Improvements in Fluid Compressors.
Year: 1896

page_text: Date of Application, 6th Oct., 1896-Accepted, 14th Nov., 1896
COMPLETE SPECIFICATION.
Improvements in Fluid Compressors.
I, FRANCIS MARION RITES, Mechanical Engineer, residing in the City of
Ithaca, County of Tompkins, State of New York, and United States of America,
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:-
The object of my invention is to provide means for varying the period of
operation of the positively operated valves of a fluid compressor, the operation of
which valves is effected and maintained by the mechanism of the compressor or
motor, and to enable the compressor to be run at a high rate of speed, without
imposing strains on the governing mechanism.
To this end, my invention, generally stated, consists in the combination, with a
motor cylinder and a compressor cylinder, of an adjustable valve gear, and a valve
for the compressor cylinder connected thereto, whose operation is effected and
maintained by the motor, but whose relative periods of operation are varied by
a governor under the influences of pressures within and without the compressor
cylinder.
The improvement claimed is hereinafter fully set forth.
My invention is not limited in application to the specific form of valve gear
berein set forth, but may be employed in connection with any of the usual forms of
adjustable valve mechanism, or with any form of valve mechanism in which the
functions of the valves are adapted to be automatically varied.
In the accompanying drawings:
Figure 1 is a side elevation of a compressor showing an application of my
improvement in connection with an Allan valve gear;
Fig. 2, a vertical, longitudinal section, or an enlarged scale, through the cylinder
and valve of the pressure governor, and through the cylinder of the device which
directly effects the variation in the adjustment of the valve gear of the compressor
cylinder;
Fig. 3, a vertical, longitudinal section, on the line x, x, of Figure 4, through a
valve device for controlling the admission of fluid from the compressor cylinder to
the cylinder of the pressure governing device, the means for actuating the admission
valve being shown in elevation;
Fig. 4, a horizontal section of the admission valve device, and a plan view of the
actuating mechanism for the admission valve;
Fig. 5, a plan view of a compound fluid compressor with a modification of my
improvement applied thereto;
Fig. 6, a side elevation and partial section of the compressor shown in Figure 5,
looking in the direction of the arrow marked a ;
Fig. 7, a similar side elevation and partial section of the construction shown in
Figure 5, looking in the direction indicated by the arrow marked b;
Fig. 8, an elevation of the shifting eccentric mechanism for controlling the
cut-off in the steam cylinders of the compressor shown in Figure 5 ;
Fig. 9, a section at right angles to Figure 8;
Fig. 10, an elevation of the fly wheel and.eccentric mechanism on the opposite
side of the compressor shown in Figure 5;
Fig. 11, a section at right angles to Figure 10;

page_text: Fig. 12, a central section through a compressor provided with another
modification of my improvement;
Fig. 13, an end elevation of the compressor shown in Figure 12;
Fig. 14, a modification of a portion of the governing mechanism shown in
Figure 12;
Fig. 15, a central section, on an enlarged scale, through the governing valve
device shown in Figure 13;
Fig. 16, a section, on an enlarged scale, through the governing valve device shown
in Figures 5, 6, and 7;
Fig. 17, a section through a modification of the governing valve device.
In the practice of my invention, as exemplified in Figures 1 to 4 of the drawings,
I provide a compressor in which the valve gear of the steam cylinder, 1, and the
valve gear of the air compressing cylinder, 2, are operated by a single eccentric, 4,
on the main shaft 5, both valve gears being connected with an Allan link, 3, which
is actuated by the eccentric.
The valve stem, 6, of the steam distribution valve, is connected to an oscillating
arm 50, and, by means of a rod 7, with a block, 8, which is adapted to slide in the
link 3. The block 8 is adjusted in position by the centrifugal governor, 9, which
is connected to the rod 7, by means of the lever 10 and link 11, or which may be
connected more directly to the block 8.
The air compressing cylinder, 2, may be provided with oscillating inlet and
outlet valves of any of the usual forms.
The arms 12 and 12", on the stems of the inlet valves, are connected by means of
rods, 13 and 13, with an oscillating wrist plate, 14, which is connected with the
link 3, by means of the rod 15.
The arins 16 and 16, on the stems of the outlet valves, are connected together
by means of, a rod 17, and also connected, by means of a rod 17", with an
oscillating arm 18, which is mounted on the frame of the engine. The oscillating
arm 18 is connected by means of a rod 19 with a block 20, fitted to slide in the
slot 3 of the Allan link 3.
