and by
reason of the inclination of their outer sides the strips forming each pair are
pressed towards each other against the enclosed blade thereby affording a good
packing without materially impeding the movement of the blade. The drum
is provided at each end with an annular centring tongue 37 engaging in corre-
sponding grooves in the plates 30 and 46 at the ends of the drum. Said drums
are provided with recesses for the heads and projecting ends of the packing
strips 38b above mentioned.
40 is what I call a balancing ring which is located in the cylinder midway of
its ends in recesses 41 in the blades 38, the external diameter of the balancing
ring being slightly less than the bore of the cylinder, and the depth of each
recess 41 being less than the thickness of the ring. By this arrangement the
ring can rotate freely in the cylinder and at the same time the blades 38 bear
against the ring instead of against the surface of the cylinder. The drum 37 is
provided with a circumferential recess 42 similar to the recesses 41 in the
blades 38.
It will be understood that the annular recess for the reception of the balancing
ring may be in the cylinder instead of in the drum and blades as described. It
would also obviously be feasible to locate the ring partly in a recess in the
cylinder and partly in recesses in the drum and blades. More than one ring may
also be employed if desired.
The exterior surface of the balancing ring is provided with packing rings 43
and with a groove 44 which communicates with chamber 17 by the passage 45
(see Figure 3). Since the packing rings 43 prevent the passage of fluid from the
interior of the cylinder to the space between said rings, and the groove 44 is by
45 connected with the chamber 17 which as will be hereinafter described
passage
is a high pressure chamber of the pump, a substantial equality of pressure will
be maintained between the ring 40 and the contiguous surface of the cylinder
throughout the circumference. Furthermore, the balancing ring is so propor-
tioned with reference to the centrifugal force exerted upon it by the blades when
the drum is rotated that the various forces acting upon the ring within the
cylinder are balanced and no appreciable pressure is exerted by the ring upon
the periphery of the cylinder at any point. By these means the friction between
the balancing ring and the cylinder is reduced and the former can rotate freely
between the inner surface of the cylinder and the blades. As a general rule the
ring rotates at a somewhat less speed than that at which the drum is rotated.
The portion of the shaft 29 which passes through the cylinder 2 is provided

page_text: with a drum 37 which does not differ except in length from the drum 37 of
cylinder 1. The bore of the cylinder 2 is, however, for convenience and simplicity
of construction so located with reference to the shaft 29 that the eccentricity is
opposite to that of the cylinder 1. The blades with their packing strips, the
balancing ring, and other appurtenances of the drum are similar to those herein
before described with reference to cylinder 1.
46 is a plate of the same thickness as the annular partition plate 3 and the
same diameter as the drums 37 and 37ª. Said plate is mounted upon the shaft 29
between the drums and is provided with three packing rings 47 and two annular
grooves 48. These grooves are located between the packing rings 47 and com-
municate by passage 49 with the interior of the drums 37 and 37 (see Figures 3
and 4). The groove 48 which communicates with the drum 37 may communicate
with chamber 17 by means of a passage 48" so that an equilibrium of fluid pressure
may be established between the interiors of said drum and said chamber. A
plate 30 with a reduced portion 31ª similar to plate 30 and part 31 is removably
secured to the shaft 29 at the end of the drum 37" and a nut (not shewn in the
drawings) is provided which clamps the drums, plate 46, plate 30, and plate 30º
rigidly to the shaft. The bearings and other appurtenances contained in the
head 5 are similar to those at the other end of the pump contained in head 4.
Referring more particularly to Figures 2 and 12 to 15, 52 is an air reservoir
which receives air under pressure from the pump through a pipe 53 having a
check valve 54. 55 is a similar pipe leading from reservoir 52 to the annular
plate 3 and is connected with the grooves 48 in the plate 46 through passages 56
and 57 in the latter of which are located screw plugs 58 (see Figure 3) for regu-
lating the amount of oil supplied to the pump. 59 is the inlet pipe or suction
connected to the inlet opening 9 (see Figure 7) which is preferably provided with
a check valve 60. In order to prevent a back flow of air and oil from the reser-
voir 52 when the pump is not in operation I preferably provide a combined air
and oil check valve shewn in Figures 12 and 13 of which Figure 12 is a vertical
section, and Figure 13 a plan. A chamber 61 is formed in a two part casting 62
bolted to the underside of the reservoir 52 as indicated in Figures 14 and 15.