It will be seen that, with this construction, the inlet and ontlet valves of the air
compressing cylinder, and the distribution valve of the steam cylinder, are all-
"actuated by the single eccentric 4, on the main shaft 5. The valve gear for
operating the outlet valves of the air compressing cylinder, and the valve gear for
operating the distribution valve of the steam cylinder, are adapted to be adjusted
by shifting the sliding blocks 20 and 8, respectively, in the slot 3 of the link 3.
The adjustment of the valve gear of the steam cylinder is effected by means of the
centrifugal governor 9 which operates automatically to shift the block 8, and the
adjustment of the valve gear which operates the outlet valves of the compressing
cylinder is effected by means of my improved governing mechanism, which will
now be described.
In the embodiment of my invention shown in Figures 1 to 4 of the drawings, a
lever 21, which is shown pivoted to the base or frame of the centrifugal governor,
is connected at one end to the rod 19, by means of a rod 22, and, at its other end,
by means of a link 23, to the rod 24, of a piston 25, shown in Figure 2, which is
fitted to work in a cylinder 26.
If preferred, the rod 22 may connect directly to the block 20, the object of the
connection being that the block 20 may be adjusted in position relative to the
link 3, by the movement of the lever 21. The movement of the lever 21, for this
purpose, is effected by the movement of the piston 25, which is actuated by fluid
under pressure in the cylinder 26, the admission and release of the fluid, to and
from opposite sides of the piston 25, being controlled by the valve 27.
The fluid by which the piston 25 is actuated may be obtained from any convenient
source of fluid under pressure, but in order to insure a constant supply of fluid
under pressure which will always be available, independently of the operation of
the compressor, and which will be of substantially uniform pressure, I prefer to
employ, in the construction shown, the pressure from a water main, or some other

page_text: permanent reservoir of pressure, which, in this instance, is connected with the valve
chamber 28 by means of the' passage 46, which opens into the valve chamber 28,
between the ends of the valve 27.
The valve 27 is connected, by means of a stem 29, with a floating lever 30, which
is connected at one end to the stem 24, of the piston 25, and, at its other end, to
the stem 31, of a piston 32, in the small cylinder 33.
One end of the cylinder 33 is connected, by means of a pipe 34, with the outlet
passage, 35, of the fluid compressing cylinder, 2, or with the reservoir into which
the fluid is compressed, and one side of the piston 32 is thus at all times exposed to
the pressure in the outlet, or in the reservoir, of the fluid compressor. The other
end of the cylinder 33 is connected, by means of a pipe 36, with branch pipes 37,
leading to opposite ends of the fluid compressing cylinder, 2, through which fluid
may be admitted from either end of the compressing cylinder to one side of
the piston 32 in the cylinder 33.
As it is not desirable that either end of the compressing cylinder should be, at
all times, in communication with the cylinder 33, I employ valves 39, in the
casings 38 and 38, shown in section in Figures 3 and 4, for closing communication
from each end of the cylinder 2, through the branch pipes 37, to the pipe 36 and
cylinder 33, and provide means for opening the valves 39, when it is desired
to put the cylinder 33 in communication with either end of the compressing
cylinder 2.
The valves 39 are normally beld to their seats, by means of springs 40, and are
provided with stems 41, which pass through the stuffing boxes 42, and extend into
position to be actuated by the tappets 43, which are pivoted on the arms, 16
and 16, of the outlet valves.
When the arm 16 is turning in the direction indicated by the arrow in Figure 3,
the tappet 43 is held against the stop 44.by the spring 45, one end of which bears
against the tappet and the other end of which is secured to the stop 44; and when
the tappet comes in contact with the stem 41, the valve 39 is unseated so as
to admit fluid from the end of the compressing cylinder 2 to the pipe. 36 and
cylinder 33. When the arm 16 is moving in the opposite direction, and the
tappet 43 comes in contact with the stem 41, the spring 45 yields and permits the
tappet to pass by the stem without opening the valve. The valves 39 are held
closed by the springs 40, except when unseated by the contact of the tappets 43
with the stems 41, and the positions of the tappets 43, on the armis 16 and 16, are
such that each tappet will come in contact with one of the stems 41, and unseat one
of the valves 39, just before the outlet valve at that end of the compressing
cylinder is opened. Communication is thus opened, through the pipes 37, and 36,
between one end of the compressing cylinder and the upper end of the cylinder 33,
at each stroke of the piston in the compressor cylinder, and the small piston 32, in
the cylinder 33, is exposed on one side to the pressure of the compressed fluid in
the compressing cylinder, just before the outlet valve at the end of the compressing
cylinder opens, and the closing of the valve 39 which is then effected by
the spring 40 prevents a reduction of pressure in the cylinder 33, above the
piston 32, such as would occur if communication between the compressing cylinder
and the small cylinder 33 remained open after the opening of the outlet valves of
the compressing cylinder. The closing of the valve 39 also prevents the small
piston 32 from being subjected to the variations of pressure which occur at other
times in the compressing cylinder.
It will be understood that each of the casings, 38 and 38", contains a valve
device similar to that shown in Figures 3 and 4; that both of these valves remain
closed except during the time that they are momentarily opened by the tappets 43;
and that the opening and closing movements of each of the admission, valves 39
always occur just before the opening of the outlet valve on the same end of the
5 compressor cylinder. The result of this operation is that the only pressure
admitted to the upper end of the smail cylinder 33 is the maximum pressure which
exists in the compressor cylinder just before the opening of the outlet valves.

page_text: So long as the pressure in the reservoir, or outlet passage, of the compressing
cylinder, and the maximum pressure which exists in the compressing cylinder, just
before the opening of the outlet valves, substantially balance oue another, the
opposing pressures on the opposite sides of the small piston 32 will balance one
another, and there will be no movement of the piston 32; the valve 27 will be held
in its middle position, so as to close the ports 47 and 48; the piston 25 will not be
moved to change the adjustment of the block 20 in the link 3; and there will be
no variation in the time of opening of the outlet valves.
If the adjustment of the block 20, in the link 3, is such that the outlet valves are
opened before the pressure of the fluid which is being compressed in the compressor
cylinder equals the pressure in the outlet passage or reservoir of the compressor,
or, if the adjustment is such that the outlet valves do not open until the pressure
in the compressing cylinder is considerably in excess of the pressure in the outlet
passage or reservoir, there will be a corresponding difference of pressures acting on
the opposite sides of the piston 32, the piston 32 will be moved, so as to shift the
valve 27 from its middle position, one of the ports, 47 or 48, in the cylinder 26, will,
be opened to admit fluid under pressure from the passage 46 to one side of
the piston 25, and the other port, at the opposite end of the cylinder 26, will be
opened to permit the escape of fluid from the other side of the piston 25, through
the valve 27, to the exhaust passage 49, and the piston 25 will be moved, by the
fluid under pressure from the passage 46, to operate the lever 21, and shift
the position of the block 20, in the link 3, in direction to effect the desired
variation in the time of opening the outlet valves.
If the pressure of the fluid admitted from the compressor cylinder to the small
cylinder is less that the reservoir pressure acting on the other side of the
small piston, the small piston 32, and the valve 27, will be moved upward, the
water main, or other independent source of fluid under pressure which is connected
to the opening 46, will be put in communication with the upper end of the
cylinder 26, the lower end of the cylinder 26 will be put in communication with
the exhaust or drain pipe, 49, and the piston 25 will be moved downward. The
downward movement of the piston 25, acting through the lever 21, will cause an
upward movement of the block 20 toward the centre of the link 3, and the
valve gear for operating the outlet valves will thereby be adjusted to effect a later
opening of the outlet valves. In case the pressure of the fluid admitted from the
compressor cylinder to the small cylinder 33 is sufficiently greater than the
reservoir pressure to cause a downward movement of the piston 32, the valve 27
will also be moved downward, the lower end of the cylinder 26 will be put
in communication with the main or other independent source of pressure, the upper
end of the cylinder 26 will be opened to the exhaust or drain pipe, 49, the
piston 25 will be moved upward, the lever 21 will be actuated to move the block 20
downward toward the end of the link 3, and the outlet valve gear will thereby be
adjusted to effect an earlier opening of the outlet valves.
In whatever direction the valve 27 is moved by the small piston 32, the piston 25
will be moved in the opposite direction, to effect the proper adjustment of the
outlet valve gear, and the same movement of the piston 25 which effects adjustment
of the valve gear, will, by means of the lever 30, move the valve 27 back to its
central position, in which position the valve 27 covers both of the ports 47 and 48,
at opposite ends of the cylinder 26, and confines the fluid in both ends of the
cylinder 26. The confined fluid on opposite sides of the piston 25 will then tend
to check or prevent any vertical vibratory movement of the end of the rod 23 or
of the rod 19.