To the underpart of the casting the tubes 53 and 55 are connected by inlet open-
ings 63 and 64, and the chamber 61 communicates with the interior of the
reservoir 52 by an air tube 65 and oil tube 66, the former of which projects into
the reservoir a short distance above the floor thereof. The upper end of the inlet
pipe 63 is normally closed by a valve 67 seated at the bottom of a cylindrical
recess 67 The valve has therefore to rise a considerable distance before air can
pass from the inlet 63 to the chamber 61 and into the reservoir. The upper end
of the opening 64 is also normally closed by a valve 68 which is pivoted to a
lever 69, one end of which is pivoted to the casting 62, the other end of said lever
being located above and nearly in contact with valve 67. The action of this
device is as follows, that is to say, when the pump stops, valve 67 drops to its
Beat and permits the free end of lever 69 to fall, allowing valve 68 to close. The
air and oil which has been pumped into the reservoir is thereby retained.
The arrangements for circulating water through the chambers in the pump
walls when necessary are shewn in Figures 2, 5, and 6 in which 70 is a water
tank connected at its top to chamber 22 in the pump walls by means of a pipe 71
and at its bottom with chamber 26 by pipe 72. The circulation of the water is
as follows: From the tank through pipe 72, chamber 26, pàssage 27, chamber 25,
passage 28, chamber 23, passage 24, chamber 22, and thence to the top of the 5
tank again by pipe 71. The circulation in this particular apparatus is effected
by reason of the heat generated in the machine, but any suitable circulating
arrangements may be provided if desired.
I will now describe the operation of the machine when employed for pumping
and compressing air. The shaft 29 is rotated in the direction of the arrow shewn 5
in Figures 6 to 8 by means of a belt on the pulley 73 or by any suitable means
and air is drawn in through pipe. 59. and valve 60, inlet 9, vertical tube. 11,

page_text: valve 12, chambers 13 and 14, and ports 16 into cylinder 1. This air forced by
the blades 38 through the outlet ports 18 into the chamber 17 and drawn
from thence through the ports 19 into the upper portion of the high pressure
cylinder 2, being delivered through ports 21, chamber 20 and pipe 53 into the air
reservoir 52. The air valve 67 (see Figure 12) will of course be raised by the
air pressure, and through the medium of lever 69 raises valve 68, oil can then
flow out of reservoir 52, through tube 66, 64 and pipe 55 and passages 56 and 57
into the grooves 48 in the plate 46, and thence through passages 49 into the
adjacent cavities in the drums 37 and 37. The centrifugal force due to the
rotation of the drums will then force the oil between the sides of the blades against
the air pressure in the cylinders, but a portion of the oil will find its way into the
cylinders and be carried along with the air to the reservoir 52 again. It will
therefore be seen that the oil is used over and over again, and has the effect of
making the pumping apparatus substantially air tight, while at the same time
thoroughly lubricating every part so as to reduce the friction to a minimum.
Air and oil are also forced to a greater or less extent from the chambers 17 and 20
through the passages 45 into the grooves 44 of the balancing rings 40, and serves
to lubricate the outer surfaces of the rings. Said passages lead preferably as
shewn to the points of highest pressure with reference to the respective cylinders.
As hereinbefore mentioned the balancing rings 40 will rotate with the drums
and blades but at a less speed, and on account of the balancing of pressure all
the parts will rotate in the cylinders with very little friction. Any oil which
passes beyond the packing rings in the plates 30 and 30b will fleback through
the passages 73 and 74 into chambers 14 and 20 as indicated in Figure 3, and
any oil which passes beyond the bearing rings 35 will flow back through the
channel 35 into the chamber 8 as shewn in Figure 4. The accumulation of oil
in chamber 8 will be drawn up together with the air through the tube 11 and
returned into the machine. The cylinders are kept cool by the circulation of
water. in the passages 22 to 26 as hereinabove described.
It will be readily understood that the machine herein before described can be
used as a motor or engine, and may be operated by steam or compressed air or
other fluid, the valve 12 at the top of the pipe 11 being removed, and the operating
fluid being supplied under pressure in the reverse direction to the hereinbefore
described. When driven by air the oil packing may be omitted or it may be
provided for by constantly collecting the oil which passes out the exhaust of the
engine and pumping it back to serve as a packing. When driven by steam, water
under considerable pressure such as results from condensation may be used for
packing purposes, or such packing may be dispensed with.