After the adjustment of the block 20 to effect the opening of the outlet valves
at the proper time, that is, to effect the opening of the outlet valves at the time
when the pressure in the compressing cylinder bears the proper relation to the
pressure in the outlet passages and reservoir, these two pressures will be
approximately equal, the piston 32, in the small cylinder 33, will be substantially
balanced by the pressures on its opposite sides, and will be unaffected by any

page_text: vibrations of the valve mechanism whose adjustment it controls. In the drawing,
the area of that side of the piston 32 on which the reservoir pressure acts, is
greater than the area of the opposite side, on which the pressure in the com-
pressing cylinder acts, the difference being equal to the cross sectional area of the
piston rod 31, and the piston 32 is, to that extent, a differential piston. This
difference in area may be increased or diminished as found desirable, by enlarging
er diminishing the cross sectional area of the piston or by other means, or an
equivalent result may be obtained by the employment of a spring or weight on one
side of the piston, to offer additional resistance to pressure on the opposite sile.
I make no claim to any specific construction for this purpose, but merely indicate
that the construction and proportions may be varied without departure from my
invention.
The diameter of the piston 32 may be very small, as it is only necessary that the
area of the piston should be sufficient to permit the difference of pressures on its
opposite sides to move the small balanced valve 27. The pipe 36, which connects
one end of the small cylinder 33 with the ends of the air compressing cylinder, 2,
may be of such small diameter that it will contain but a small volume of fluid, aud
the volume of the cylinder 33 on one side of the piston 32, together with the
volume of the pipe 36, will, when the valve 39 is open, add but very little to the
clearance at the ends of the air compressing cylinder. This is of importance in all'
fluid compressors, but it is of special importance in fluid compressors employed in
connection with refrigerating apparatus.
In the practice of my invention, as shown in Figures 5, 6, and 7, I employ a
high pressure steam cylinder, 51, a low pressure steam cylinder, 52, a low pressure
Acid compressing cylinder, 53, and a high pressure fluid compressing cylinder, 54.
The piston, 55, in the high pressure steam cylinder and the piston in the low
pressure compressing cylinder have their reds 56 and 57 connected by means of a
yake, 58, within which the crank pin 59 works. The piston rods, 60, and 61, of'
the low pressure steam piston, 62, and the bigh pressure compressing piston, 63, are
connected together by means of the yoke 64, within which the crank pin 65 works.
The cranks 66 and 67 are placed at right angles to one another.
On one end of the shaft, 68, a fly wheel or rotary carrier, 69 on which is
mounted a shifting eccentric, 70, shown in Figures 5, 6, 8, and 9. This eccentric
is provided with a strap having the angularly disposed arms 71 and 72, the arm 71
being connected by the rods 73 and 74 with the admission valves, 75, of the high
pressure steam cylinder, and the arm 72 being connected with an arm 76, on a
rock shaft 77, which extends across the frame of the engine to the opposite side,
and carries, on its opposite end, an arm 78, which is connected, by the rods 79
and 80, with the admission valves, 81, of the low pressure steam cylinder, 52. By
means of these connections the shifting eccentric 70 is connected with, and adapted
to vary the adjustment of, the admission valves of both the bigh and low pressure
steam cylinders.
On the same side of the engine with the shifting eccentric, 70, is located a fixed
eccentric, 82, the strap of which is connected with the high pressure steam exhaust
valves, 83, by means of the rods 84 and 85, and with the inlet valves, 86, of the
low pressure compressing cylinder by means of the rods 87 and 88.
A fly wheel, or rotary carrier, 89, is mounted on the main shaft, 68, on the side
of the engine opposite to the fly wheel 69, and carries a shifting eccentric, 90,'
which is provided with a strap, having angularly disposed arms, 91, and 92; the
arm 91 being connected by rods 93 and 94 with the outlet valves, 95, of the high
pressure compressing cylinder, and the arm 92 being connected with an arm, 96, on
one end of a rock shaft, 97, which extends across the frame of the engine to the
opposite side, where it is provided with an arm, 98, which is connected, by means
of the rods 99 and 100, with the outlet valves 101 of the low pressure compressing
cylinder 53. By means of these connections the shifting eccentric 90 operates the
outlet valves of both the high and low pressure compressing cylinders.
Mounted on the main shaft, 68, outside of the shifting eccentric 90, is a fixed

page_text: eccentric 102, the strap of which is connected by rods, 103, and 104, with the
exhaust valves 105 of the low pressure steam cylinder, 52, and, by means of
rods 106 and 107, with the inlet valves 108, of the high pressure compressing
cylinder 54.
The shifting eccentric 70, which operates the admission valves of the high and
low pressure steam cylinders, may form part of and be adjusted by any preferred
form of governor, such as that shown in Figure 8, but the shifting eccentric.90,
which operates the outlet valves of the high and low pressure compressing
cylinders, is adjusted by mechanism whose operation is dependent on the relative
pressures in the high pressure compressing cylinder and in the reservoir, or
outlet passage leading from the high pressure compressing cylinder.
The governing mechanism controlling the adjustment of the shifting eccentric 90
is shown in Figures 5, 6, and 7, in position on the compressor, and in Figure 16 on
a larger scale and detached from the compressor.
As shown in the drawings the reservoir space, or outlet passage, 109, into which
the fluid is discharged from the high pressure compressing cylinder 54, is connected
by means of a pipe, 110, with one end of the governing valve device, 111, within
which is fitted the connected pistons 112 and 113. Springs 114 and 115 are
located in the piston chamber 120 of the cylindrical casing 111, in position to bear
on the opposite ends of the pistons, 112, and 113, and these springs tend to hold
the pistons in a central position. The outer ends of the springs bear against
plates 116 and 117, which are adjustable in position by means of the screws 118
and 119, as shown in Figure 16.
The outer end of the piston 112 is at all times exposed to the pressure in the
reservoir, which is admitted through the pipe 110, and the opposite end of the
piston chamber 120 is at intervals put in communication with the interior of
the high pressure compressing cylinder by the action of the outlet valve 95, shown
ou the left of Figure 7. A cavity 122 is so formed and located in the face of the
outlet valve 95 that, when the outlet valve is about to open, the cavity connects
the pipe, or passage, 123, leading to the lower end of chamber 120 with a pipe, or
passage, 121, leading to the interior of the high pressure compressing cylinder, and
thereby exposes the outer end of the piston valve 113 to the pressure within the
high pressure compressing cylinder.
If the pressures acting on the outer ends of the pistons 112 and 113 are equal,
there will be no movement of those pistons, but if the pressure in the compressing
cylinder, which acts on the outer end of the piston 113, is in excess of that in the
reservoir, and which acts on the piston 12, the pistons will be moved upward, and
the piston 112 will uncover the pipe, or passage, 124, leading from a supply of
fluid under pressure, and admit fluid under pressure to the pipe, 125, which leads
to a chamber 126 formed in the main shaft. 68. Within the chamber 126 is fitted
a piston, 127, and on its stem, 128, is formed, or secured, an inclined rack, 129, which
engages with a rack, 130, passing through the shaft and secured to the shifting
eccentric 90. Surrounding the stem of the piston 127 is a spring 131, which tends
to hold the piston in the outer end of the chamber 126 as shown in Figure 11.
6
When fluid under pressure is admitted through the pipe 125 to the chamber 126,
the piston 127 will be moved so as to adjust the eccentric 90 to a position in which
an earlier opening of the outlet valves of the compressor cylinders will be
effected.
When the outlet valve 95 puts the compressor cylinder in communication with
the chamber 120 below the piston 113, if the pressure in the compressing cylinder
is less than the reservoir pressure acting on the piston 112, the pistons 112 and 113
will be moved down so as to close the passage 124 and to open the pipe or
passage, 132. The fluid pressure acting on the small piston 127 will then be
released, through the pipe 132 which opens to the atmosphere, and the spring 131
will move the piston 127, and the rack 129, so as to shift the eccentric 90 into
position to effect a later opening of the outlet valves of the compressor cylinders.
It will be seen that by means of my improvement the shifting eccentric, operating

page_text: and controlling the time of opening of the outlet valves of the compressing cylinders..
will be automatically adjusted in accordance with the variations of fluid pressure in:
the reservoir and compressing cylinder, and this governing action, by varying the
time of opening of the outlet valves of the compressor, will also affect the resistance
required to be overcome by the motor, and cause a corresponding variation in the
cut-off of the motor fluid by means of the shifting eccentric 70.
The pipe 124, through which fluid pressure is admitted between the pistons 112.
and 113 and to the pipe 125, for moving the piston 127 in the chamber 126, may
be connected with a water main, or a steam boiler, or with any other suitable
supply of fluid under pressure, but it is preferred that this pressure should be
independent of the compressor or its condition as to operation, that is, it should be
available at all stages of operation of the compressor.
A small valve, 133, controls a passage, 134, in the head of the high pressure
compressing cylinder, and is normally held to its seat by the pressure in the
reservoir or outlet passage 109, and by a spring. The stem, 136, of this valve
passes out through a plug 135 into position to be visible on the outside of the
cylinder head, or to be felt by the hand, so that its outward movement by unusual
differences of pressure will indicate the condition of pressure in the compressing
cylinder. The sound caused by the closing movement of this valve may also-
indicate that the valve has been opened.