Referring now to Figures 16 to 21 which illustrate. a pump of modified con-
struction 80 is a cylindrical outer casing having an air inlet 81 at one end and
closed at the other end by a cover 82.
Bolted to. the inner side of the cover 82
is a casing 83 having a head 84 similar to the head 4 of the figures previously
described. The casing 80 is provided at each side with a long horizontally pro-
jecting lug 85 by which the apparatus may be supported. The side walls of the
inner casing 83 are provided at the bottom with two chambers 86 and 87 separated
by a partition 88, and at the top with a single chamber 89. The chamber 86
communicates with a chamber 89 on either side through valves 90 and 91, the
cavity 92 between the valves communicating with the interior of the cylinder
through the ports 93, and all the valves are arranged to open upwardly as shewn.
Shaft 29 is supported in the heads 84 and 82 in a similar manner to that herein-.
above described with reference to Figure 1 of the drawing, and is provided with
a drum, blades, balancing ring, and other appurtenances as hereinabove described.
The chamber 89 communicates through a channel in the head 32 with a pipe 94
which forms the delivery orifice of the pump.
The operation of the pump is as follows:-
When the shaft 29 is rotated for example in the direction of the arrow shewn
Licure 21 a nartial vacuum will be created in the right hand chamber 92. hv.'

page_text: Air
means of which the valve 91 will be held to its seat and valve 90 be raised.
will then be drawn from the chamber 86 which is in communication with the
atmosphere through the orifices 95 and 81 and passing through the right hand
chamber 92 into the cylinder will be forced into the left hand chamber 92 causing
the left hand valve 90 to be held down, while left hand valve 91 is raised. The
air will then pass into the chamber 89 and into the delivery pipe 94.
If now the shaft 29 be rotated in the opposite direction to that hereinabove
indicated air will be drawn from the chamber 86 through the left hand valve 90
and cavity 92 and be forced by the blades into the right hand chamber 92
through the right hand valve 91 into the chamber 89. It will therefore be seen.
that the pump adjusts itself automatically so as to force air always in the same
direction through the delivery pipe 94 irrespective of the direction of rotation
of the shaft 29.
The arrangement for lubricating the blades and moving parts of the pump
will now be described with reference to Figure 22 which illustrates the applica-
tion of a pump such as that above described to an air brake. The pump may be
connected by a belt 96 to one of the motors 97 which drives the vehicle. 98 is
an air reservoir connected by a pipe 99 to the delivery orifice 94 of the pump.
Said reservoir 98 preferably contains a small supply of oil, which as the air is
pumped into the tank is forced out through the pipe 100 into the chamber 87
(see Figure 18) and thence passes through the passages 101 and 49 into the
interior of the drum 37, whence it is forced as herein before described through
the radial slots through the other moving parts of the apparatus. The oil which
collects is returned by the pipes 35" to the chamber 86.
The air pipes, valves, and other parts of the brake apparatus may be of the
usual description.
I desire it to be understood that although I have herein described and illus-
trated practical embodiments of my invention the details of construction and
arrangements of the parts may be varied within considerable limits without
departing from the spirit and scope of my invention.
Dated the 11th day of November 1807
W. P. THOMPSON & Co.<
322, High Holborn, W.C., Patent Agents for the Applicant.
Improved Rotary Motor or Pump.
I, GEORGE WESTINGHOUSE, of Westinghouse Building, Pittsburg, County of
Allegheny, and State of Pennsylvania, United States of America, Manufacturer,
do hereby declare the nature of this invention and in what manner the same is to
be performed, to be particularly described and ascertained in and by the following
statement:―
My invention relates to rotary motors or pumps and particularly to the class
of machines in which a drum mounted to rotate eccentrically within a cylindrical
cavity is provided with blades moving in radial slots in said drum, said blades
forming the pistons which are either acted upon by the motive fluid admitted
to the cavity and thereby rotate the shaft or when the shaft is rotated draw in
air or other fluid at one side of the cavity and discharge it at the other side of the
same so as to act as a pump.
The object of my invention is to construct an improved machine of the type men-
tioned which may either be operated as a motor by means of steam, compressed

page_text: air, or other fluid or which may be driven mechanically or otherwise as a pump.
A further object of my invention is to provide a pump which when rotated in
either direction acts to force the fluid in the same direction, that is to say, in
which the suction and delivery orifices are not changed when the direction of
rotation of the shaft is reversed.