In Figures 12 and 13 I have shown my improvement applied to a vertical
compressor, in which the piston, 137, of the steam cylinder, 138, and the piston, 139..
of the compressing cylinder, 140, are connected to the cranks 141 and 142 placed.
at right angles to one another on the main shaft 143. On one end of the main.
sbaft is a fly wheel, 144, carrying a governor, not shown, and a shifting eccentric, 145,
which is connected to and operates the steam distribution valve 146. On the
opposite end of the main shaft is a shifting eccentric, 147, which is connected to
and operates the distribution valve, 148, of the compressing cylinder 140.
The shifting eccentric, 147, is adapted to be adjusted by means of a sliding wedge.
block, 149, which, in itself, is a common device for this purpose, and is employed
merely to show an application of my improvement. Sliding motion is given to the
wedge block by means of a pivoted arin, 150, which is provided with a forked
upper end, 151, connected to a loose collar, 152, on an extension of the wedge-
block. The arm 150 is pivoted at its lower end, and between its ends is connected
to the rod, 153, of a small piston, 154, which is fitted in a cylinder, 155. Inside of
the cylinder 155, the piston rod is surrounded by a spring, 177, which tends to
move the piston and the wedge block toward the left, as shown in Figure 12, and
to shift the eccentric so as to cause an early opening of the outlet valve of the
compressor.
The interior of the small cylinder, 155, is in communication, through the pipe 157,.
with the valve chamber, 158, of a governing valve device, 156, shown in Figures 13
and 15. The pipe 157 opens into the valve chamber, 158, between the two.
pistons, 159, and 160, which are connected to and operated by the movement of a
movable abutment, or diaphragm, 161. The diaphragm, 161, is exposed on one-
side to the pressure in the reservoir, or outlet passage, of the compressor, which is
admitted to the chamber 162 of the governing valve, through the pipe 163. The
outer side of the diaphragm, 161, is exposed to the pressure in the cylinder, 140, of
the compressor, which is admitted to the chamber 164 through the passage 165,.
which is at intervals connected with the interior of the cylinder 140 by means.
of a valve device connected to or operated by the main valve, 166, of the-
compressor.
Fluid is admitted to the ports 168 und 169 in the opposite ends of the compressing
cylinder, 140, through the passage 167 and through the body of the main
valve, 166, and alter being compressed is discharged into the passage 170 which
communicates with the reservoir.
Formed on, or connected to, the main valve, 166, of the compressor, is a small
valve, 171, having a cavity, 172, formed in its face, which controls communication.

page_text: between the passages 165 and 173 in the wall of the cylinder 140. The passage 173.
is at all times in communication with the interior of the compressor cylinder, 14),
and the passage 165 is in communication with the chamber 164 of the governing
valve device 156, and about the same time that the port 169 is opened to the
reservoir space, 170, by the valve 166, the cavity 172 connects the passage 173
with the passage 165 and admits fluid under pressure to the chamber 164 of the
governing valve device, on one side of the diaphragm 161. Except when the small
cavity 172 connects the passages 165 and 173, the chamber 164 of the governing
device is cut off from the main cylinder 140, and the diaphragm 161 is, therefore,
not exposed to the great variations of pressure that occur in the main cylinder.
When the pressure in the compressor cylinder, 140, at or near the time of
opening the port 169 to the reservoir, is substantially the same as the pressure in
the reservoir the diaphragm 161 of the governing device will be substantially
balanced by the reservoir pressure on one side acting against the cylinder pressure
and the pressure of the spring 174 on the other side, and the pistons 159 and 160
of the governing device will be held in the position shown in Figure 15. There
will then be no change in the adjustment of the shifting eccentric, 147, or of the
valve 166. When, however, the pressure in the compressing cylinder, at the time
of discharge through the port 169, is greater or less than the pressure in the
reservoir, the diaphragm 161 and the piston valves 159 and 160 will be moved in
direction to effect a proper adjustment of the eccentric 147 and valve 166, and
thereby to vary the time of opening the discharge from the cylinder 14 into the
reservoir space 170.
If, at the time of discharging from the compressor cylinder, the cylinder pressure
is considerably in excess of the reservoir pressure, it will be because the discharge.
from the cylinder to the reservoir is not early enough, and the cylinder pressure,
acting below the diaphragm 161, will move the diaphragm and the piston valves
upward, so as to close the exhaust passage, 175, and to connect the pipe 157 with
the pipe, or passage, 176, which may be connected with any reservoir or supply
of pressure, preferably a permanent supply from which pressure may be
obtained at any time.