The chief features of my invention are as follows:
The blades or pistons are each made in two parts the inner or main portion
being encircled by one or more rings, which I term balancing rings; the opera-
tion of this ring or rings is to restrain the outward movement of the main portion
of the blade under the action of the fluid pressure so as to prevent undue pressure
on the internal periphery of the cylinder, at the same time the outer portion of
the blades is free to move radially outward and press against the interior surface
of the cylinder, such pressure is however very moderate owing to the small mass of
the outer portions of the blades. Further important features relate to the means I
provide for lubricating the moving parts of the machine, and to the utilization of
oil or liquid lubricant as a packing medium, as will hereinafter fully set forth.
My invention also comprises various constructions the details of which will be
hereinafter described.
In the accompanying drawings,
Figure 1 is a side elevation of the motor or pump constructed in accordance
with my invention.
Figure 2 is a plan of the machine also showing air and water reservoirs and
fluid conducting pipes.
Figure 3 is a plan partly sectional, a portion of the machine at one end being
broken away;
Figure 4 is a vertical longitudinal section and
Figures 5 to 8 are transverse sections on the lines V-V, VI-VI, VII—VII,
VIII-VIII, of Figure 1 looking in the direction of the arrow in said figure.
Figures 9 to 15 are views shewing details and hereinafter explained.
Figure 16 is a side elevation of a pump of modified construction.
Figure 17 is a plan partly sectional and
Figure 18 is a vertical longitudinal section of the pump shewn in Figure 16
looking from the rear.
Figures 19 to 21 are transverse sections on lines XIX-XIX, XX-XX, and
XXI-XXI Figure 16 looking in the direction of the arrow Figure 16.
Figure 22 is a diagrammatic plan view of a railway vehicle shewing an air
pump, storage cylinder, valves, pipes, and other parts forming an air brake
equipment.
Figures 3 to 13 and 17 to 21 are drawn to a larger scale than the other figures
of the drawings, and similar parts are denoted by the same reference numerals
throughout.
The apparatus illustrated in Figures 1 to 15 of the drawings is intended for
and will be described as an air compressing and storing apparatus, but it is to be
understood that the invention is not limited to this particular use.
The air compressor is of the compound double cylinder type and comprises a
low pressure cylinder 1 a high pressure cylinder 2, and an intermediate annular
plate 3, 4 is a head bolted to the end of the cylinder 1, and a similar head 5 is
bolted to the end of the cylinder 2 by bolts 6 which may extend through the
cylinder 2 and plate 3 into the cylinder 1. 7 is the base which may be cast in
one piece with the cylinder 1 if desired. Within the base 7 is a cavity 8 having
an opening 9, and immediately above said opening is a valve seating 10 forming
the upper end of a tube 11, this tube descending nearly to the bottom of the
chamber 8. 12 is an upwardly opening valve at the top. of the tube 11, and
above said valve is a cavity 13 which communicates with a chamber 14 (see
Figures 3 and 7) located in the side wall of the cylinder 1 and extending the
entire length of the same. Chamber 13 is closed by a screw cap 15 having a
guiding socket for the stem of the valve 12. The chamber 14 communicates

page_text: with the interior of the cylinder 1 by ports 16 as shewn in Figure 3, and in the
opposite wall of the cylinder is a chamber 17 communicating with the interior
of the cylinder by ports 18. Said chamber 17 communicates either through the
plate 3 as shewn or through an external tube with a similar chamber 17" in the
wall of the cylinder 2, the latter chamber communicating with the interior of
the cylinder 2 by ports 19. 20 is a chamber located in the wall of cylinder 2 similar
to chamber 14 and communicating with the interior of this cylinder by ports 21
and having an orifice 53 in its outer wall. The walls of the cylinders contain
other cavities as will be seen from Figures 6 to 8, namely, the chambers 22 and 23
in the upper part which are connected by a passage 24 and chambers 25 and 26
in the lower part connected by passage 27. The chambers 23 and 25 are also
connected by passage 28, and it will be seen on reference to Figure 1 that this
latter passage is located at one end of the machine while the passages 24 and 27
are located at the other end of the machine.
A shaft 29 extends from end to end of the machine and within the head 4 has
secured to it or formed in one piece with itself a plate 30 which plate also forms
part of an enlargement 31 supported by a series of bearing rollers 32 contained
in a cage 33 in the usual manner; the part of the head 4 containing the rollers
is preferably lined with a steel bushing 34. On the outer end of the shaft 29
a driving pulley 73 is provided and to prevent any egress of air from the cylinder
and at the same time avoid friction between the shaft and head I provide suit-
able packing rings 35 some of which are secured to the head while others of
slightly less external diameter are secured to and rotate with the shaft. Other
forms of packing may be used.