When the pipe 157 is put in communication with the pipe, or passage, 176, the
pressure acting on the piston 154 will move the piston, and with it the lever 150
and the wedge block 149, to the right, and the shifting eccentric 147 and valve 166,
will be adjusted to effect an earlier discharge of fluid from the compressor
cylinder 140.
If the discharge from the compressor cylinder occurs too early, that is, at a
time when the pressure in the cylinder is relatively low as compared with that in
the reservoir, the pressure admitted through the passages 173, 172, and 165, to the
chamber 164 of the governing valve device, will be less than that above the
diaphragm, and the diaphragin and piston 159 and 160 will be moved down,
closing the passage 176 and opening the passage 175 which communicates with the
atmosphere. Pressure will then be released from the cylinder 154 through the
pipe 157 and pipe 175, and the spring 177 will move the arm or lever 150 and
the wedge block 149, so as to adjust the eccentric 147 and valve 166 to effect a
later opening of the discharge from the cylinder 140.
As shown in Figure 12 the passage 173 is so located that it may be opened to
the reservoir space, 170, at one end, by the movement of the small valve 171, but
its inner end will then be closed by the piston 139.
In Figure 14 of the drawings, I have shown a modification in which the
arrangement of the passages 173 and 165, through which fluid from the compressor
cylinder is admitted to one side of the diaphragm 161, is the same as in Figure 12,
but the valve 171 instead of being formed integral with the main valve 166, is
formed of a separate piece, fitted between two shoulders on the main valve, and
held to its sent by a spring 178.
In Figure 17, I have shown a modification of the governing valve device, in
which a piston, 180, fitted in a casing, 179, is connected to a valve, 181, controlling

page_text: the admission of pressure from the reservoir of the compressor to a pipe, 182,
through which fluid is supplied to act on a piston for operating the shifting
eccentric. Fluid under pressure from the cylinder of the compressor lifts the
check valve 184, and acts on the upper side of the piston 180, tending to move that
piston soas to seat the valve 181. The piston 180 and valve 181 are acted on by
the springs 185 and 186 tending to balance them when in the position shown in the
drawing. The check valve 184 is opened only when the pressure in the compressor
cylinder is in excess of that above the piston 180, and the closing of the check
valve prevents any return of fluid from the upper side of the piston 180 to the
cylinder. When the pressure in the reservoir is in excess of that above the
piston 180, the fluid under pressure admitted from the reservoir, through the
pipe 187, to the underside of the valve 181, will lift the valve 181, and pass through:
the pipe 182 to act on the piston for shifting the eccentric.
When the pressure in the reservoir is not sufficient to overcome the pressure
closing the valve 181, pressure inay be released from the pipe 182, through the
small passage, 188, in the casing 179, so as to permit an adjustment of the shifting
eccentric the reverse of that effected by admitting reservoir pressure to the
pipe 1×2.
A comparatively slow release of pressure from above the piston 180 is permitted
through the small passage 189 in the piston 180, but no pressure in the pipe 182
is caused thereby, as the Huid may escape more quickly through the opening, 188,
in the casing than it can pass through the passage 189 in the piston 180. The
object of the leakage passage 189 is to permit variations of pressure above the
piston 180, corresponding with the changes of pressure in the. compressor
cylinder.
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. In an elastic fluid compressor, the combination, of a compressing cylinder,
valve mechanism controlling the valves of said cylinder, and so connected with the
motor as to be positively and continuously operated by the motor during the whole
of the cycle of operation of the compressor, a pressure actuated device connected
to and acting to vary the operation of said valve mechanism, and connections from
the compressor cylinder. and from the outlet passage or reservoir of the compressor
to the pressure actuated governing device, whereby the adjustment of the valve
mechanism is effected by the opposing pressures of the fluid in the cylinder. and in
the outlet passage or reservoir of the compressor, substantially as set forth.
2. In an elastic fluid compressor, the combination, of a compressor cylinder,
valve mechanism controlling the valves of said cylinder, and so connected with the
motor as to be positively and continuously operated by the motor during the whole
of the cycle of operation of the compressor, a fluid pressure actuated device for:
effecting the adjustment of the valve mechanism and means whereby the operation
of the fluid pressure actuated device is controlled by the opposing pressures of the
fluid in the compressor cylinder and in the outlet passage or reservoir of the
compressor, substantially as set forth.
3. In an elastic fluid compressor, the combination, of a motor, a compressor
cylinder, valve mechanism receiving motion from the notor through an adjustable
link connection for directly operating the valves of the compressor cylinder from
the motor, and a fluid pressure governing device for effecting the adjustment of the
link connection and controlled by the opposing pressure of fluid in the compressor
cylinder and in the outlet passage or reservoir of the compressor, substantially as..
set forth.