-
35 is a passage leading from the packing rings 35 to the chamber 8 by which
any oil which passes the bearings flows back into said chamber.
Upon the shaft 29 is mounted a drum 37 provided with slots in which are
located the blades whch move radially in the slots as the drum rotates. The
number of slots and blades may of course be varied, and the radial arrangement of
the same though preferable is not absolutely necessary. Each blade consists of
two parts, an inner main portion 38 and an outer lighter portion 38" as clearly
shewn in Figures 9 and 10 which shew respectively the end elevation and a part
sectional elevation of a portion of the drum and one of the blades. The said outer
portions 38 automatically adjust themselves by centrifugal force so as to make
close contact with the inner periphery of the cylinder. Recesses or cavities are
provided at the end of the drum 37 adjacent to its shaft in which are placed
rings 39, which are located between the inner edges of the blades and serve to
maintain the same in position.
·
one
In order to prevent leakage past the blades from the cylinder into the cavities
within the drum, and at the same time to permit of the free movement of the
blades in their slots I provide triangular packing strips 38b in recesses in the
drum on each side of each blade each strip having a head at
end as shewn in Figure 11 which is a perspective view of one pair of strips. It
will be readily observed that the end of each strip which projects beyond the
blade enclosed between the pair of strips is flush and rests laterally against the
head of the other strips of the pair. The centrifugal force when the drum is in
motion tends to force the strips radially outwards from the shaft, and by
reason of the inclination of their outer sides the strips forming each pair are
pressed towards each other against the enclosed blade thereby affording a good
packing without materially impeding the movement of the blade. The drum
is provided at each end with an annular centring tongue 37b engaging in corre-
sponding grooves in the plates 30 and 46 at the ends of the drum. Said drums
are provided with recesses for the heads and projecting ends of the packing
strips 38b above mentioned.
The inner portions 38 of the blades are encircled by a ring 40 hereinafter called
a balancing ring which is located in the cylinder midway of its ends in recesses 41
in the blades. The external diameter of the balancing ring is slightly less than

page_text: the bore of the cylinder, and the depth of each recess 41 is. less than the thickness.
of the ring. By this arrangement the ring can rotate freely in the cylinder and.
at the same time the inner parts 38 of the blades bear against the ring. instead.
of against the surface of the cylinder. The drum 37 is provided with a circum-
ferential recess 42 similar to the recesses 41 in the inner portions of the blades..
It will be understood that the annular recess for the reception of the balancing
ring may be in the cylinder instead of in the drum and blades as described. It
would also obviously be feasible to locate the ring partly in a recess in the
cylinder and partly in recesses in the drum and blades. More than one ring may
also be employed if desired.
The exterior surface of the balancing ring is provided with packing rings 43
and with a groove 44 which communicates with chamber 17 by the passage 45
(see Figure 3). Since the packing rings 43 prevent the passage of fluid from the
interior of the cylinder to the space between said rings, and the groove 44 is by
passage 45 connected with the chamber 17 which as will be hereinafter described
is a high pressure chamber of the pump, a substantial equality of pressure will
be maintained between the ring 40 and the contiguous surface of the cylinder
throughout the circumference.
With reference to the pressures internal and external which act upon the
balancing ring 40, the pressure existing in the central space of each drum is as
will be hereinafter shewn equal to the maximum pressure occurring in the
cylinder and this pressure acts upon the inner end surfaces of all the blades 38.
Upon the outer ends of the blades there is an inward pressure which varies accord-
ing to the position of the blades. If we consider the first cylinder for example,
a section of which is shewn in Figure 7, the inward pressure acting upon the
outer ends of the blades 38 will be least when said blades are opposite the inlet
chamber 14, and will increase until in the case of the blade which
opposite the
outlet ports 19, the inward pressure will be equal to the outward pressure; conse-
quently on the whole there will be a resulting pressure outwardly towards the
inlet side of the cylinder and the ring 40 will press more heavily upon that side
of the cylinder than upon the other side. With regard to the pressures to which
the ring is subject owing to centrifugal force, the ring itself is rotating in a cir-
cular path and the centrifugal force will act equally all round and will merely
act as a force tending to burst the ring. There is also the centrifugal force of the
blades this is also balanced or at any rate is equal in all directions as the blades are
rotating in a circular path. There then remains the forces due to air pressure
on the inside of the ring 40, and those due to the pressure on the outside of said
ring, namely, in the groove 44. Dealing with the latter it is obvious that it is
equal all round the ring and simply adds strength thereto counteracting the
bursting pressure due to the centrifugal forces of the ring and blades. With
regard to the air pressures on the inside of the ring the following point requires
careful noting. Referring to Figure 4 which shews a section of the ring it is to
be observed that the air pressure on the inside of the ring whatever it be, is
balanced by the air pressure on the outside of the ring except at that part between
the packing rings 43, consequently the unbalanced part of the internal pressure
has to be taken over a ring equal in width to the distance between said packing
rings only. This pressure will be least in the suction part of the cylinder and
greatest in the delivery part of the cylinder, consequently there will be a tendency
on the part of this pressure to force the ring to the delivery side of the cylinder.
By varying the distance between the packing rings it is obvious that we can vary
this resultant force, and it will be readily seen that by choosing a proper distance
between the packing rings this force which tends to push the ring towards the
delivery side of the cylinder may be made to exactly compensate the unbalanced
force due to the air pressure on the blades 38, which tend to force the ring to the
suction side of the cylinder; consequently all the forces due both to air pressures
and centrifugal force will be in equilibrium. As a general rule the ring rotates
at a somewhat less speed than that at which the drum is rotated. The portion of

page_text: the shaft 29 which passes through the cylinder 2 is provided with a drum 37ª
which does not differ except in length from the drum 37 of cylinder 1. The bore
of the cylinder 2 is, however, for convenience and simplicity of construction so
located with reference to the shaft 29 that the eccentricity is opposite to that of
the cylinder 1. The blades with their packing strips, the balancing ring, and
other appurtenances of the drum are similar to those herein before described with
reference to cylinder 1.
46 is a plate of the same thickness as the annular partition plate 3 and the
same diameter as the drums 37 and 37. Said plate is mounted upon the shaft 29
between the drums and is provided with three packing rings 47 and two annular
grooves 48.
These grooves are located between the packing rings 47 and com-
municate by passages 49 with the interior of the drums 37 and 37 (see Figures 3
and 4). The groove 48 which communicates with the drum 37 may communicate
with chamber 17 by means of a passage 48° so that an equilibrium of fluid pressure
may be established between the interiors of said drum and said chamber. A
plate 30 with a reduced portion 31" similar to plate 30 and part 31 is removably
secured to the shaft 29 at the end of the drum 37" and a nut (not shewn in the
drawings) is provided which clamps the drums, plate 46, plate 30, and plate 30
rigidly to the shaft. The bearings and other appurtenances contained in the
head 5 are similar to those at the other end of the puinp contained in head 4.
Referring more particularly to Figures 2 and 12 to 15, 52 is an air reservoir
which receives air under pressure from the pump through a pipe 53 having a
check valve 54. 55 is a similar pipe leading from reservoir 52 to the annular
plate 3 and is connected with the grooves 48 in the plate 46 through passages 50
and 57 in the latter of which are located screw plugs 58 (see Figure 3) for regu-
lating the amount of oil supplied to the pump. 59 is the inlet pipe or suction
connected to the inlet opening 9 (see Figure 7) which is preferably provided with
a check valve 60. In order to prevent a back flow of air and oil from the reser-
voir 52 when the pump is not in operation I preferably provide a combined air
and oil check valve shewn in Figures 12 and 13 of which Figure 12 is a vertical
section, and Figure 13 a plan. A chamber 61 is formed in a two part casting 62
bolted to the underside of the reservoir 52 as indicated in Figures 14 and 15.
To the underpart of the casting the tubes 53 and 55 are connected by inlet open-
ings 63 and 64, and the chamber 61 communicates with the interior of the
reservoir 52 by an air tube 65 and oil tube 66, the former of which projects into
the reservoir a short distance above the floor thereof. The upper end of the inle
pipe 63 is normally closed by a valve 67 seated at the bottom of a cylindrical
recess 67ª. The valve has therefore to rise a considerable distance before air can
pass from the inlet 63 to the chamber 61 and into the reservoir. The upper end
of the opening 64 is also normally closed by a valve 68 which is pivoted to a
lever 69, one end of which is pivoted to the casting 62, the other end of said lever
being located above and nearly in contact with valve 67. The action of this
device is as follows. That is to say, when the pump stops, valve 67 drops to its
seat and permits the free end of lever 69 to fall, allowing valve 68 to close. The
air and oil which has been pumped into the reservoir is thereby retained.