4. In an elastic fluid compressor, the combination, substantially as set forth, of
a compressing cylinder, positively operated valve mechanism controlling the ou let
valves of said cylinder, a pressure actuated governing device connected to and
acting to vary the period of operation of said valve mechanism, valve mechanism

page_text: controlling the admission of pressure from the compressing cylinder to Bid
pressure actuated governing device, and connections for actuating said controlling
valve mechanism by the actuating mechanism of the outlet valves.
5. In an elastic fluid compressor, the combination, substantially as set forth, of
a compressing cylinder, a motor effecting the function of fluid compression in said
cylinder, valve mechanism controlling the outlet valves of the compressing cylinder
and operated positively by the motor, a pressure actuated governing device
connected to and adapted to vary the position of the member through which the
motor operates said valve mechanism, valve mechanism controlling the admission
of pressure from the compressing cylinder to said pressure actuated governing
device, and connections for actuating said controlling valve mechanism by the
actuating mechanism of the outlet valves.
6. In an elastic fluid compressor, the combination, substantially as set forth, of
a compressing cylinder, a motor effecting the function of compression in said
cylinder, valve mechanism controlling the cutlet valves of the compressing
cylinder, a valve actuating member operated positively by the motor shaft and
connected with said valve mechanism, a pressure actuated governing device
connected to said valve mechanism and adapted to vary the period of operation
imparted to it by the actuating member, valve mechanism controlling the admission
of pressure from the compressing cylinder to the pressure actuated governing
device, and connections for actuating said controlling valve mechanism by the
actuating mechanism of the outlet valves.
7. In a fluid compressor, the combination, with a valve device controlling the
port, or ports, of the compressing cylinder, of a shifting eccentric for operating
the valve device, and a governing device, operated by variations in the relative
pressures in the compressing cylinder and in the reservoir, or outlet passage, of the
compressor, for controlling the adjustinent of the shifting eccentric.
8. In a fluid compressor, the combination, with a valve device controlling the
discharge of fluid from the compressor cylinder, of a shifting. eccentric for
operating the valve device, and a governing device, operated by variations in the
relative pressures in the compressing cylinder and in the reservoir, or outlet
passage, of the compressor, for controlling the adjustment of the shifting
eccentric.
9. In a fluid compressor, the combination, with a valve device controlling the
port, or ports of the compressing cylinder, of a shifting eccentric for operating the
valve device, a governing device operated by variations in the relative pressures in
the compressing cylinder and in the reservoir, or outlet passage, of the compressor,
for controlling the adjustment of the shifting eccentric, and a passage controlled
by a main valve of the compressor for admitting fluid under pressure from the
compressor cylinder to the governing device.
10. In a fluid compressor, the combination, with a valve device controlling
a port, or ports, of the compressing cylinder, of a shifting eccentric for operating
the valve device, a governing device controlling the adjustment of the shifting
eccentric, and a valve for admitting fluid under pressure from the compressor
cylinder to the governing device.
11. In a fluid compressor, the combination, with a valve device controlling the
release of fluid from the compressing cylinder of a shifting eccentric for operating
the valve device and varying its time of opening, a governing device controlling
the adjustment of the eccentric, and a valve for admitting fluid under pressure
from the compressing cylinder. to the governing device.
12. In a fluid compressor, an indicating device exposed to the pressures in the
cylinder and in the outlet passage, or reservoir, of the compressor acting in opposite
directions, and a stem extending outside of the valve casing in position to act as an
indicator of the relative pressures in the cylinder and reservoir, substantially as
set forth.
13. In a fluid compressor, the combination, with the main valve, or valves, of
the compressing cylinder, of an auxiliary valve device mounted in the head, or

page_text: wall, of the cylinder in position to be acted on by the pressures in the reservoir and
cylinder, and which is adapted to be moved by the pressure within the cylinder
only when that pressure is abnormally greater than the pressure in the reservoir or
outlet passage, substantially as set forth.
14. In a fluid compressor, the combination, with a compressing cylinder having
a positively operated main valve, of an auxiliary valve device exposed to the
pressures in the cylinder and in the reservoir, or outlet passage, and adapted to be
operated by excess of pressure in the cylinder, and a stem extending outside of the
cylinder in position to indicate movement of the auxiliary valve device, sub-
stantially as set forth.
Dated the Seventh day of September. A.D. 1896.
Witnesses:-
W. M. TAYLOR.
E. DODDS.
FRANCIS MARION RITES.