The arrangements for circulating water through the chambers in the pump
walls when necessary are shewn in Figures 2, 5, and 6 in which 70 is a water
tank connected at its top to chamber 22 in the pump walls by means of a pipe 71
and at its bottom with chamber 26 by pipe 72. The circulation of the water is
as follows: From the tank through pipe 72, chamber 26, passage 27, chamber 25,
passage 28, chamber 23, passage 24, chamber 22, and thence to the top of the
tank again by pipe 71. The circulation in this particular apparatus is effected
by reason of the heat generated in the machine, but any suitable circulating
arrangements may be provided if desired.
I will now describe the operation of the machine when employed for pumping
and compressing air. The shaft 29 is rotated in the direction of the arrow shewn
in Figures 6 to 8 by means of a belt on the pulley 73 or by any suitable means,

page_text: and air is drawn in through pipe 59 and valve 60, inlet 9, vertical tube 11, .
valve 12, chambers 13 and 14, and ports 16 into cylinder 1. This air forced by
the blades 38 through the outlet ports 18 into the chamber 17 and 17ª is drawn
from thence through the ports 19 into the upper portion of the high pressure
cylinder 2, being delivered through ports 21, chamber 20, and pipe 53 into the air
reservoir 52. The air valve 67 (see Figure 12) will of course be raised by the
air pressure, and through the medium of lever 69 raises valve 68, oil can then
flow out of reservoir 52, through tubes 66, 64 and pipe 55 and passages 56 and 57
into the grooves 48 in the plate 46, and thence through passages 49 into the
adjacent cavities in the drums 37 and 37*.
The oil is introduced into the cylinder in such a way that efficient packing and
lubrication of the frictional surfaces of all parts contained therein is secured. To
obtain this result, the oil enters each cylinder by flowing from one of the angular
channels 49 of the collar 46 into the adjacent one of the two cavities which are
recessed for the rings 39 of each cylinder in the drums 37 and 37 respectively.
This oil lubricates directly the inner end of each blade when it enters the central
space, which is tightened on its exterior by the packing strips 38b. The oil
pressure in the central space may attain that in the reservoir and the oil is in fact
held at this pressure in the central space of the small cylinder, so that it has the
maximum pressure of the air in this cylinder. To secure a corresponding oil
pressure in the central space of the low pressure cylinder, a channel 48" (Figure 3).
connects the intermediate air channel 17. in which the air has a pressure equal
to the maximum pressure in the said cylinder, with the angular channel 49 by
means of the oil groove 48 formed on the collar 46. The regulating screws 58
aid to produce the proper oil pressure in the central space of the cylinder. From
this space the oil is pressed outwardly along the sides of the blades 38 and
lubricates the packing strips 38b. Then it enters the air space of the cylinder,
where it collects on the forward surfaces of the blades and serves anew as a pack-
ing between the cylinder surface and the packing strips 38, and further between
the packing strips and the outer ends of the blades 38. The oil partly escapes
from the cylinder with the air and is delivered into the reservoir, from which
it returns into the cylinder in the way above described.
As hereinbefore mentioned the balancing rings 40 will rotate with the drums
and blades but at a less speed, and on account of the balancing of pressure all the
parts will rotate in the cylinders with very little friction. Any oil which passes
beyond the packing rings in the plates 30 and 30b will flow back through the
passages 73 and 74 into chambers 14 and 20 or into 14 alone as indicated in
Figure 3. and any oil which passes beyond the bearing rings 35 will flow back
through the channel 35" into the chamber 8 as shewn in Figure 4. The accumu-
lation of oil in chamber 8 will be drawn up together with the air through the
tube 11 and returned into the machine. The cylinders are kept cool by the circula-
tion of water in the passages 22 to 26 as hereinabove described.
It will be readily understood that the machine herein before described can be
used as a motor or engine, and may be operated by steam or compressed air or
other fluid, the valve 12 at the top of the pipe 11 being removed, and the operating
fluid being supplied under pressure in the reverse direction to that herein before
described. When driven by air the oil packing may be omitted or it may be
provided for by constantly collecting the oil which passes out the exhaust of the
engine and pumping it back to serve as a packing. When driven by steam, water
under considerable pressure such as results from condensation may be used for
packing purposes, or such packing may be dispensed with.
Referring now to Figures 16 to 21 which illustrate a pump of modified con-
struction 80 is a cylindrical outer casing having an air inlet 81 at one end and
closed at the other end by a cover 82. Bolted to the inner side of the cover 82
is a casing 83 having a head 84 similar to the head 4 of the figures previously
described. The casing 80 is provided at each side with a long horizontally pro-.

page_text: jecting lug. 85 by which the apparatus may be supported. The side walls of the
inner casing 83 are provided at the bottom with two chambers 86 and 87-separated
by a partition 88, and at the top with a single chamber. 89. The chamber 86
communicates with a chamber 89 on either side through valves 90. and 91, the
cavity 92 between. the valves communicating with the interior of the cylinder
through the ports 93, and all the valves are arranged to open upwardly, as shewn.
Shaft 29 is supported in the. heads 84 and 82 in a similar manner. to that herein-
above described with reference to Figure 1. of the drawing, and is provided with
a drum, blades, balancing ring, and other appurtenances as hereinabove described.
The chamber 89 comunicates through a channel in the head 84 with a pipe 94
which forms the delivery orifice of the pump.
The operation of the pump is as follows:-
When the shaft 29 is rotated for example in the direction of the arrow shewn
in Figure 21 a partial vacuum will be created in the right hand.chamber 92 by
means. of which the valve 91 will be held to its seat and valve 90 be raised. Air
will then be drawn from the chamber 86 which is in communication. with the.
atmosphere through the orifices 95 and 81 and passing, through the right hand
chamber 92.into.the cylinder will be forced into the left hand chamber 92. causing
the left hand valve 90 to be held down, while left hand valve 91 is raised.. The
air will then pass into the chamber 89 and into the delivery. pipe 94.
If now. the shaft 29 be rotated in the opposite direction. to that hereinabove
indicated air will be drawn from the chamber 86 through the left hand valve 90
and cavity 92 and be forced by the blades into the right hand chamber. 92
through the right hand valve 91 into the chamber 89.. It will therefor be seen
that the pump, adjusts itself automatically so as to force air always in the same
direction through the delivery pipe 94 irrespective of the direction of rotation.
of the shaft 29.
.
The arrangement for lubricating the blades and moving, parts of the pump
will now be described with reference to Figure 22 which illustrates the applica-.
tion of a pump such as that above described to an air brake. The pump. may be
connected by a belt 96 to one of the motors 97 which drives the vehicle. 98 is
an air reservoir connected by a pipe 99 to the delivery orifice 94. of the pump.
Said reservoir 98 preferably contains a small supply. of oil, which as the air is
pumped into the tank is forced. out through the pipe 100 into the chamber 87
(see Figure 18) and thence passes through the passages 101 and 49 into the
interior of the drum 37, whence it is forced as herein before described through.
the radial slots through the other moving parts of the apparatus. The. oil which
collects is returned' by, the pipes 35 to the chamber 86.
The air pipes, valves, and other parts of the brake apparatus may be the
usual description.
I desire it to be understood that although I have herein described and illus-
trated practical embodiments of my invention the details of construction and.
arrangements of the parts may be varied within considerable. limits without
departing from the spirit and scope of my invention.
Having now particularly described and ascertained the nature of my said inven-
tion and in what manner the same is to be performed I declare that what I
claim is:-
1. A rotary engine or pump of the class described having the blades divided
into two parts, one heavier than the other, the centrifugal force of. the former
being balanced, while that. acting on. the latter is utilized to maintain a suitable
pressure between said parts and the. interior surface of the cylinder.
2. In a rotary motor or pump of the kind.described a balancing ring, encircling
the radially movable piston blades operating_as and for the purpose specified.
3. In a pump of the kind described a double valve attached to the reservoir.
for the oil and compressed fluid so arranged that the oil valve is opened when but:
not until, the fluid valve has been raised a certain amount.

page_text: 4. The arrangements for using on as a packing as well as a lubricating material
substantially as described.
5. A rotary motor or pump constructed substantially as described with reference
to Figures 1 to 15 of the accompanying drawings.
6. A rotary motor or pump constructed substantially as described with reference
to Figures 16 to 21 of the accompanying drawings.
Dated this 10th day of August 1898.
W. P. THOMPSON & Co.,
322, High Holborn, London, W.C., Patent Agents for the Applicant.